Lubrication management of a pump for a micro combined heat and power system

Info

Publication number: 20040144093
Type: Application
Filed: Jan 28, 2003
Publication Date: Jul 29, 2004
Inventors: William Thompson Hanna (Gahanna, OH), Jan Beryl Yates (Reynoldsburg, OH), John Edward Lambert (Dublin, OH), Scott Nicholas Danhof (Plain City, OH)
Application Number: 10352452

Abstract

A piston pump with a working fluid region, drive mechanism and a lubricating fluid region. The pump's working fluid region is configured to circulate a working fluid through an external circuit, such as a micro combined heat and power system. The working fluid region is separated from its lubricating fluid region by a seal. By keeping a sufficient quantity of lubricating fluid against the lubricating fluid region side of the seal, leakage of working fluid from the working fluid region to the lubricating fluid region can be significantly reduced. The pump may include various alternative forms of lubricant pumping devices to effect transport and pressurization of the lubricating fluid, including a variable volume pumping cavity, separate oil transfer pump, and mixture between the lubricating fluid and high pressure working fluid. Various piston configurations in the working fluid region may also be used to improve piston sealing.

Description

Description

BACKGROUND OF THE INVENTION

[0001] The present invention generally relates to improvements in lubrication of a piston pump, and more particularly to improvements in the handling, transport and efficacy of piston pump lubricant used in the presence of an organic working fluid.

[0002] The concept of cogeneration, or combined heat and power (CHP), has been known for some time as a way to improve overall efficiency in energy production systems. With a typical CHP system, heat (usually in the form of hot air or water) and electricity are the two forms of energy that are generated. In such a system, the heat produced from a combustion process can drive an electric generator, as well as heat up water, often turning it into steam for dwelling or process heat. Traditionally, CHP systems have been large, centrally-operated facilities under the control of the state or, a large utility company, sized to provide energy for many thousands of users. Recent trends in the deregulation of energy production and distribution have made viable the concept of distributed generation. With distributed generation, the large, central generating station is supplemented with, or replaced by numerous smaller autonomous or semi-autonomous units. These changes have led to the development of smaller CHP systems, called micro-CHP, which are distinguished from traditional CHP by the size of the system. For example, the electric output of a generating station-sized CHP could be in the tens, hundreds or thousands of megawatts (MW), where the electric output of a micro-CHP is fairly small, in the low kWc or even sub-kWc range. The inclusion of a distributed micro-CHP system into dwellings that already have fluid-carrying pipes for heat transport is especially promising, as little or no disturbance of the existing building structure to insert new piping is required.

[0003] Accordingly, the market for localized heat generation capability in Europe and the United Kingdom (UK), as well as certain parts of the United States, dictates that a single unit for residential and small commercial sites provide heat for both space heat (SH), such as a hydronic system with radiator, and domestic hot water (DHW), such as a shower head or faucet in a sink or bathtub, via demand (instantaneous) or storage systems.

[0004] The inventors have discovered that the use of an organic working fluid in a micro-CHP system produces specific benefits over conventional fluids, such as water. For example, many organic working fluids remain fluid at temperatures that cause water to freeze, where damage and inoperability could ensue after prolonged exposure of a water-filled system to such temperatures. In addition, by using an organic working fluid rather than water, corrosion issues germane to water in the presence of oxygen, and expander sizing or staging issues associated with low vapor density fluids, are avoided. The inventors have additionally discovered that certain organic working fluids, such as halocarbon refrigerants or naturally-occurring hydrocarbons, combine desirable operational attributes with environmentally benign features. Examples of the former include the refrigerant known as R-245fa, while examples of the latter include some of the alkanes, such as isopentane.

[0005] The inventors have further discovered that, as an outgrowth of the use of organic working fluids, the feed pump becomes one of the key components in a micro-CHP system. The feed pump is responsible for circulating the working fluid through various Rankine-cycle components, including an evaporator, expander and condenser. While there are numerous pump configurations to choose from, the inventors have additionally discovered that axial piston pumps are especially beneficial in situations where long, maintenance-free pump life is of paramount concern. In such pumps, a mechanism such as a crank or swashplate converts the rotary movement of a shaft into rectilinear motion of one or more pistons inside close-fitting cylinders. The cylinders are typically defined at a distal (working fluid) end by a working fluid pumping chamber, and at a proximal (lubricating fluid) end by means to accommodate the crank, with a coupling device and associated drive mechanism extending between the proximal and distal ends. The reciprocating motion of the piston in the pumping chamber allows the working fluid present therein to be pressurized and subsequently discharged. Lubricant (such as oil) contained within the crankcase is circulated throughout at least the lubricating fluid region and the drive mechanism of the pump to reduce component wear. A difficult problem for piston pumps is how to maintain an appropriate lubricant supply in the crankcase with an imperfect seal between the pumping chamber of the working fluid region and the drive mechanism and lubricating fluid region, where over time, leakage of the working fluid past the seal will collect in the crankcase with the lubricating oil. Such action tends to dilute the oil, and since the working fluid (such as one of the aforementioned organic working fluids) is typically a low viscosity fluid, such dilution can compromise the ability of the oil to perform its intended lubricating function. This problem worsens as the seals wear, such wear being exacerbated by the large pressure differential between the pumping chamber and the crankcase. In another scenario, backward migration of lubricant or a mixture of lubricant and working fluid from the lubricating fluid region across the seal to the pumping chamber is possible, and can show up under the wide variations in system operating conditions, where during at least part of the cycle, the crankcase pressure is greater than the intake pressure.

[0006] What is needed is a pump that operates efficiently under the myriad operating conditions inherent in a micro-CHP system. The present inventors have recognized that judicious management of the pump lubricant can make important contributions to pump operability, durability and efficiency, which in turn has a dramatic effect on overall micro-CHP system durability and efficiency.

BRIEF SUMMARY OF THE INVENTION

[0007] These needs are met by the present invention, where improved lubrication management features are incorporated into a piston pump to facilitate pump operability. According to a first aspect of the present invention, a piston pump is disclosed. The pump includes at least one working fluid region, a drive mechanism, a lubricating fluid region and a seal that defines a boundary between the working fluid and lubricating fluid regions. The working fluid region includes an intake port configured to receive a working fluid, an outlet port configured to dispense the working fluid, and a piston disposed between the intake and outlet ports such that upon oscillation of the piston, the working fluid is pumped from the intake port to the outlet port. The drive mechanism includes a power transfer shaft rotatably responsive to a drive source, a tubular passageway extending from a space adjacent the power transfer shaft to the working fluid region such that the piston is contained in the portion of the tubular passageway in the working fluid region, a crosshead slidably disposed in the tubular passageway, the crosshead pivotally connected to the power transfer shaft, and at least one piston rod connected at a first end to the crosshead (or to the piston that is configured for long life with the side loads otherwise carried by the crosshead) and at a second end to the piston, the piston rod configured to impart an oscillating motion to the piston. The lubricating fluid region is coupled to at least the drive mechanism and includes a lubricant sump disposed adjacent the power transfer shaft and configured to contain at least a portion of the lubricant (alternately referred to as lubricating fluid), a lubricant reservoir in fluid communication with the lubricant sump, and a lubricant pumping device fluidly coupled to the lubricant sump. The seal is configured to reduce migration of fluid between the working fluid region and the lubricating fluid region.

[0008] Optionally, the lubricant sump is hermetically sealed. In another option, the lubricant pumping device can be configured to include a lubricant inlet channel configured to receive lubricant from at least one of the lubricant sump and the lubricant reservoir; an inlet check valve disposed in the lubricant inlet channel; a lubricant outlet channel; an outlet check valve disposed in the lubricant outlet channel; and a variable volume pumping cavity at least partially disposed in the tubular passageway, the cavity in fluid communication with the lubricant inlet channel and the lubricant outlet channel, the cavity defined at a first end by the crosshead such that upon oscillating motion of the crosshead, the lubricant introduced into the cavity through the lubricant inlet channel becomes pressurized and exits through the lubricant outlet channel. In addition, wherein the lubricant inlet channel can be fluidly coupled to the lubricant reservoir. Moreover, the variable volume pumping cavity is defined at a second end by a wall intermediate the crosshead and the working fluid region, and the seal is disposed in the wall. A reservoir seal (different than the previously-described seal defined at the boundary between the working fluid region and the lubricating fluid region) can also be disposed about the piston rod between the lubricant reservoir and the lubricant pumping device. Together, the boundary-defining seal and the reservoir seal distinguish the multiple compartments along the lengthwise dimension of the tubular passageway. The working fluid region can additionally be configured as a multi-unit pump. For example, the pump may include multiple working fluid regions, lubricating fluid regions, check valves and drive mechanisms each configured to cooperate to define a single unit of the multi-unit piston pump. In such a multi-pump configuration, the plurality of tubular passageways can be fluidly connected with one another.

[0009] In other options, the lubricant pumping device can comprise a separately-powered oil transfer pump, while the lubricant reservoir can be fluidly coupled to the piston pump. The pumping capacity of the oil transfer pump is preferably a small fraction of the capacity of the piston pump, for example, five (5) percent or less. The lubricant reservoir can be made to be separately pressurizable from the remainder of the lubricating fluid region, thereby pressurizing the seal that defines the boundary between the working fluid region and the lubricating fluid region. In at least one configuration, the drive source is a motor, where a first compartment can be configured to contain the motor, while a second compartment can hold at least a portion of the lubricating fluid region and the drive mechanism. In addition, a coupling extends from the motor (in the first compartment) to the power transfer shaft in the second compartment, while a vapor space seal is disposed about the coupling to define a boundary between the first and second compartments. A lubricant drain line fluidly coupled to the first compartment and to the oil transfer pump can be added such that the lubricant drain line can remove at least one of the working fluid and the lubricant from the first compartment. A lubricant return line may also be included to fluidly couple the second compartment and the oil transfer pump. In one embodiment, the first and second compartments are disposed in a common housing, which may be hermetically sealed. The first compartment may further comprise a heating element to maintain the temperature in the first compartment above the saturation temperature of the working fluid, thus inhibiting condensation of the working fluid. The lubricant drain line and the surface of the first compartment that contains the vapor space seal can be made to occupy the substantially lowest vertical position in the first compartment such that any lubricant that collects in the first compartment will flow through the lubricant drain line.

[0010] In another option, the lubricant pumping device can comprise a high pressure vapor source fluidly coupled to the lubricant sump. By way of example, the high pressure vapor source could be a lubricant pressurization chamber fluidly coupled to the lubricant sump. The pressurization chamber includes at least one check valve and a flow regulating device configured to intermittently allow the transport of fluid contained in the lubricant pressurization chamber to at least one of the working fluid region and the lubricating fluid region. In one embodiment, the flow regulating device is a time-responsive valve. By way of another example, the high pressure vapor source is a jet pump configured to inject lubricant into a flow of high pressure vapor, thereby causing the two streams to mix and a pumping effect is obtained.

[0011] According to another aspect of the invention, a piston pump is disclosed. The piston pump includes at least one working fluid region, drive mechanism and seal similar to that of the previous aspect. The lubricating fluid region includes a lubricant sump, a lubricant reservoir in fluid communication with the lubricant sump, and a lubricant pumping device. The lubricant pumping device includes a lubricant inlet channel configured to receive lubricant from at least one of the sump and reservoir, inlet and outlet check valves disposed in respective inlet and outlet channels, and a variable volume pumping cavity. The cavity is at least partially disposed in the drive mechanism's previously-described tubular passageway, and is in fluid communication with the lubricant inlet and outlet channels. The cavity is defined at a first end by the drive mechanism's crosshead (previously-described) such that upon reciprocating motion of the crosshead, lubricant introduced into the cavity through the lubricant inlet channel becomes pressurized and exits through the lubricant outlet channel. While the fluid is being pressurized in the cavity, it can exert a force on the seal to further reduce migration of working fluid into the lubricating fluid region from the working fluid region.

[0012] According to yet another aspect of the invention, a piston pump is disclosed. The piston pump includes at least one working fluid region, a drive mechanism, a lubricating fluid region and a sealing fluid distribution network. The working fluid region includes a pumping chamber for pressurizing a working fluid, intake and outlet ports fluidly coupled to the pumping chamber, and a piston disposed in the pumping chamber such that upon oscillation of the piston, working fluid in the pumping chamber is moved. A sealing channel is defined in the space between the piston and the pumping chamber such that sealing fluid introduced into the sealing channel effects an improved seal between the piston and the chamber. The drive mechanism includes a power transfer shaft rotatably responsive to a drive source, a tubular passageway extending from a space adjacent the drive mechanism to the working fluid region such that the piston is contained in the portion of the tubular passageway in the working fluid region, at least one piston rod pivotally coupled at a first end to the power transfer shaft and at a second end to the piston, the piston rod configured to impart an oscillating motion to the piston, and a lubricating fluid region coupled to at least the drive mechanism. The lubricating fluid region includes a lubricant sump disposed adjacent the power transfer shaft and configured to contain at least a portion of the lubricant; and a lubricant pumping device fluidly coupled to the lubricant sump. The sealing fluid distribution network is configured to transport the sealing fluid from the lubricating fluid region to the sealing channel.

[0013] Optionally, the sealing fluid distribution network has a lubricant flowpath disposed within the piston and piston rod such that fluid communication is established between the two. In addition, the flowpath can be made to terminate along a radial surface of the piston such that sealing fluid routed through the network can provide sealing and lubrication in the sealing channel. The piston further comprises at least one circumferential groove that is in fluid communication with the lubricant flowpath. An axial passage is disposed between the circumferential groove and the lubricant flowpath such that lubricant can be conveyed from the lubricant flowpath to the circumferential groove. In another embodiment, the sealing fluid distribution network comprises the piston, a scraper ring coupled to the piston, and the tubular passageway in the working fluid region. In this embodiment, the scraper ring can traverse the sealing channel during piston oscillation. The scraper ring may include a taper on its outer surface to preferentially allow sealing fluid migration into the pumping chamber while inhibiting working fluid migration out of the pumping chamber. The sealing fluid distribution network can be configured such that the pressure of the sealing fluid flowing through the sealing channel is sufficient to ensure that the net flow of fluid between the pumping chamber and the lubricating fluid region during each oscillating piston cycle is toward the pumping chamber. Each of the intake and outlet ports may additionally include a check valve.

[0014] According to still another aspect of the invention, a micro combined heat and power system is disclosed. The system includes a working fluid circuit configured to transport a working fluid, and at least one energy conversion circuit operatively responsive to the working fluid circuit such that upon operation of the system, the energy conversion circuit is configured to provide useable energy. The working fluid circuit includes an evaporator configured to convert the working fluid from a subcooled liquid into a superheated vapor, an expander in fluid communication with the evaporator, the expander including a first lubricant sump, a condenser in fluid communication with the expander, and a working fluid feed pump. The feed pump includes features that are common with previously-described aspects, including having at least one working fluid region, a drive mechanism, a lubricating fluid region and a seal.

[0015] Optionally, the previously-described lubricant pumping device comprises a high pressure vapor source fluidly coupled to the lubricant sump, where, in one embodiment, the expander is the high pressure vapor source. Also as discussed with some of the previous aspects, a jet pump coupled to the expander can be used to achieve pressurization of the lubricating fluid. In another embodiment, the lubricant pumping device is a separately-powered oil transfer pump fluidly connected between the expander and the second lubricant sump such that it can move the lubricant from the second lubricant sump to the expander, or from the first lubricant sump to the second lubricant sump at least during periods of system operation. The oil transfer pump can also be used to maintain the second lubrication sump substantially full of lubricant at least during periods of system operation. A pressure relief valve may further be disposed between the first lubricant sump and the second lubricant sump. In one configuration, the expander is a scroll expander comprising a working fluid inlet, a working fluid outlet, an orbiting involute spiral wrap, a stationary involute spiral wrap and a working fluid outlet. In another embodiment, a vapor line may extend from the second lubricant sump to the condenser. The lubricant reservoir can be made to be fluidly coupled to the first lubricant sump to receive lubricant that has been separated out of the expander. Also as previously discussed, the lubricant pumping device may be equipped with a lubricant inlet channel configured to receive lubricant from at least one of the first or second lubricant sumps or the lubricant reservoir, inlet and outlet check valves disposed in respective channels and a variable volume pumping cavity in fluid communication with the lubricant channels such that lubricant introduced into the cavity through the lubricant inlet channel becomes pressurized and exits through the lubricant outlet channel. The working fluid feed pump may further comprise a motor configured to provide power to the pump, and a housing with a first compartment configured to contain the motor, a second compartment configured to contain at least the power transfer shaft and the second lubricant sump, a coupling extending from the motor to the power transfer shaft, a vapor space seal disposed about the coupling and defining a boundary between the first and second compartments, and a lubricant drain line fluidly connected between the first compartment and the first lubricant sump. Additionally, a lubricant return line can be included that extends from the second compartment to the first lubricant sump such that, in conjunction with the oil transfer pump, a continuous loop is formed therebetween. In one embodiment, the second compartment is situated below the first compartment such that any lubricant present in the first compartment will collect along a lower surface formed in part by the vapor space seal. The first lubricant sump is configured such that a lubricant fluid level therein is situated in a lower vertical elevation than a lubricant fluid level in the first and second compartments, while the lubricant drain line is spaced adjacent the vapor space seal such that at least one of the working fluid and the lubricant collecting therealong can flow through the lubricant drain line to the first lubricant sump. As before, the first compartment may include a heating element to maintain the temperature in the first compartment above the saturation temperature of the working fluid.

[0016] In another option similar to that discussed in conjunction with the previous aspects, a sealing fluid distribution network configured to maintain a sealing fluid between the piston and a complementary surface in the working fluid region can be included. The sealing fluid distribution network may be configured as previously described, including a piston, a scraper ring coupled to the piston, and the tubular passageway in the working fluid region, where the scraper ring (which may additionally be tapered, also as previously described) may traverse the sealing channel upon the oscillation of the piston within the tubular passageway. In another embodiment (also as previously described), the sealing fluid distribution network comprises a lubricant flowpath disposed within the piston and piston rod such that fluid communication is established therebetween. As before, the pressure of the sealing fluid flowing through the sealing channel is sufficient to ensure that the net flow of fluid between the pumping chamber and the lubricating fluid region during each oscillating piston cycle is toward the pumping chamber.

[0017] According to yet another aspect of the invention, a method of operating a piston pump is disclosed. The method includes the steps of configuring the pump, connecting the intake port and the outlet port to a supply of the working fluid; introducing the working fluid to the intake port; activating the drive source so that the piston moves at least a portion of the working fluid from the intake port to said outlet port; and maintaining a sufficient quantity of said lubricating fluid in said lubricant reservoir to ensure that the side of said seal that is adjacent said lubricant reservoir is exposed to a substantially vapor-free environment. As before, the pump includes at least one working fluid region, a drive mechanism, a lubricating fluid region coupled to the drive mechanism, and a seal disposed in the tubular passageway, the seal defining a boundary between the working fluid region and the lubricating fluid region.

[0018] Optionally, the lubricant pumping device is a separate oil transfer pump placed in fluid communication with said lubricant sump. An additional step can include configuring a sealing fluid distribution network to provide sealing fluid to a sealing channel disposed between the piston and a complementary surface in the working fluid region. The sealing fluid distribution network comprises a flowpath defined in the piston and the piston rod to establish fluid communication between the lubricant sump and the sealing channel such that a sealing fluid may be introduced into the sealing channel through the flowpath. In another embodiment, the sealing fluid distribution network comprises the piston, a scraper ring coupled to the piston, and the complementary surface in the working fluid region. As previously discussed, the scraper ring can traverse the sealing channel upon the oscillation of the piston within the complementary surface in the working fluid region. The step of configuring the pump may include providing a motor configured to provide power to the pump, providing a first compartment to contain the motor, providing a second compartment configured to contain at least the power transfer shaft and the second lubricant sump, extending a coupling from the motor to the power transfer shaft, and establishing a vapor space seal disposed about the coupling such that a boundary is formed between the first and second compartments. The step of configuring the pump may further comprise connecting a lubricant drain line adjacent the vapor space seal such that lubricant collecting therealong can flow through the lubricant drain line and out of the first compartment, and connecting a lubricant return line to the second compartment such that excess of the lubricant collecting therein can flow through the lubricant return line and out of the second compartment. The step of configuring the pump may also include activating a heating element disposed in the first compartment so that the temperature in the first compartment is maintained above the saturation temperature of the working fluid. The oil transfer pump can be used such that at least a portion of the lubricant flowing in at least one of the lubricant drain line or the lubricant return line is moved to the lubricant sump. In an alternate operating mode, the oil transfer pump can be used to substantially fill the lubricant sump.

[0019] According to another aspect of the present invention, a method of operating a micro combined heat and power system is disclosed. The method includes the steps of configuring the pump to comprise at least one working fluid region, a drive mechanism, a lubricating fluid region coupled to the drive mechanism, and at least one seal disposed in the tubular passageway, connecting the intake port and the outlet port to a supply of the working fluid, introducing the working fluid to the intake port, activating the drive source so that the piston moves at least a portion of the working fluid from the intake port to the outlet port, and increasing the pressure of the lubricating fluid at the boundary above that of the lubricating fluid remaining in the sump. The working fluid region includes an intake port configured to receive a working fluid, an outlet port configured to dispense the working fluid, and a piston disposed between the intake and outlet ports such that upon oscillation of the piston, the working fluid is pumped from the intake port to the outlet port. The drive mechanism includes a power transfer shaft rotatably responsive to a drive source, a tubular passageway adjacent the power transfer shaft, a crosshead slidably disposed in the tubular passageway, the crosshead pivotally connected to the power transfer shaft, and at least one piston rod connected at a first end to the crosshead and at a second end to the piston, the piston rod configured to impart an oscillating motion to the piston. The lubricating fluid region includes a lubricant sump disposed adjacent the power transfer shaft and configured to contain at least a portion of a lubricating fluid, a lubricant reservoir in fluid communication with the lubricant sump, and a lubricant pumping device fluidly coupled to the lubricant sump.

[0020] Optionally, the increased lubricant pressure at the boundary can be produced by configuring the lubricant pumping device to include a lubricant inlet channel configured to receive lubricant from at least one of the lubricant sump and the lubricant reservoir, an inlet check valve disposed in the lubricant inlet channel, a lubricant outlet channel, an outlet check valve disposed in the lubricant outlet channel, and a variable volume pumping cavity at least partially disposed in the tubular passageway, the cavity in fluid communication with the lubricant inlet channel and the lubricant outlet channel, the cavity defined at a first end by the crosshead such that upon oscillating motion of the crosshead, the lubricant introduced into the cavity through the lubricant inlet channel becomes pressurized and exits through the lubricant outlet channel. The increased lubricant pressure at the boundary could also be produced by the additional steps of configuring the lubricant pumping device as a separate oil transfer pump and operating the separate oil transfer pump to pressurize the lubricant reservoir to a pressure higher than the pressure of the remainder of the lubricating fluid region.

[0021] According to still another aspect of the invention, a method of operating a micro combined heat and power system is disclosed. In addition to configuring a working fluid circuit to transport a working fluid similar to that of the previous aspect, the method includes the steps of fluidly connecting the intake port to the condenser, fluidly connecting the outlet port to the evaporator, starting the system such that the working fluid within the evaporator is converted into superheated vapor, expanded in the expander, cooled in the condenser, and pumped by the pump back to the evaporator in a continuous loop, and maintaining a sufficient quantity of the lubricating fluid in the lubricant reservoir to ensure that the side of the seal that is adjacent the lubricant reservoir is exposed to a substantially vapor-free environment.

[0022] Optionally, the method includes the additional step of configuring the lubricant pumping device to comprise a lubricant inlet channel to receive lubricant from at least one of the first or second lubricant sumps or the lubricant reservoir, an inlet check valve disposed in the lubricant inlet channel, a lubricant outlet channel, an outlet check valve disposed in the lubricant outlet channel, and a variable volume pumping cavity at least partially disposed in the tubular passageway, the cavity in fluid communication with the lubricant inlet channel and the lubricant outlet channel, the cavity defined at a first end by the crosshead such that upon reciprocating motion of the crosshead, the lubricant introduced into the cavity through the lubricant inlet channel becomes pressurized and exits through the lubricant outlet channel. The step of configuring the working fluid circuit could also comprise incorporating a separate oil transfer pump as the lubricant pumping device. In another embodiment, the method could also comprise the additional step of introducing the lubricating fluid into a sealing channel disposed between the piston and the generally cylindrical passageway. Moreover, the sealing fluid can be transported from the lubricating fluid region to the sealing channel. In addition, the sealing fluid distribution network comprises a lubricant flowpath disposed within the piston and piston rod such that fluid communication is established therebetween. Also, as previously discussed, the pump can be configured to have a first and second compartment to house the motor and power transfer shaft with second lubricant sump, respectively. Similar construction of the lubricant drain line and lubricant return line to that previously discussed can also be provided, as can heating the first compartment with a heating element. The step of operating the oil transfer pump may occur independent of operation of the micro combined heat and power system. An additional step of pressurizing the lubricating fluid with high pressure vapor that has exited the evaporator can also be employed, where the step of pressurizing the lubricating fluid is accomplished a device that comprises a lubricant pressurization chamber fluidly coupled to the lubricant sump, the pressurization chamber including at least one check valve and a flow regulating device configured to intermittently allow the transport of fluid contained in the lubricant pressurization chamber to at least one of the working fluid region and the lubricating fluid region. More specifically, the flow regulating device is a time-responsive valve. The step of pressurizing the lubricating fluid can also be accomplished with a jet pump configured to inject the lubricating fluid into a flow of the high pressure vapor.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS

[0023] The following detailed description of the preferred embodiments of the present invention can be best understood when read in conjunction with the following drawings, where like structure is indicated with like reference numerals and in which:

[0024] FIG. 1 shows a schematic diagram of a micro-CHP system according to an embodiment of the present invention with connection to external SH and DHW loops;

[0025] FIG. 2A shows a simplified cross section of an embodiment of the feed pump as well as fluid interconnection between it and other components of the micro-CHP system of FIG. 1;

[0026] FIG. 2B shows a variation of the feed pump of FIG. 2A. including a pressurizable lubricant reservoir;

[0027] FIG. 3 shows an alternate interconnection between the feed pump and the expander;

[0028] FIG. 4A shows the pump of the present invention that achieves lubricant pressurization with a variable volume pumping cavity;

[0029] FIG. 4B shows the pump of the present invention in its presently preferred configuration;

[0030] FIG. 5A shows one configuration of a hermetic feed pump and motor with a vapor seal therebetween;

[0031] FIG. 5B shows an alternate configuration of a hermetic feed pump and motor;

[0032] FIG. 6A shows one configuration for effecting a sealing interface between a piston and tubular passageway of the feed pump;

[0033] FIG. 6 shows an alternate configuration of the sealing interface;

[0034] FIG. 6C shows a variation of the piston of FIG. 6A;

[0035] FIG. 6D shows a cutaway view of the piston of FIG. 6C, showing the internal lubricant transfer path;

[0036] FIG. 6E shows a side view of the piston of FIG. 6C;

[0037] FIG. 7A shows an alternative system, where high pressure working fluid in conjunction with a timed valve are used for pressurizing lubricant; and

[0038] FIG. 7B shows a variation of the system shown in FIG. 7A, using a jet pump.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0039] Referring initially to FIG. 1, a micro-CHP system 100 capable of providing electric current and heated fluid is shown. The system 100 includes a working fluid circuit and an energy conversion circuit. The working fluid circuit includes an expander 101, a condenser 102, a pump 103 and an evaporator 104. These four components define the major components that together approximate an ideal Rankine cycle system, where the evaporator 104 acts as a constant pressure heat addition, the expander 101 allows efficient, nearly isentropic expansion of the working fluid, the condenser 102 acts to reject heat at a constant pressure, and the pump 103 provides efficient, nearly isentropic compression. The evaporator 104 functions as the primary heat generator, where the heat (shown in the figure being produced by a combustion process where a fuel, such as natural gas, is transported via gas line 152 past gas valve 153 to a burner 151) in the evaporator is transferred to an organic working fluid being transported through conduit 110 (alternately referred to as piping), while the hot exhaust gas stream from the combustion process is directed axially through exhaust duct 155. The organic working fluid (such as naturally-occurring hydrocarbons or halocarbon refrigerants, not shown) leaves the evaporator 104 and circulates via conduit 110 through the expander 101, condenser 102 and pump 103. The embodiment of the micro-CHP system 100 presently shown is operated as a directly-fired system, where the fluid that passes adjacent the heat source is also the working fluid passing through the expander 101. While the expander 101 can be any type, it is preferable that it be a scroll device, such devices being well known in the art. The energy produced by the expansion of the organic working fluid in the expander 101 is converted to electricity and heat in the energy conversion circuit, which is discussed in more detail below. The condenser 102 extracts excess heat from the organic working fluid after the fluid has been expanded and, in the process, returns the organic working fluid in liquid form to the pump 103, after which it is returned to evaporator 104. A controller 130 is used to regulate system operation. Sensors connected to controller 130 are used to measure key parameters, such fluid level information taken from level indicator switch 120, and organic working fluid temperatures at various points within the organic working fluid circuit. Through appropriate program logic, it can be used to vary pump speed, gas flow rate and evaporator output temperature, as well as to open and close valves.

[0040] As previously mentioned, the energy conversion circuit takes the increased energy imparted to the working fluid in the working fluid circuit and converts it into useable electrical and thermal forms. The electrical form of the useable energy comes from a generator 105 (preferably induction type) that is coupled to expander 101. The thermal form of the useable energy comes from a circulating fluid medium 140 (shown preferably as a combined SH and DHW loop) thermally coupled to condenser 102. Hydronic fluid flowing through circulating fluid medium 140 is circulated with a conventional pump 141, and can be supplied as space heat via radiator 148 or related device. The nature of the heat exchange process is preferably through either heat exchangers 180 (shown notionally for the DHW loop, but equally applicable to the SH loop), or through a conventional hot water storage tank (for a DHW loop). It will be appreciated by those skilled in the art that while the embodiments depicted in the figures show DHW and SH heat exchangers in parallel, it is within the spirit of the present disclosure that series or sequential heat exchange configurations could be used. It will also be appreciated that the heat exchanger 180 depicted in FIG. 1 could be in the form of the aforementioned hot water storage tank, where the hot fluid circulating through circulating fluid medium 140 gives up at least a portion of its heat to incoming domestic cold water coming from water supply 191A, which is typically from a municipal water source, well or the like. Once heated in the tank, the domestic water can then be routed to remote DHW locations, such as a shower, bath or hot water faucet, through DHW outlet 191B.

[0041] Referring next to FIG. 2A, details of the pump 103 and its interconnection to evaporator 104, expander 101 and condenser 102 are shown. The pump 103 provides the necessary pressurization to the working fluid to ensure that the fluid passes through all of the components in the working fluid circuit. As with many mechanical devices, pump 103 requires lubrication to avoid damage to and overheating of its various parts that come into moving contact with one another. The relatively compact nature of such pumps (including piston pumps), coupled with the commonality of some pump components between the working fluid and lubricant regions of the pump, is such that the working fluid and the lubricant can commingle if there is a leakage path between them. The construction of pump 103 according to the present invention is such that first, the likelihood of contamination of the lubricant by the working fluid is reduced, and second, fluid management features are included to meliorate the effects caused by the presence of working fluid that does happen to migrate to the lubricating fluid region so that working fluid can be at least partially purged from the lubricant and placed back in circulation in the working fluid circuit. The pump 103 is shown in a single piston configuration, although it will be appreciated by those skilled in the art that a multi-piston configuration would be equally applicable to the present micro-CHP system 100. In multi-piston pumps (not presently shown), two or more pistons can be arranged side-by-side, each inside of a corresponding cylinder, to increase working fluid flow throughput. In either the single piston or multi-piston arrangements, the pump 103, as described below, includes at least a working fluid region, a drive mechanism and a lubricating fluid region.

[0042] The working fluid region, through which the organic working fluid passes, accepts condensate from the condenser 102 through conduit branch 110D at intake port 103A and into engagement with an oscillating piston 103B in a working fluid pressurization chamber. The piston 103B forces the condensate to flow past check valve 103C toward outlet port 103D, after which it proceeds along conduit branch 110A to evaporator 104 to repeat its thermodynamic cycle. In one embodiment, the piston 103B can be configured as a generally hollow cylindrical member disposed coaxially about the piston rod 103H in a generally cylindrical chamber. The tubular body of the piston 103B includes disks 103B1, 103B2 disposed at opposite axial ends thereof such that they can move independently of one another for at least a portion of the motion in one direction of the axial dimension traversed by the piston rod in the tubular passageway. The first disk 103B1 is mounted to the piston rod 103H and is selectively engageable with a first end of the tubular body of piston 103B during the compression portion of piston motion such that the first disk 103B1 confines the working fluid within the tubular body during the compression portion of the reciprocating motion. The second disk 103B2 is selectively engageable with a second end of the tubular body of piston 103B, and is spaced axially apart from the first disk by an amount greater than the length of the tubular body such that the first and second disks alternately engage with respective ends of the tubular body. The second disk 103B2 includes at least one aperture therein such that the second disk 103B2 allows the introduction of the working fluid to pass through the tubular body during the suction portion of the piston's reciprocating motion. Seals can be disposed circumferentially about the piston 103B to reduce working fluid leakage around the piston.

[0043] The drive mechanism includes a power transfer shaft 103E, tubular passageway 103F, crosshead 103G and piston rod 103H. The shaft 103E is configured similar to a crankshaft in an internal combustion engine. The inherent eccentricity in shaft 103E, in combination with the tubular passageway 103F and the piston rod 103H and related linkages (not shown), converts the purely rotational movement coming from an external power source (such as a motor, described in more detail below) to impart linear, oscillating motion on piston 103B. The tubular passageway 103F extends from a proximal end that terminates in the lubricating fluid portion (discussed in more detail below) to a distal end that terminates in the aforementioned working fluid pressurization chamber of the working fluid region. The tubular passageway 103F can be cylindrical in shape, and may have multiple compartments along its axial dimension, each compartment defined by differing diameters and separated from one another by walls, seals or the like. An example of one compartment is the aforementioned working fluid pressurization chamber. The piston rod 103H extends through the substantial entirety of the tubular passageway 103F, terminating at one end in piston 103B and the other end at crosshead 103G. The crosshead 103G effects a relatively tight fit against the internal wall of tubular passageway such that side loads are borne through them rather than through the piston 103B. It will be appreciated by those skilled in the art that while the crosshead configuration does provide a reliable way to take some of the loads off the piston 103B, thereby allowing simpler sealing between the piston 103B and the corresponding inner wall of the tubular passageway 103F, other pump configurations that do not incorporate a crosshead could be used in the present pump. An example of such a configuration will be discussed below.

[0044] The lubricating fluid region occupies the inner cavity 103I (alternately referred to as a crankcase) of compartment 103Z of the pump housing, and includes a lubricant sump 103J that collects excess lubricant not being used on the internal pump machinery. The motion of shaft 103E, crosshead 103G and piston rod 103H is sufficient to splash lubricant throughout the lubricating fluid region, causing it to coat the substantial entirety of the internal cavity 103I and the various components therein. A lubricant reservoir 103K is spaced below an expander sump return port 103L such that lubricant travelling from the sump 101A of expander 101 through lubricant return line 110B is deposited into lubricant reservoir 103K. The lubricant level in lubricant reservoir 103K is such that it surrounds piston rod 103H, as well as bathes seal 103M. By having separate lubricant reservoir 103K, adequate lubricant contact with the seal 103M is maintained without having to flood the entire lubricant sump 103J; such a quantity of lubricant (if present) would necessitate the use of more oil, and would cause an unduly large viscous drag on the moving shaft 103E, crosshead 103G and piston rod 103H. While lubricant reservoir 103K is currently shown open at the top, thereby allowing excess lubricant to spill over into the lubricant sump 103J via channel 103N, as well as generally retaining pressure parity with the rest of lubricant sump 103J, another configuration (discussed in conjunction with FIG. 2b below) can be separately pressurizable relative to the rest of lubricant sump 103J. The bottom of lubricant sump 103J includes a lubricant transfer port 103P that is fluidly connected to expander 101. Oil transfer pump 103Q (which can be configured to pump in either direction) is used to distribute lubricant between pump 103 and expander 101. As presently shown, the oil transfer pump 103Q is configured to deliver lubricant from lubricant sump 103J to either expander 101 (where it can enter into the working fluid stream to pass through the expander), or expander sump 101A. In the case of a scroll expander, lubricant coming through the former path can be beneficial in getting lubricant to the scrolls in the aforementioned situation where the lubricant should not be exposed to the high temperature environment of the evaporator 104. Similarly, the expander sump 101A (essentially the shell for the power module), by virtue of its prevailing temperature regime, is a rather efficient separator of lubricant and working fluid; accordingly, lubricant routed therethrough can in effect be separated from the working fluid contaminant and sent back into the lubricant sump 103J of pump 103.

[0045] In a typical piston pump, the working fluid, being pressurized by a piston as well as having a low viscosity, can cross the boundary between the working fluid region and the lubricating fluid region. Since a lubricating fluid's viscosity is an important parameter to consider in determining the applicability of a lubricant for a particular application, the presence of a typically low-viscosity organic working fluid in the lubricating fluid region of a piston pump should be kept to a minimum, as any undue dilution of the lubricant caused by migration of the working fluid into the lubricant region can cause a reduction in pump lubrication, with a concomitant loss in pump performance and life. A significant leakage path for working fluid into the lubricant sump occurs along the piston rod in the space that bridges the working fluid region and the lubricating fluid region of a typical piston pump. In the present invention, seal 103M is disposed between the working fluid region and the lubricating fluid region, and is used to minimize the amount of fluid cross-talk between the two. Seal 103M and station line 103SL define the boundary between the working fluid region and the lubricating fluid region. The seal 103M is disposed about the portion of piston rod 103H that extends between the working fluid region and the internal cavity of the lubricating fluid region. The presence of seal 103M wrapped around the piston rod 103H helps to reduce contamination of the lubricant by the organic working fluid, but does not entirely prevent it, especially as the seal 103M wears out over time. Since operability concerns dictate that the pump 103 run for prolonged periods, and over myriad pressure and temperature regimes without the need to service the seal 103M, it is preferable to sacrifice complete fluid isolation by the seal for longer seal life to keep service, cost and system down-time to a minimum. By keeping one side of the seal 103M completely bathed in lubricant, the amount of working fluid that leaks into the lubricating fluid region is reduced. To further reduce the tendency of the working fluid to condense and subsequently mix with the lubricant in lubricant sump 103J, a supplemental heating device 103S can be added to the sump 103J. The heat generated will keep the working fluid in vapor form, where it can then be routed to the inlet of condenser 102 via working fluid vapor port 103R. This can be beneficial in system 100 startup, as residual liquid working fluid present in the evaporator sump 101A can be heated up in lubricant sump 103J to reduce working fluid contamination therein.

[0046] In operation of the micro-CHP system 100, a small amount of lubricant travels with the organic working fluid through at least a part of the working fluid circuit. By way of example, with scroll-based expanders, if the flow of working fluid through the working fluid circuit is on the order of 20 lbs/min., the lubricant flow might be on the order of 0.1 to 0.4 lbs/min (0.5 to 2 percent of the working fluid flow rate). This lubricant is necessary to prevent wear and enhance sealing of the scroll components. The nature of the organic working fluid and the lubricant is such that they can be either miscible, partially miscible, or immiscible with one another. Either type of lubricant is potentially capable of meeting the lubrication and sealing requirements. The primary difference is the ease with which the lubricant may be separated from the working fluid. Miscible lubricants cannot be readily be separated from the working fluid while in the liquid state. Thus, any miscible lubricant that passes through pump 103 will continue through the evaporator 104 and on to the expander 101 where it may be separated from the working fluid vapor and collected in expander sump 101A, which is fluidly connected to a lubricant return line 110B into pump 103. Immiscible lubricants can potentially be separated from liquid working fluid. Accordingly, the immiscible lubricant can be bypassed around the evaporator 104 to avoid adding heat to liquid which cannot do work in the expander. Therefore, a significant volume of immiscible oil could be passed through the pump for improved sealing and/or lubrication of the pump 103 without the need to have this additional, or large flow of working fluid passing through the evaporator 104 or the expander 101.

[0047] The configuration of FIG. 2A is not intended to bypass all the lubricant around the evaporator. Some lubricant will be carried over in the expander discharge line to the condenser and this lubricant will necessarily pass through the evaporator 104. The lubricant pump 103Q is intended to recirculate the lubricant/working fluid mixture back to the expander sump 101A so that the working fluid has the opportunity to separate-out and allow nearly pure lubricant to return through line 110B. This separation occurs because the mixture in the expander sump is at a much higher temperature than the mixture at the main pump inlet, even though both mixtures are at the same nominal pressure. The lubricant retains less working fluid at higher temperature, so one can minimize the working fluid concentration in the lubricant by allowing working fluid to distill off of the mixture in the expander sump 101A.

[0048] A variation of the system shown in FIG. 2A is depicted in FIG. 2B, where by action of oil transfer pump 103Q, the pressurized fluid flowing from lubricant sump 103J can be used to transport lubricant to pressurizable lubricant reservoir 103KK. Unlike lubricant reservoir 103K shown in FIG. 2A, the pressurizable lubricant reservoir 103KK is closed (save the inlet that is coupled to oil transfer pump 103Q) so that fluid pumped into it remains pressurized. A second seal 103MM surrounds piston rod 103H and is disposed in a wall used to compartmentalize pressurized lubricant reservoir 103KK. This configuration keeps fluid pressure on seal 103M that is at least equal to pressure on the seal from the working fluid region, thus minimizing leakage of working fluid into the lubricant. In this instance, the pressurized lubricant coming from the lubricant sump 103J through oil transfer pump 103Q can also be used for the expander 101, adding to the lubricant entering the expander with the working fluid vapor, as previously discussed.

[0049] Referring next to FIG. 3, an alternate arrangement between the pump 103 and the expander 101 is shown. While the interconnection between the pump 103 and the evaporator 104 and condenser 102 is the same as shown in FIGS. 2A and 2B, the interrelationship between the pump 103 and the expander 101 differs. In the present embodiment, the expander sump 101A is connected directly to the lubricant sump 103J through working fluid vapor port 103R such that oil transfer pump 103Q is oriented to pump from the expander sump 101A and into the sump 103J. By such an approach, the lubricant sump 103J is kept relatively full of lubricant (note the higher fluid level compared to FIGS. 2A and 2B). In the absence of active lubricant level controls, one of the lubricant sumps must be allowed to be full of lubricant, while the level in the other drops to some sustainable level and the lubricant pump maintains this status quo. The sustainable level and the lubricant charge to the system must allow for adequate lubricant and system function. As previously mentioned, the pumping direction of the oil transfer pump 103Q can be oriented either way, and coupled with relative changes in the vertical position of the lubricant sump 103J to expander sump 10A, configured according to system 100 needs. A check valve 103T is used to prevent the backflow of lubricant from the lubricant sump 103J to the expander sump 101A; this will help ensure that lubricant sump 103J stays relatively full of lubricant during periods where the pump 103 is not running, such as during shutdown/off conditions. Similarly, a pressure relief valve 103U is installed in a second recirculation line coming from the working fluid vapor port 103R. Large pressure differences between 101 and 103I are to be avoided. If the pressure in 101 is much higher than the pressure in 103I, then both lubricant from the sump and refrigerant from the condenser flow into the into the pump. The lubricant flow is tolerable, but the refrigerant will flow past the seal 103M and into 103I: this will tend to dilute the lubricant in 1031, inhibiting good lubrication of the working parts. This situation is preventable by allowing the lubricant to freely move through 103T into the pump reservoir 1031, thus pressurizing the reservoir and reducing the pressure difference. However, if the pressure in 1031 is higher than the pressure in 101, then the vapor can flow to 101 via valve 103U, thus equalizing the pressures, while the lubricant is trapped in the sump by valve 103T.

[0050] Referring next to FIGS. 4A and 4B, variations on another form of achieving oil pumping and seal pressurization are shown. Instead of incorporating a separate piece of machinery (in the form of oil transfer pump 103Q shown in FIGS. 2A and 2B), the present embodiments form a pumping device from the existing motion of the piston rod 103H and attached crosshead 103G in tubular passageway 103F. The addition of fluid-activated inlet check valve 103V and fluid-activated outlet check valve 103W in the portion of tubular passageway 103F in the lubricating fluid region that houses crosshead 103G allows lubricant entrained therein to be pressurized and pumped for distribution to other locations within micro-CHP system 100, such as to expander 101. As shown with particularity in FIG. 4A, excess from the expander sump 101A is pressurized and routed through conduit 103N, while the configuration of FIG. 4B takes low pressure lubricant with a low concentration of working fluid from lubricant sump 103J and after pressurizing it, routes it through lubricant reservoir 103K and into the inlet line of expander 101. As shown, the check valves 103W, 103V are configured to allow flow in the direction opposite of that of the embodiment shown in FIG. 4A. While both of these embodiments require the operation of pump 103 to function, and thus can not be run during periods of pump 103 inactivity, this limitation does not appear to have any practical consequences, based on the analysis of system testing. These embodiments are simple to operate, thereby providing a low-cost way to meet lubricant transfer needs.

[0051] An additional benefit to the approach of FIG. 4A is that the configuration of conduit 103N is such that it can receive fluid input via either lubricant reservoir 103K or lubricant sump 103J (the latter in cases (not shown) where the lubricant level in the sump is allowed to pass through overflow 103OF and to the inlet check valve 103V in the inlet channel). In situations where the lubricant level in the lubricant sump 103J is not above the inlet channel most, if not all, of any working fluid-rich fluid entering into the conduit 103N from the pumping device formed by crosshead 103G, piston rod 103H, the inner wall of a portion of tubular passageway 103F and the associated check valves 103V and 103W comes as overflow from lubricant reservoir 103K, which generally has a higher concentration of working fluid contaminant. Another benefit of both the FIGS. 4A and 4B embodiments is that the side of the seal 103M that is exposed to the variable cavity pumping device formed by passageway 103F, crosshead 103G, piston rod 103H and check valves 103V, 103W can be directly pressurized by the pumping action, as it is formed in a wall that defines a remote end of the cavity. As an alternate to the fluid-activated check valves, rotary valves (not shown) built into the crosshead connecting rod pin or the crankshaft could be used.

[0052] Additional variations could leave the inlet check valve 103V in place, while removing the outlet check valve 103W by discharging the lubricant through an orifice at elevated pressure, where the orifice would cause sufficient backflow resistance during the intake stroke to cause the lubricant to preferentially enter the tubular passageway pumping cavity through the inlet check valve. This variation allows for less complex construction and potentially lower cost, at the expense of reducing pump efficiency. Using a long capillary tube as the orifice could reduce the backflow from the high pressure side of the lubricant pump during the filling stroke, effectively utilizing the dynamics of the flow to reduce backflow and maintain pump volumetric efficiency. In both figures, working fluid vapor port 103R fluidly couples the top of the lubricating region of pump 103 to the inlet of the condenser 102 through conduit branch 110C so that any working fluid in the lubricating fluid region that exists in vapor form can be vented out. By placing the working fluid in the condenser 102 inlet, it can combine with the stream of working fluid in the working fluid circuit, and be placed back into circulation.

[0053] Referring next to FIG. 5A, an approach for achieving vapor sealing between compartments in pump 103 is shown. Pump 103 is shown presently as a multi-unit variation of that of FIGS. 2A and 2B, specifically including a three piston pump. As previously mentioned, the lubrication management approach of the present invention is equally applicable to single unit or multi-unit pumps. The drive source for turning shaft 103E is shown as an electric motor 103AA, which is housed in first compartment 103Y, while the remainder of pump 103 is housed in second compartment 103Z. Two separate compartments are advantageous because the presence of a fluid lubricant, which is crucial to proper operation of the contacting components within the pump 103, can cause excess viscous drag if present near the rotor of electric motor 103AA. Thus, to avoid a buildup of lubricant in the first compartment 103Y, it is substantially fluidly isolated from second compartment 103Z. As with the space between the working fluid region and the lubricating fluid region discussed in conjunction with FIGS. 2A and 2B, a coupling 103BB between components in adjacent compartments also provides a leakage path that, unless kept in check, will only worsen with use. In the present figure, the coupling 103BB is used to transmit rotational power from motor 103AA to shaft 103E. In the alternate, coupling 103BB can be a common shaft between the motor 103AA and the pump 103. Accordingly, a vapor seal 103CC is disposed about the coupling between the first and second compartments 103Y, 103Z to minimize leakage of lubricant and organic working fluid from the latter to the former. As with seal 103M discussed above, vapor seal 103CC need not be a leak-free seal, as more emphasis is placed on its long-life properties than on its ability to provide complete fluid isolation between the two compartments. A lubricant drain line 103DD fluidly connects the first compartment 103Y to expander sump 101A, while a lubricant return line 103EE fluidly connects the second compartment 103Y to expander sump 101A. The lowest portion of the first compartment 103Y is situated vertically higher than the expander sump 101A so that any lubricant or organic working fluid that does get past vapor seal 103CC can drain to the expander sump 101A through lubricant drain line 103DD. Ideally, the temperature in the first compartment 103Y would remain (during system operation) above the local saturation temperature of the organic working fluid. If such conditions aren't always possible, a heater 103FF can be included in the first compartment 103Y to provide supplemental heating such that if heat from the motor 103AA is insufficient to vaporize any organic working fluid present in the first compartment 103Y, the heater 103FF can be used to boil off excess organic working fluid as vapor, where it can be returned to the expander sump 101A for reintroduction into the working fluid circuit of the system 100. As before, an oil transfer pump 103Q, shown presently pumping from evaporator sump 101A to lubricant sump 103J to overcome the effects of gravity between the two, circulates lubricant between the expander sump 10A and lubricant sump 103J in pump 103.

[0054] Referring next to FIG. 5B, an alternate configuration for the vapor seal of FIG. 5A is shown. The present configuration is simpler than the one shown in FIG. 5A, in that it does not include a direct fluid connection to take excess lubricant collecting in the first compartment 103Y back to either expander sump 101A or second compartment 103Z. Nevertheless, as with the configuration of FIG. 5A, it includes provisions (including heater 103FF) to remove organic working fluid vapor from first compartment 103Y and put it back in evaporator sump 10A. During system operation, the pressure in second compartment 103Z is greater than the pressure in first compartment 103Y, due in part to organic working fluid build-up in the lubricant sump 103J in second compartment 103Z. This prevents the migration of lubricant that collects above the vapor seal 103CC at least until system shutdown, where pressures on opposite sides of the vapor seal 103CC can equalize. Lubricant drain line 103DD is situated between the area immediately above seal 103CC and the expander sump 101A to avoid excess lubricant buildup above this seal, with proper function ensured by placing sump 101A on a similar level with the seal. It will be appreciated by those skilled in the art that other pumping devices besides the oil transfer pump 103Q can be used with the vapor seal configuration of the present figure. To prevent leakage of the organic working fluid to the outside environment, the first and second compartments 103Y, 103Z can be hermetically sealed.

[0055] Referring next to FIGS. 6A and 6B, alternate configurations for the piston and working fluid region of the pump of FIGS. 2A and 2B are shown. By delivering the relatively high viscosity fluid to the interface (hereinafter referred to as sealing channel) between piston 203B and the inner wall of working fluid pressurization chamber 203D, both improved sealing and wear resistance are affected. A sealing fluid distribution network is set up to effect sealing in the channel. In the first embodiment, shown with particularity in FIG. 6A, the piston 203B is shown with scraper 203LL disposed around the piston periphery. The scraper 203LL is defined by a tapered shape such that only during the suction stroke of the piston 203B does a portion of the lubricant in the lubricant sump 203J pass the scraper 203LL and into the discharge side at the working fluid pressurization chamber 203D. The manner in which the lubricant reaches the scraper 203LL is by splash, spray, flooding or related means well-known in engines and compressors. Once the lubricant gets past the scraper 203LL and into the working fluid pressurization chamber 203D, it gets trapped, thus effecting a seal in the sealing channel on the discharge stroke of the piston 203B. Unlike the construction of piston 103B shown in FIGS. 2A and 2B, where the piston itself included a pumping chamber, the present embodiment reflects the relatively simple construction similar to that found in an internal combustion piston engine, including a pivotal connection to piston rod 203H at wrist pin 203MM. Similar to the embodiment shown in FIGS. 2A and 2B, the working fluid region is fluidly connected to the working fluid circuit of a micro-CHP system (not presently shown) through an intake port 203A and outlet port 203D. Fluid-activated check valves 203NN are placed in the respective inlet and outlet ports to ensure only one-way flow.

[0056] In a second embodiment of the sealing fluid distribution network, shown with particularity in FIGS. 6B through 6E, the piston 203B of FIG. 6A includes a modification, in that in place of scraper 203LL, a circumferential lubricant injection groove 203PP is embedded in the piston periphery such that lubricant can be distributed to the sealing channel, thereby allowing it to act like a hydrodynamic bearing. Unlike the piston configuration of FIG. 6A, the present embodiment delivers the lubricant under pressure to the sealing channel via internal flowpaths in piston 203B and piston rod 203H, where pressurized lubricant can be introduced into piston rod 203H from oil transfer pump 203Q. FIGS. 6C through 6E show internal construction of the piston 203B. Cutout 203RR defines the region in piston 203B that accommodates the wrist pin attached to the piston rod, neither of which are currently shown. The circumferential delivery made possible by groove 203PP helps to ensure an even distribution of the lubricant to the sealing channel. Sealing fluid that enters the cutout 203RR can both lubricate the wrist pin as well as escape side openings 203SS to the sealing channel. FIG. 6D shows a section view of piston 203B, highlighting how sealing fluid can pass through cutout 203RR and extension 203TT, terminating in one or more radial apertures in the surface of groove 203PP. FIG. 6E shows the piston 203B rotated 90° about the vertical axis relative to the position shown in FIGS. 6C and 6D, with an alternate way to deliver sealing fluid to groove 203PP. Here, extension 203TT is placed on the outer surface of piston 203B such that it fluidly connects cutout 203RR and groove 203PP without an internal connection. This can be advantageous in that it is easier to make the external cut on the piston as shown in FIG. 6E than the internal passageways shown in FIGS. 6C and 6D. This embodiment functioning as a hydrodynamic bearing may enable the crosshead (not presently shown) to be removed, as side loads that were hitherto taken up by the crosshead can be absorbed by the sealing interface between the piston and the tubular passageway. In one embodiment, the sealing fluid used at the sealing channel is the same as the lubricant disposed in lubricant sump 203J.

[0057] The previously-described oil transfer pump 103Q and the variable volume pumping cavity are but two ways of achieving supplemental lubrication management within the micro-CHP system 100. Referring next to FIGS. 7A and 7B, additional methods for pressurizing the lubricating fluid can be used. For example, high pressure organic working fluid can be extracted from the working fluid circuit prior to expansion in expander 301 and routed to chamber 303UU. Referring with particularity to FIG. 7A, the check valves 303QQ allow low pressure lubricating fluid sump 303J to fill lubricant pressurization chamber 303UU when vapor valve 303RR is closed. When the vapor valve 303RR is opened, the high pressure working fluid vapor pressurizes the fluid in lubricant pressurization chamber 303UU and the mixture is forced out through one of the check valves 303QQ to where the oil is needed, such as expander 301 or lubricant reservoir 303KK. When the vapor valve 303RR is closed, the residual vapor collapses and the pressure between the two check valves 303QQ drops, allowing fresh oil to flow in through the check valve upstream of lubricant pressurization chamber 303UU, refilling the chamber. The cycle is then ready to restart. Referring with particularity to FIG. 7B, the mixing of high pressure vapor and lubricant can occur in a jet pump 303SS, where, as before, the lubricant can be added from lubricant sump 303J. In the jet pump 303SS, high pressure working fluid, taken upstream of expander 301, is passed through a venturi 303VV in pump 303SS such that, in what is commonly known as the Bernoulli effect, the decreased pressure in the working fluid vapor stream draws in the low pressure lubricant at inlet 303WW, thus promoting mixture between the two fluids. In a manner somewhat similar to the configuration shown in FIG. 2B (where lubricant can enter via inlet 103LL), the lubricant exiting expander sump 301A can enter blind reservoir 303KK through inlet 303L and be used to keep seal 303M bathed in lubricant. Gap 303MM between piston rod 303H and the wall defining one side of blind reservoir 303KK allows lubricant cross-talk between blind reservoir 303KK and the inner cavity/crankcase 3031 of compartment 303Z of the pump 303. It will be appreciated by those skilled in the art that the configurations shown in FIGS. 7A and 7B can be coupled to any of the previously-disclosed configurations, as evidenced by the commonality of numerous piston pump components.

[0058] Having described the invention in detail and by reference to preferred embodiments thereof, it will be apparent that modifications and variations are possible without departing from the scope of the invention defined in the appended claims. More specifically, although some aspects of the present invention are identified herein as preferred or particularly advantageous, it is contemplated that the present invention is not necessarily limited to these preferred aspects of the invention.

Claims

1. A piston pump comprising:

at least one working fluid region comprising:

an intake port configured to receive a working fluid;

an outlet port configured to dispense said working fluid, and

a piston disposed between said intake and outlet ports such that upon oscillation of said piston, said working fluid is pumped from said intake port to said outlet port;

a drive mechanism comprising:

a power transfer shaft rotatably responsive to a drive source;

a tubular passageway extending from a space adjacent said power transfer shaft to said working fluid region such that said piston is contained in the portion of said tubular passageway in said working fluid region;

a crosshead slidably disposed in said tubular passageway, said crosshead pivotally connected to said power transfer shaft; and

at least one piston rod connected at a first end to said crosshead and at a second end to said piston, said piston rod configured to impart an oscillating motion to said piston;

a lubricating fluid region coupled to at least said drive mechanism, said lubricating fluid region comprising:

a lubricant sump disposed adjacent said power transfer shaft and configured to contain at least a portion of said lubricant;

a lubricant reservoir in fluid communication with said lubricant sump; and

a lubricant pumping device fluidly coupled to said lubricant sump; and

at least one seal disposed in said tubular passageway, said seal defining a boundary between said working fluid region and said lubricating fluid region such that said seal is configured to reduce migration of fluid between said working fluid region and said lubricating fluid region.

2. A piston pump according to claim 1, wherein said lubricant sump is hermetically sealed.

3. A piston pump according to claim 1, wherein said lubricant pumping device comprises:

a lubricant inlet channel configured to receive lubricant from at least one of said lubricant sump and said lubricant reservoir;

an inlet check valve disposed in said lubricant inlet channel;

a lubricant outlet channel;

an outlet check valve disposed in said lubricant outlet channel; and

a variable volume pumping cavity at least partially disposed in said tubular passageway, said cavity in fluid communication with said lubricant inlet channel and said lubricant outlet channel, said cavity defined at a first end by said crosshead such that upon oscillating motion of said crosshead, said lubricant introduced into said cavity through said lubricant inlet channel becomes pressurized and exits through said lubricant outlet channel.

4. A piston pump according to claim 3, wherein said lubricant inlet channel is fluidly coupled to said lubricant reservoir.

5. A piston pump according to claim 3, wherein said variable volume pumping cavity is defined at a second end by a wall intermediate said crosshead and said at least one working fluid region.

6. A piston pump according to claim 5, wherein said at least one seal is disposed in said wall.

7. A piston pump according to claim 1, further comprising a reservoir seal disposed about said piston rod between said lubricant reservoir and said lubricant pumping device.

8. A piston pump according to claim 7, wherein said at least one seal and said reservoir seal define boundaries between multiple compartments along the lengthwise dimension of said tubular passageway.

9. A piston pump according to claim 1, wherein said at least one working fluid region comprises a plurality of working fluid regions, each configured to cooperate with corresponding said tubular passageways, crossheads, piston rods and seals to define a single unit of a multi-unit piston pump.

10. A piston pump according to claim 9, wherein said plurality of tubular passageways are fluidly connected with one another.

11. A piston pump according to claim 1, wherein said lubricant pumping device comprises a separately-powered oil transfer pump.

12. A piston pump according to claim 11, wherein said lubricant reservoir is fluidly coupled to said piston pump.

13. A piston pump according to claim 11, wherein said lubricant reservoir is separately pressurizable from the remainder of said lubricating fluid region.

14. A piston pump according to claim 11, wherein the pumping capacity of said oil transfer pump is less than five percent of that of said piston pump.

15. A piston pump according to claim 11, wherein said drive source is a motor.

16. A piston pump according to claim 15, further comprising:

a first compartment configured to contain said motor therein;

a second compartment configured to hold a lubricant and at least a portion of said lubricating fluid region and said drive mechanism therein;

a coupling extending from said motor to said power transfer shaft in said second compartment;

a vapor space seal disposed about said coupling and defining a boundary between said first and second compartments; and

a lubricant drain line fluidly coupled to said first compartment and said oil transfer pump, said lubricant drain line configured to remove at least one of said working fluid and said lubricant from said first compartment.

17. A piston pump according to claim 16, further comprising a lubricant return line fluidly coupled to said second compartment and said oil transfer pump.

18. A piston pump according to claim 17, wherein said first and second compartments are disposed in a common housing.

19. A piston pump according to claim 18, wherein said common housing is hermetically sealed.

20. A piston pump according to claim 16, wherein said first compartment further comprises a heating element disposed therein, said heating element configured to maintain the temperature in said first compartment above the saturation temperature of said working fluid.

21. A piston pump according to claim 16, wherein said lubricant drain line and the surface of said first compartment that contains said vapor space seal occupy the substantially lowest vertical position in said first compartment such that any lubricant that collects in said first compartment will flow through said lubricant drain line.

22. A piston pump according to claim 1, wherein said lubricant pumping device comprises a high pressure vapor source fluidly coupled to said lubricant sump.

23. A piston pump according to claim 22, wherein said high pressure vapor source further comprises:

a lubricant pressurization chamber fluidly coupled to said lubricant sump, said pressurization chamber including at least one check valve; and

a flow regulating device configured to intermittently allow the transport of fluid contained in said lubricant pressurization chamber to at least one of said working fluid region and said lubricating fluid region.

24. A piston pump according to claim 23, wherein said flow regulating device is a time-responsive valve.

25. A piston pump according to claim 23, wherein said high pressure vapor source is a jet pump configured to inject lubricant into a flow of high pressure vapor.

26. A piston pump comprising:

at least one working fluid region comprising:

an intake port configured to receive a working fluid;

an outlet port configured to dispense said working fluid, and

a piston disposed between said intake and outlet ports such that upon oscillation of said piston, said working fluid is pumped from said intake port to said outlet port;

a drive mechanism comprising:

a power transfer shaft rotatably responsive to a drive source;

a tubular passageway extending from a space adjacent said power transfer shaft to said working fluid region such that said piston is contained in the portion of said tubular passageway in said working fluid region;

a crosshead slidably disposed in said tubular passageway, said crosshead connected to said power transfer shaft; and

at least one piston rod connected at a first end to said crosshead and at a second end to said piston, said piston rod configured to impart an oscillating motion to said piston;

a lubricating fluid region coupled to at least said drive mechanism, said lubricating fluid region comprising:

a lubricant sump disposed adjacent said power transfer shaft and configured to contain at least a portion of said lubricant;

a lubricant reservoir in fluid communication with said lubricant sump; and

a lubricant pumping device comprising:

a lubricant inlet channel configured to receive lubricant from at least one of said lubricant sump and said lubricant reservoir;

an inlet check valve disposed in said lubricant inlet channel;

a lubricant outlet channel;

an outlet check valve disposed in said lubricant outlet channel; and

a variable volume pumping cavity at least partially disposed in said tubular passageway, said cavity in fluid communication with said lubricant inlet channel and said lubricant outlet channel, said cavity defined at a first end by said crosshead such that upon reciprocating motion of said crosshead, said lubricant introduced into said cavity through said lubricant inlet channel becomes pressurized and exits through said lubricant outlet channel; and

at least one seal disposed in said tubular passageway, said seal defining a boundary between said working fluid region and said lubricating fluid region such that said seal is configured to reduce migration of fluid between said working fluid region and said lubricating fluid region.

27. A piston pump comprising:

at least one working fluid region comprising:

a pumping chamber for pressurizing a working fluid;

an intake port fluidly coupled to said pumping chamber, said intake port configured to receive said working fluid;

an outlet port fluidly coupled to said pumping chamber, said outlet port configured to dispense said working fluid; and

a piston disposed in said pumping chamber and defining a sealing channel therebetween, such that upon oscillation of said piston, said working fluid is pumped from said intake port to said outlet port;

a drive mechanism comprising:

a power transfer shaft rotatably responsive to a drive source;

a tubular passageway extending from a space adjacent said drive mechanism to said working fluid region such that said piston is contained in the portion of said tubular passageway in said working fluid region;

at least one piston rod pivotally coupled at a first end to said power transfer shaft and at a second end to said piston, said piston rod configured to impart an oscillating motion to said piston; and

a lubricating fluid region coupled to at least said drive mechanism, said lubricating fluid region comprising:

a lubricant sump disposed adjacent said power transfer shaft and configured to contain at least a portion of said lubricant; and

a lubricant pumping device fluidly coupled to said lubricant sump; and

a sealing fluid distribution network configured to transport a sealing fluid from said lubricating fluid region to said sealing channel.

28. A piston pump according to claim 27, wherein said sealing fluid distribution network comprises a lubricant flowpath disposed within said piston and piston rod such that fluid communication is established therebetween.

29. A piston pump according to claim 28, wherein said flowpath terminates along a radial surface of said piston such that sealing fluid routed through said sealing fluid distribution network can affect sealing and lubrication in said sealing channel.

30. A piston pump according to claim 28, wherein said piston further comprises at least one circumferential groove, said groove in fluid communication with said lubricant flowpath.

31. A piston pump according to claim 30, wherein an axial passage is disposed between said circumferential groove and said lubricant flowpath such that lubricant can be conveyed from said lubricant flowpath to said circumferential groove.

32. A piston pump according to claim 27, wherein said sealing fluid distribution network comprises said piston, a scraper ring coupled to said piston, and said tubular passageway in said working fluid region, said scraper ring configured to traverse said sealing channel upon said oscillation of said piston within said tubular passageway.

33. A piston pump according to claim 32, wherein said scraper ring is defined by a taper on its outer surface to preferentially allow sealing fluid migration into said pumping chamber while inhibiting working fluid migration out of said pumping chamber.

34. A piston pump according to claim 27, wherein said sealing fluid distribution network is configured such that the pressure of said sealing fluid flowing through said sealing channel is sufficient to ensure that the net flow of fluid between said pumping chamber and said lubricating fluid region during each oscillating piston cycle is toward said pumping chamber.

35. A piston pump according to claim 27, wherein each of said intake and outlet ports include a check valve disposed therein.

36. A micro combined heat and power system comprising:

a working fluid circuit configured to transport a working fluid, said working fluid circuit comprising:

an evaporator configured to convert said working fluid from a subcooled liquid into a superheated vapor;

an expander in fluid communication with said evaporator, said expander including a first lubricant sump;

a condenser in fluid communication with said expander; and

a working fluid feed pump comprising:

at least one working fluid region comprising:

an intake port configured to receive said working fluid;

an outlet port configured to dispense said working fluid, and

a piston disposed between said intake and outlet ports such that upon oscillation of said piston, said working fluid is pumped from said intake port to said outlet port;

a drive mechanism comprising:

a power transfer shaft rotatably responsive to a drive source;

a tubular passageway extending from a space adjacent said power transfer shaft to said working fluid region such that said piston is contained in the portion of said tubular passageway in said working fluid region;

a crosshead slidably disposed in said tubular passageway, said crosshead pivotally connected to said power transfer shaft; and

at least one piston rod connected at a first end to said crosshead and at a second end to said piston, said piston rod configured to impart an oscillating motion to said piston;

a lubricating fluid region coupled to at least said drive mechanism, said lubricating fluid region comprising:

a second lubricant sump disposed adjacent said power transfer shaft and configured to contain at least a portion of said lubricant;

a lubricant reservoir in fluid communication with said second lubricant sump; and

a lubricant pumping device fluidly coupled to said second lubricant sump; and

at least one seal disposed in said tubular passageway, said seal defining a boundary between said working fluid region and said lubricating fluid region; and

at least one energy conversion circuit operatively responsive to said working fluid circuit such that upon operation of said system, said at least one energy conversion circuit is configured to provide useable energy.

37. A micro combined heat and power system according to claim 36, wherein said lubricant pumping device comprises a high pressure vapor source fluidly coupled to said lubricant sump.

38. A micro combined heat and power system according to claim 37, wherein said expander is said high pressure vapor source.

39. A micro combined heat and power system according to claim 38, further comprising a jet pump disposed in a flowpath fluidly coupled to said expander so that high pressure vapor in said flowpath draws lubricant into a low pressure region within said jet pump for mixing between said vapor and said lubricant such that upon mixing the fluids can be used elsewhere.

40. A micro combined heat and power system according to claim 36, wherein said lubricant pumping device is a separately-powered oil transfer pump fluidly connected between said expander and said second lubricant sump.

41. A micro combined heat and power system according to claim 40, wherein said oil transfer pump is configured to move said lubricant from said second lubricant sump to said expander.

42. A micro combined heat and power system according to claim 40, wherein said oil transfer pump is configured to move said lubricant from said first lubricant sump to said second lubricant sump at least during periods of system operation.

43. A micro combined heat and power system according to claim 42, wherein said oil transfer pump is configured to maintain said second lubrication sump substantially full of lubricant at least during periods of system operation.

44. A micro combined heat and power system according to claim 43, further comprising a pressure relief valve disposed between said first lubricant sump and said second lubricant sump.

45. A micro combined heat and power system according to claim 36, wherein said expander is a scroll expander comprising a working fluid inlet, a working fluid outlet, an orbiting involute spiral wrap, a stationary involute spiral wrap and a working fluid outlet.

46. A micro combined heat and power system according to claim 40, further including a vapor line extending from said second lubricant sump to said condenser.

47. A micro combined heat and power system according to claim 36, wherein said lubricant reservoir is fluidly coupled to said first lubricant sump to receive lubricant that has been separated out of said expander.

48. A micro combined heat and power system according to claim 36, wherein said lubricant pumping device comprises:

a lubricant inlet channel configured to receive lubricant from at least one of said first or second lubricant sumps or said lubricant reservoir;

an inlet check valve disposed in said lubricant inlet channel;

a lubricant outlet channel;

an outlet check valve disposed in said lubricant outlet channel; and

a variable volume pumping cavity at least partially disposed in said tubular passageway, said cavity in fluid communication with said lubricant inlet channel and said lubricant outlet channel, said cavity defined at a first end by said crosshead such that upon reciprocating motion of said crosshead, said lubricant introduced into said cavity through said lubricant inlet channel becomes pressurized and exits through said lubricant outlet channel.

49. A micro combined heat and power system according to claim 36, wherein said working fluid feed pump further comprises:

a motor configured to provide power to said pump; and

a housing comprising:

a first compartment configured to contain said motor;

a second compartment configured to contain at least said power transfer shaft and said second lubricant sump;

a coupling extending from said motor to said power transfer shaft;

a vapor space seal disposed about said coupling and defining a boundary between said first and second compartments; and

a lubricant drain line fluidly connected between said first compartment and said first lubricant sump.

50. A micro combined heat and power system according to claim 49, further comprising a lubricant return line that extends from said second compartment to said first lubricant sump such that, in conjunction with said oil transfer pump, a continuous loop is formed therebetween.

51. A micro combined heat and power system according to claim 50, wherein said second compartment is situated below said first compartment such that any lubricant present in said first compartment will collect along a lower surface formed in part by said vapor space seal.

52. A micro combined heat and power system according to claim 50, wherein said first lubricant sump is configured such that a lubricant fluid level therein is situated in a lower vertical elevation than a lubricant fluid level in said first and second compartments.

53. A micro combined heat and power system according to claim 50, wherein said lubricant drain line is spaced adjacent said vapor space seal such that at least one of said organic working fluid and said lubricant collecting therealong can flow through said lubricant drain line to said first lubricant sump.

54. A micro combined heat and power system according to claim 49, wherein said first compartment further comprises a heating element disposed therein, said heating element configured to maintain the temperature in said first compartment above the saturation temperature of said working fluid.

55. A micro combined heat and power system according to claim 36, further comprising a sealing fluid distribution network configured to maintain a sealing fluid between said piston and a complementary surface in said working fluid region.

56. A micro combined heat and power system according to claim 55, wherein said sealing fluid distribution network comprises said piston, a scraper ring coupled to said piston, and said tubular passageway in said working fluid region, said scraper ring configured to traverse said sealing channel upon said oscillation of said piston within said tubular passageway.

57. A piston pump according to claim 56, wherein said scraper ring is defined by a taper on its outer surface to preferentially allow sealing fluid migration into said pumping chamber while inhibiting working fluid migration out of said pumping chamber.

58. A micro combined heat and power system according to claim 55, wherein said sealing fluid distribution network comprises a lubricant flowpath disposed within said piston and piston rod such that fluid communication is established therebetween.

59. A micro combined heat and power system according to claim 57, said sealing fluid distribution network is configured such that the pressure of said sealing fluid flowing through said sealing channel is sufficient to ensure that the net flow of fluid between said pumping chamber and said lubricating fluid region during each oscillating piston cycle is toward said pumping chamber.

60. A method of operating a piston pump, said method comprising:

configuring said pump to comprise:

at least one working fluid region comprising:

an intake port configured to receive a working fluid;

an outlet port configured to dispense said working fluid, and

a piston disposed between said intake and outlet ports such that upon oscillation of said piston, said working fluid is pumped from said intake port to said outlet port;

a drive mechanism comprising:

a power transfer shaft rotatably responsive to a drive source;

a tubular passageway adjacent said power transfer shaft;

a crosshead slidably disposed in said tubular passageway, said crosshead pivotally connected to said power transfer shaft; and

at least one piston rod connected at a first end to said crosshead and at a second end to said piston, said piston rod configured to impart an oscillating motion to said piston;

a lubricating fluid region coupled to at least said drive mechanism, said lubricating fluid region comprising:

a lubricant sump disposed adjacent said power transfer shaft and configured to contain at least a portion of a lubricating fluid;

a lubricant reservoir in fluid communication with said lubricant sump; and

a lubricant pumping device fluidly coupled to said lubricant sump; and

at least one seal disposed in said tubular passageway, said seal defining a boundary between said working fluid region and said lubricating fluid region;

connecting said intake port and said outlet port to a supply of said working fluid;

introducing said working fluid to said intake port;

activating said drive source so that said piston moves at least a portion of said working fluid from said intake port to said outlet port; and

maintaining a sufficient quantity of said lubricating fluid in said lubricant reservoir to ensure that the side of said seal that is adjacent said lubricant reservoir is exposed to a substantially vapor-free environment.

61. A method according to claim 60, wherein said lubricant pumping device is a separate oil transfer pump placed in fluid communication with said lubricant sump.

62. A method according to claim 60, comprising the additional step of configuring a sealing fluid distribution network to provide sealing fluid to a sealing channel disposed between said piston and a complementary surface in said working fluid region.

63. A method according to claim 62, wherein said sealing fluid distribution network comprises a flowpath defined in said piston and said piston rod to establish fluid communication between said lubricant sump and said sealing channel such that a sealing fluid may be introduced into said sealing channel through said flowpath.

64. A method according to claim 62, wherein said sealing fluid distribution network comprises said piston, a scraper ring coupled to said piston, and said complementary surface in said working fluid region, said scraper ring configured to traverse said sealing channel upon said oscillation of said piston within said complementary surface in said working fluid region.

65. A method according to claim 61, wherein said step of configuring said pump further comprises:

providing a motor configured to provide power to said pump;

providing a first compartment to contain said motor;

providing a second compartment configured to contain at least said power transfer shaft and said second lubricant sump;

extending a coupling from said motor to said power transfer shaft;

establishing a vapor space seal disposed about said coupling such that a boundary is formed between said first and second compartments.

66. A method according to claim 65, wherein said step of configuring said pump further comprises:

connecting a lubricant drain line adjacent said vapor space seal such that lubricant collecting therealong can flow through said lubricant drain line and out of said first compartment; and

connecting a lubricant return line to said second compartment such that excess of said lubricant collecting therein can flow through said lubricant return line and out of said second compartment.

67. A method according to claim 66, wherein said step of configuring said pump further comprises activating a heating element disposed in said first compartment so that the temperature in said first compartment is maintained above the saturation temperature of said working fluid.

68. A method according to claim 67, comprising the additional step of operating said oil transfer pump such that at least a portion of said lubricant flowing in at least one of said lubricant drain line or said lubricant return line is moved to said lubricant sump.

69. A method according to claim 68, wherein said step of operating said oil transfer pump substantially fills said lubricant sump.

70. A method of operating a piston pump, said method comprising:

configuring said pump to comprise:

at least one working fluid region comprising:

an intake port configured to receive a working fluid;

an outlet port configured to dispense said working fluid, and

a piston disposed between said intake and outlet ports such that upon oscillation of said piston, said working fluid is pumped from said intake port to said outlet port;

a drive mechanism comprising:

a power transfer shaft rotatably responsive to a drive source;

a tubular passageway adjacent said power transfer shaft;

a crosshead slidably disposed in said tubular passageway, said crosshead pivotally connected to said power transfer shaft; and

at least one piston rod connected at a first end to said crosshead and at a second end to said piston, said piston rod configured to impart an oscillating motion to said piston;

a lubricating fluid region coupled to at least said drive mechanism, said lubricating fluid region comprising:

a lubricant sump disposed adjacent said power transfer shaft and configured to contain at least a portion of a lubricating fluid;

a lubricant reservoir in fluid communication with said lubricant sump; and

a lubricant pumping device fluidly coupled to said lubricant sump; and

at least one seal disposed in said tubular passageway, said seal defining a boundary between said working fluid region and said lubricating fluid region;

connecting said intake port and said outlet port to a supply of said working fluid;

introducing said working fluid to said intake port;

activating said drive source so that said piston moves at least a portion of said working fluid from said intake port to said outlet port; and

increasing the pressure of said lubricating fluid at said boundary above that of the lubricating fluid remaining in said sump.

71. A method according to claim 70, wherein said increased lubricant pressure at said boundary is effected by configuring said lubricant pumping device to comprise:

a lubricant inlet channel configured to receive lubricant from at least one of said lubricant sump and said lubricant reservoir;

an inlet check valve disposed in said lubricant inlet channel;

a lubricant outlet channel;

an outlet check valve disposed in said lubricant outlet channel; and

a variable volume pumping cavity at least partially disposed in said tubular passageway, said cavity in fluid communication with said lubricant inlet channel and said lubricant outlet channel, said cavity defined at a first end by said crosshead such that upon oscillating motion of said crosshead, said lubricant introduced into said cavity through said lubricant inlet channel becomes pressurized and exits through said lubricant outlet channel.

72. A method according to claim 70, wherein said increased lubricant pressure at said boundary is effected by the additional steps of:

configuring said lubricant pumping device as a separate oil transfer pump; and

operating said separate oil transfer pump to pressurize said lubricant reservoir more than the remainder of said lubricating fluid region.

73. A method of operating a micro combined heat and power system, said method comprising:

configuring a working fluid circuit to transport a working fluid, said working fluid circuit comprising:

an evaporator configured to convert said working fluid from a subcooled liquid into a superheated vapor;

an expander in fluid communication with said evaporator, said expander including a first lubricant sump; and

a condenser in fluid communication with said expander; and

a working fluid feed pump comprising:

at least one working fluid region with an intake port configured to receive a working fluid, an outlet port configured to dispense said working fluid, and a piston disposed between said intake and outlet ports such that upon oscillation of said piston, said working fluid is pumped from said intake port to said outlet port;

a drive mechanism with a power transfer shaft rotatably responsive to a drive source, a tubular passageway adjacent said power transfer shaft, a crosshead slidably disposed in said tubular passageway, said crosshead connected to said power transfer shaft, and at least one piston rod connected at a first end to said crosshead and at a second end to said piston, said piston rod configured to impart an oscillating motion to said piston;

a lubricating fluid region with a second lubricant sump disposed adjacent said power transfer shaft and configured to contain at least a portion of a lubricating fluid, and a lubricant pumping device fluidly coupled to said second lubricant sump; and

at least one seal disposed in said tubular passageway, said seal defining a boundary between said working fluid region and said lubricating fluid region;

fluidly connecting said intake port to said condenser;

fluidly connecting said outlet port to said evaporator;

starting said system such that said working fluid adjacent said evaporator is converted into superheated vapor, expanded in said expander, cooled in said condenser, and pumped by said pump back to said evaporator in a continuous loop; and

maintaining a sufficient quantity of said lubricating fluid in said lubricant reservoir to ensure that the side of said seal that is adjacent said lubricant reservoir is exposed to a substantially vapor-free environment.

74. A method according to claim 73, comprising the additional step of configuring said lubricant pumping device to comprise:

a lubricant inlet channel to receive lubricant from at least one of said first or second lubricant sumps or said lubricant reservoir;

an inlet check valve disposed in said lubricant inlet channel;

a lubricant outlet channel;

an outlet check valve disposed in said lubricant outlet channel; and

a variable volume pumping cavity at least partially disposed in said tubular passageway, said cavity in fluid communication with said lubricant inlet channel and said lubricant outlet channel, said cavity defined at a first end by said crosshead such that upon reciprocating motion of said crosshead, said lubricant introduced into said cavity through said lubricant inlet channel becomes pressurized and exits through said lubricant outlet channel.

75. A method according to claim 73, wherein said step of configuring said working fluid circuit further comprises incorporating a separate oil transfer pump as said lubricant pumping device.

76. A method according to claim 73, comprising the additional step of introducing said lubricating fluid into a sealing channel disposed between said piston and said generally cylindrical passageway.

77. A method according to claim 76, wherein said step of introducing said lubricating fluid comprises the additional step of configuring a sealing fluid distribution network to transport a sealing fluid from said lubricating fluid region to said sealing channel.

78. A method according to claim 77, wherein said sealing fluid distribution network comprises a lubricant flowpath disposed within said piston and piston rod such that fluid communication is established therebetween.

79. A method according to claim 73, wherein said step of configuring said pump further comprises:

providing a motor configured to provide power to said pump;

providing a first compartment to contain said motor;

providing a second compartment configured to contain at least said power transfer shaft and said second lubricant sump;

extending a coupling from said motor to said second compartment;

establishing a vapor space seal disposed about said coupling; and

defining a boundary between said first and second compartments such that said lubricant is substantially contained in said second compartment.

80. A method according to claim 79, wherein said step of configuring said pump further comprises:

fluidly coupling a lubricant drain line between said first compartment and said first lubricant sump, said lubricant drain line spaced adjacent said vapor space seal such that lubricant collecting therealong can flow through said lubricant drain line to said first lubricant sump; and

fluidly coupling a lubricant return line between said second compartment and said first lubricant sump.

81. A method according to claim 80, comprising the additional step of heating said first compartment with a heating element such that the temperature in said first compartment is maintained above the saturation temperature of said fluid to be pumped.

82. A method according to claim 75, wherein said step of operating said oil transfer pump occurs independent of operation of said micro combined heat and power system.

83. A method according to claim 73, comprising the additional step of pressurizing said lubricating fluid with high pressure vapor that has exited said evaporator.

84. A method according to claim 83, wherein said step of pressurizing said lubricating fluid is accomplished a device that comprises:

a lubricant pressurization chamber fluidly coupled to said lubricant sump, said pressurization chamber including at least one check valve; and

a flow regulating device configured to intermittently allow the transport of fluid contained in said lubricant pressurization chamber to at least one of said working fluid region and said lubricating fluid region.

85. A method according to claim 84, wherein said flow regulating device is a time-responsive valve.

86. A method according to claim 84, wherein said step of pressurizing said lubricating fluid is accomplished with a jet pump configured to inject said lubricating fluid into a flow of said high pressure vapor.