Apparatus for converting thermal energy

Abstract

In an apparatus for converting thermal energy from a heat source into mechanical energy by means of a thermodynamic cycle using a working medium which is guided in the cycle and in that context experiences a changing pressure, wherein a saturated steam temperature value of the working medium is associated with the respective pressure, and an expansion device for expanding the working medium from an elevated pressure to a lower pressure, wherein after expansion to the lower pressure the working medium has a waste steam temperature, there is provided an adjustment device for setting the waste steam temperature to a defined waste steam temperature value above the saturated steam temperature value associated with the lower pressure.

Description

TECHNICAL FIELD

The disclosure concerns an apparatus for converting thermal energy from a heat source into mechanical energy by means of a thermodynamic cycle using a working medium. Furthermore, the disclosure relates to a corresponding method for converting thermal energy into mechanical energy.

BACKGROUND

Generic apparatuses and methods are used to generate electrical energy from thermal energy in what is known as power generation by heat. As a thermodynamic cycle, a Clausius-Rankine cycle is usually carried out, which is widely used in steam power plants with water as a working medium. The water is heated to about 600° C. by means of high temperature heat sources such as coal, natural gas, petroleum and nuclear energy. If an organic working medium is used instead of water, this is called the ORC process (Organic Rankine Cycle). Organic working media can boil at a far lower temperature than water and evaporate at lower temperatures. Therefore, ORC processes are used to recover thermal energy from low temperature heat sources that have temperatures of 60° C. to 200° C. Such heat sources are solar thermal or geothermal sources and waste heat from engines, industrial production processes and biogas plants. They can only be used insufficiently with conventional apparatuses and methods.

In a thermodynamic cycle, the working medium undergoes periodic changes in its thermodynamic state variables such as temperature and pressure. Depending on the change in the state variables, energy can be absorbed by the working medium from the environment or emitted into the environment. In this case, the working medium therefore experiences a changing pressure. It is first placed under an elevated pressure as a liquid working medium and then evaporated and superheated by means of transferring thermal energy from the heat source. The result is a high-energy compressed working medium vapor, which can again emit its absorbed energy during expansion from the elevated pressure to a lower pressure by means of an expansion device. The emitted energy can drive a generator to generate electrical energy in the form of mechanical energy.

After the expansion or the expansion process, the working medium vapor in the form of exhaust vapor often has a proportion of liquid working medium. This proportion of liquid working medium lowers the efficiency and service life of many expansion devices. A major reason for this is that most expansion devices, such as positive displacement machines and in particular rotary vane expanders, usually require oil lubrication with a lubricating oil. By means of the lubricating oil, friction between moving parts of the expansion device can be kept low and leak gaps can be sealed in an expansion chamber carrying the working medium. If, on the other hand, the lubricating oil accumulates with the proportion of liquid working medium, then the lubricating properties and sealing capabilities of the lubricating oil decrease. Lower lubricating properties increase wear on the moving parts. Lower sealing capabilities lead to a higher leakage of the working medium in the expansion device and therefore to a lower efficiency. Furthermore, an additional heating energy for a subsequent thermal expulsion of liquid working medium from a recirculated lubricating oil is necessary, which further reduces the efficiency.

SUMMARY

The problem addressed by the disclosure is that of providing an apparatus and method for a thermodynamic cycle using a working medium for the conversion of thermal energy. In this case, the thermodynamic cycle is intended to be optimized, especially in terms of the service life and efficiency of the expansion device and the expansion process.

This problem is solved by an apparatus for converting thermal energy from a heat source into mechanical energy by means of a thermodynamic cycle using a working medium which is carried in the cycle and in the process experiences a changing pressure, wherein a saturated vapor temperature value of the working medium is associated with the particular pressure in each case, and an expansion device for expanding the working medium from an elevated pressure to a lower pressure, wherein, after expansion to the lower pressure, the working medium has an exhaust vapor temperature. In this case, an adjustment device is provided for adjusting the exhaust vapor temperature to a defined exhaust vapor temperature value above the saturated vapor temperature associated with the lower pressure.

By means of the apparatus, the working medium carried in the cycle experiences a changing pressure, which is in particular subject to periodic changes. In this case, a saturated vapor temperature value of the working medium is associated with each pressure experienced by the working medium. The saturated vapor temperature value is the temperature value at which liquid working medium is in equilibrium with gaseous working medium. It depends on the particular pressure in each case, which is called the saturated vapor pressure value. The dependency on the saturated vapor pressure value and the saturated vapor temperature value can be represented in a vapor curve as a phase boundary line between the liquid and gaseous working medium. The vapor curve is specific to each working medium.

If the working medium has a temperature below the saturated vapor temperature value of the particular pressure currently experienced thereby, then the working medium is liquid. If the working medium has a temperature above the saturated vapor temperature value of the particular pressure, then the working medium is gaseous. When cooling the gaseous working medium, first condensation drops of the working medium are formed once the saturated vapor temperature value is reached.

By means of the expansion device, the working medium carried in the cycle shall be expanded from an elevated pressure to a lower pressure. During expansion, not only does the pressure of the working medium decrease to the lower pressure, but the temperature of the working medium also decreases. The temperature of the working medium after expanding to the lower pressure is referred to as the exhaust vapor temperature.

An adjustment device is provided by means of which this exhaust vapor temperature can be adjusted to a defined exhaust vapor temperature value above the saturated vapor temperature value associated with the lower pressure. By means of such an adjustment device, the exhaust vapor temperature value of the working medium can be adjusted specifically so as to be above the saturated vapor temperature value associated with the lower pressure. The working medium which has an exhaust vapor temperature value above the saturated vapor temperature is gaseous. The working medium can be reliably prevented from condensing from its gaseous state to its liquid state during and after expansion. Thus, a consistently condensate-free working medium vapor is achieved without a proportion of liquid working medium in the associated expansion device. Lubricant which is provided in and on the expansion device and is usually liquid, such as in particular a lubricating oil, cannot be contaminated with liquid working medium. The lubricant that is therefore kept clean reliably prevents friction between movable components of the expansion device and reliably seals the expansion chamber from leakage of working medium. In addition, a subsequent heating to expel an otherwise occurring liquid working medium in the usually recirculated lubricant is not necessary. Thus, both the efficiency and the service life of the expansion device of the disclosed apparatus are significantly improved by comparison with conventional devices of this type.

The solution according to the invention is initially surprising, since additional components and additional energy expenditure are required for the adjustment device. In addition, there is a higher exhaust vapor temperature value by comparison with conventional devices of this type. Such a higher exhaust vapor temperature value results in an energy loss. A relatively small amount of energy can be released during the expansion, which can be reused as mechanical energy. According to the invention, however, it has surprisingly been found that the advantage of the consistently condensate-free working medium vapor in the expansion device far outweighs the additional energy expenditure and the resulting energy loss.

Furthermore, with the solution according to the invention, the gaseous working medium can be prevented from condensing after expansion independently of a wide range of external and internal conditions of the thermodynamic cycle. No matter what thermal energy the heat source has and no matter what temperature and pressure the working medium has on entering the expansion device, the exhaust vapor temperature value of the working medium is always adjusted so as to be above the saturated vapor temperature value associated with the lower pressure. Therefore, the exhaust vapor temperature value is defined as a function of the lower pressure, which may vary depending on the inlet temperature and inlet pressure of the working medium in the expansion device. The inlet temperature and the inlet pressure are often dependent on the thermal energy of the heat source. In addition, the exhaust vapor temperature value is defined as a function of the saturated vapor temperature value associated with the lower pressure. This saturated vapor temperature value is specific to each working medium, so that the gaseous working medium can also always be reliably prevented from condensing after expansion, regardless of the type of working medium.

The defined exhaust vapor temperature value is preferably kept constant above the saturated vapor temperature value associated with the lower pressure. With the exhaust vapor temperature value kept constant in this way, the expansion and condensation following the expansion in the cycle can be carried out particularly uniformly without large temperature fluctuations. In particular, only a small amount of internal friction losses in the working medium and a small amount of external friction losses occur with respect to a line carrying the working medium. Otherwise occurring energy losses can be reduced.

Advantageously, the defined exhaust vapor temperature value is between 2 K and 12 K, preferably between 4 K and 8 K, and particularly preferably between 5 K and 6 K above the saturated vapor temperature value associated with the lower pressure. It has been found that even such a small difference between the exhaust vapor temperature value and the relevant saturated vapor temperature value is sufficient to reliably prevent the working medium vapor from condensing during expansion to the lower pressure. For a larger difference, a higher exhaust vapor temperature value would have to be set, which would cause unnecessary energy loss.

Furthermore, it is advantageous to increase a temperature of the working medium by means of the adjustment device such that the exhaust vapor temperature has the defined exhaust vapor temperature value above the saturated vapor temperature value associated with the lower pressure. Such a temperature increase is easy to carry out.

As is known, the working medium carried in a thermodynamic cycle in its liquid state is shall be transferred from a lower pressure to an elevated pressure. Thereafter, the working medium placed under the elevated pressure shall be isobarically evaporated and superheated. The temperature of the working medium increases in the process. When the compressed and superheated working medium vapor expands to the lower pressure, the temperature of the working medium vapor drops to the exhaust vapor temperature.

The temperature of the working medium carried in the cycle shall now preferably be increased by means of the adjustment device after evaporation and before or during expansion such that the exhaust vapor temperature then has the defined exhaust vapor temperature value above the saturated vapor temperature value associated with the lower pressure.

The temperature of the working medium within the expansion device shall be particularly preferably increased by means of the adjustment device. Thus, the temperature during the expansion process can be increased, which is more energy efficient than a temperature increase of the superheated working medium vapor before expansion. In particular, the temperature of the working medium shall be increased in this case toward the end of the expansion process. Toward the end of the expansion process, the temperature of the expanding working medium vapor is lower than at the beginning or in the middle of the expansion process. Therefore, the temperature of the working medium can be increased in an energy-efficient manner from a relatively low temperature to the required temperature value, at which the defined exhaust vapor temperature value should be achieved after expansion.

Furthermore, the adjustment device advantageously comprises a vapor supply for supplying vapor to the working medium, wherein the vapor is in particular superheated vapor. Vapor molecules which form the vapor move quickly and transmit their movement in a collision correspondingly fast to the working medium vapor molecules, which increases the temperature of the working medium vapor correspondingly fast. In addition, depending on the temperature and amount of vapor to be supplied, the temperature of the working medium vapor can be adjusted in a very purposeful way to the defined exhaust vapor temperature value. If the vapor is overheated, the temperature increase is even faster.

The vapor supply is preferably adapted to supply the vapor to the expansion device, in particular after supplying the working medium vapor carried in the cycle to the expansion device. This allows the temperature of the working medium vapor to be increased during expansion in an energy-efficient manner. A vapor supply leading into the expansion device preferably toward the end of expansion is particularly energy-efficient in accordance with the embodiments described above.

In addition, the vapor supply to the expansion device has the advantage that the vapor supplied can expand as additional vapor. This results in additional expansion capacity of the additional vapor, which can be delivered to the expansion device in the form of additional mechanical power. Higher power and associated higher efficiency of the expansion device can be achieved, which increases the efficiency of the entire apparatus.

Furthermore, the vapor is advantageously a vapor of the working medium. Therefore, despite the supply of additional vapor, the working medium remains a pure working medium that is not contaminated with the vapor of another medium. Preferably, the vapor of the working medium comes from the same cycle as the working medium vapor itself, which is to be conducted to the expansion device at the beginning of expansion. Only a single vapor generation process is then required so as to save on energy and components, and as a result of which thermal energy can be transferred from the heat source particularly efficiently.

The expansion device is advantageously designed as a positive displacement machine for passing the working medium through at least one expansion chamber or volume chamber which increases in size when said medium passes therethrough. In this case, an inlet for introducing the working medium vapor placed under the elevated pressure is provided in the expansion chamber. The introduced working medium vapor then displaces a component that delimits the expansion chamber. This increases the size of the expansion chamber and at the same time moves the component to perform mechanical work. Increasing the size of the expansion chamber causes expansion of the working medium vapor from the elevated pressure to the lower pressure.

In such a positive displacement machine, the working medium vapor can be carried through the inlet and the additional vapor through a vapor supply positioned between the inlet and the outlet in the expansion chamber. In this case, the working medium vapor can expand when passing through the expansion chamber which is increasing in size and can be reheated by means of the supplied vapor through the expansion chamber increasing in size. Along with the supplied vapor, the reheated working medium vapor may continue to expand toward the outlet.

The vapor supply of such a positive displacement machine can be designed in a particularly purposeful way to comprise two or more expansion chambers. The vapor supply may in this case be designed such that additional vapor is to be conducted to the expansion chamber in a targeted manner when the expansion chamber has reached a desired size. According to this size, there is then correspondingly expanded and cooled working medium vapor, which can then be heated in a targeted manner. The heated working medium vapor can then expand further in the expansion chamber that continues to increase in size until an outlet is reached in the expansion chamber, from which the working medium vapor and the additional vapor can escape. In this case, at least the inlet for the working medium vapor is arranged spatially far enough away from the vapor supply that an expansion chamber located at the inlet is spatially separate from an expansion chamber located at the vapor supply. Preferably, the outlet is arranged spatially far enough away from the vapor supply that an expansion chamber located at the outlet is spatially separate from the expansion chamber located at the vapor supply. This allows for a particularly purposeful increase in temperature during expansion in a defined expansion zone. The defined expansion zone corresponds to the size of the expansion chamber at the vapor supply.

In addition, a counterpressure shall be generated on the working medium in an advantageous manner by means of the adjustment device in such a way that the exhaust vapor temperature has the defined exhaust vapor temperature value above the saturated vapor temperature value associated with the lower pressure. A structure with such a counterpressure is particularly energy-efficient.

With this kind of counterpressure, the lower pressure is not reached at first during expansion. Instead, a lower pressure increased according to the counterpressure is reached. The increased lower pressure is associated with a correspondingly increased saturated vapor temperature value of the working medium. By means of the counterpressure, the working medium vapor is initially kept at the increased lower pressure and has an exhaust vapor temperature which corresponds to this increased saturated vapor temperature value. Upon further expansion, the lower pressure increased according to the counterpressure shall then be expanded to the lower pressure. After the remaining expansion, the working medium vapor has an exhaust vapor temperature that corresponds to the defined exhaust vapor temperature value above the saturated vapor temperature value associated with the lower pressure. The working medium vapor is reliably prevented from condensing throughout the entire expansion process.

For this purpose, an expansion device is preferably provided for expanding the working medium from an elevated pressure to a lower pressure, in which the lower pressure is to be achieved by means of a two-stage expansion process. The elevated pressure is to be expanded in a first expansion stage, first by means of the generation or build-up of counterpressure, to a first lower pressure. Thereafter, the first lower pressure is to be expanded in a second expansion stage to a second lower pressure, the second lower pressure corresponding to the above-mentioned lower pressure after expansion.

In this case, the first and the second expansion stages can take place in a single expansion device. Particularly preferably, the first expansion stage is to be carried out in a first expansion unit and the second expansion stage is to be carried out separately in a second expansion unit. The first expansion unit is designed in particular having a positive displacement machine and the second expansion unit is designed in a structurally simple manner to be a line element within a line carrying the working medium. The first and second expansion units then constitute the expansion device as a whole.

In addition, the adjustment device advantageously comprises a blocking element for generating the counterpressure on the working medium, which blocking element is designed in particular having a valve for selectively opening and closing a line carrying the working medium. By means of the blocking element, a working medium flow of the working medium carried in the cycle can be shut off in a structurally particularly simple and rapid manner. After this kind of shut-off, the desired counterpressure builds up on the working medium. The counterpressure can be relieved again with short reaction times when needed, by the blocking element being designed having a valve that can be easily opened again.

Preferably, the blocking element is arranged within the expansion device between the first and second expansion units, as a result of which the described two-stage expansion process is made possible.

In addition, advantageously, the working medium is carried in a circulation direction and a condensation device for condensing the expanded working medium is provided downstream of the expansion device in the circulation direction, wherein the adjustment device comprises a temperature measuring element for measuring a temperature of the working medium after expansion and before condensation in the circulation direction and/or a pressure measuring element for measuring the pressure of the working medium after expansion and before condensation in the circulation direction. With this kind of temperature measuring element and/or pressure measuring element, a control device is created by means of which the adjustment device shall be controlled according to the measured temperature and/or the measured pressure. This type of control allows the exhaust vapor temperature to always be reliably adjusted to the desired defined exhaust vapor temperature value as required by means of the adjustment device.

In particular, the temperature measuring element measures the exhaust vapor temperature of the working medium after expansion. The exhaust vapor temperature is also dependent on the temperature of an inlet vapor of the working medium when entering the expansion device. In addition, the temperature of the working medium before condensation or the condensation temperature can be determined. The condensation temperature value corresponds in particular to the saturated vapor temperature value associated with the lower pressure. By means of the pressure measuring element, a currently valid saturated vapor pressure value or condensation pressure value of the working medium can be measured, in particular shortly before condensation, which is dependent on a cooling capacity of the condensation device.

Furthermore, the disclosure is directed to a method for converting thermal energy from a heat source into mechanical energy by means of a thermodynamic cycle using a working medium which is carried in the cycle and in the process experiences a changing pressure, wherein a saturated vapor temperature value of the working medium is associated with the particular pressure in each case, and a step of expanding the working medium from an elevated pressure to a lower pressure, wherein, after expansion to the lower pressure, the working medium has an exhaust vapor temperature. The exhaust vapor temperature is adjusted to a defined exhaust vapor temperature value above the saturated vapor temperature value associated with the lower pressure.

The advantages of such a method are apparent from the advantages already described in the description of the disclosed apparatus.

BRIEF DESCRIPTION OF THE DRAWINGS

In the following, embodiments of a solution are explained in more detail on the basis of the appended schematic drawings, in which:

FIG. 1 is a simplified process diagram of an apparatus for converting thermal energy according to the prior art.

FIG. 2 is a schematic log pressure-enthalpy diagram of the thermodynamic cycle from FIG. 1.

FIG. 3 is a vapor curve of a working medium carried in the cycle.

FIG. 4 shows the detail IV according to FIG. 1 of a first embodiment of an apparatus according to the invention.

FIG. 5 is a schematic log pressure-enthalpy diagram of the thermodynamic cycle from FIG. 4.

FIG. 6 is a cross section of a positive displacement machine of the apparatus according to FIG. 4.

FIG. 7 shows the detail IV according to FIG. 1 of a second embodiment of an apparatus for converting thermal energy.

FIG. 8 is a schematic log pressure-enthalpy diagram of the thermodynamic cycle from FIG. 7.

DETAILED DESCRIPTION

In the figures, an apparatus 10 and an associated method 12 for converting thermal energy from a heat source 14 are shown. The apparatus 10 forms a closed system of a process plant in which a thermodynamic cycle 16 is to be completed by means of a working medium carried in the cycle 16.

The illustrated thermodynamic cycle 16 is a modified Organic Rankine Cycle (ORC) in which the working medium is an organic working medium. In the present case, the working medium is designed having ammonia, preferably anhydrous ammonia (NH₃, R 717) in a concentration of over 99.6% by mass. With such an almost pure ammonia, the physical and thermodynamic properties of ammonia can be exploited without disturbing influences of other substances. Liquid ammonia has, for example, a high evaporation enthalpy, which means that a relatively large amount of energy has to be used to convert ammonia from its liquid state to its gaseous state. This means that a correspondingly high amount of energy can be stored in gaseous ammonia and then converted into mechanical energy during expansion.

Low temperature heat sources are used as the heat source 14. The heat source 14 can be a single heat source 14 or have two different heat sources 14 and 17. In the embodiments shown, two different heat sources are used to generate energy, where heat source 14 has a lower temperature than heat source 17. Heat source 14 is engine waste heat, and heat source 17 is exhaust gas waste heat of an internal combustion engine of a combined heat and power plant.

The working medium is provided in the form of a pressure-liquefied gas in a collecting tank 18 which is part of the cycle 16. In this case, the working medium is under a pressure which represents a lower pressure level of the thermodynamic cycle 16 as a lower pressure 20. Starting from the collecting tank 18, a line 22 carries the working medium in a circulation direction 24 to a pressure increasing device 26. By means of the pressure increasing device 26, the pressure experienced by the working medium shall be increased from the lower pressure 20 to a pressure which represents an upper pressure level of cycle 16 as an elevated pressure 28.

In circulation direction 24, the liquid working medium is then pumped from the pressure increasing device 26 through line 22 to a heat transfer device 30. The heat transfer device 30 comprises a first heat exchanger 32 and a second heat exchanger 34 connected in series. The first heat exchanger 32 is coupled to heat source 14 so as to transmit heat by means of a transfer medium carried through a line 36. Accordingly, the second heat exchanger 34 is coupled to heat source 17 by means of a transfer medium carried through a line 38.

Between the two heat exchangers 32 and 34 there is a separator 40 having a lower region 42 and an upper region 44. In the upper region 44, the liquid working medium is carried by means of line 22. The liquid working medium separates itself from any gaseous working medium present and sinks into the lower region 42. From there, a line 46 carries the liquid working medium separated in this way into the first heat exchanger 32, which serves as a preheater and evaporator. There, the liquid working medium is preheated by transferring thermal energy from the first heat source 14 and is largely evaporated. A working medium vapor generated in this way is a wet vapor. This means that even small drops and finely distributed liquid working medium are present in the gaseous working medium as a condensate portion. The wet vapor is carried out of the first heat exchanger 32 through a line 48 into the upper region 44 of the separator 40. The condensate portion sinks into the lower region 42 and accumulates there as a liquid working medium, whereas only gaseous working medium remains in the upper region 44. A particularly dry gaseous working medium can therefore be produced. The liquid working medium flows from the lower region 42 through line 46 back into the first heat exchanger 32 for reheating.

By means of the separator 40, the lines 22 and 48 leading into its upper region 44 and the line 46 leading out of its lower region 42, evaporation according to a thermosiphon principle is made possible. This principle is based on the fact that, during evaporation in the first heat exchanger 32, the density of the working medium located therein is reduced due to the wet vapor formed. Thus, the wet vapor pushes through line 48 into the separator 40. In addition, the same amount of liquid working medium always flows from the lower region 42 of the separator 40 through line 46 into the heat exchanger 32 as is required for evaporation. In the separator 40 a level controller (not shown) is provided by means of which the pressure increasing device 26 shall be controlled in such a way that only as much working medium is pumped to the first heat exchanger 32 as can also be evaporated.

From the separator 40, the gaseous working medium from the upper region 44 is carried through a line 50 into the second heat exchanger 34. The second heat exchanger 34 serves as a superheater by means of which the gaseous working medium shall be superheated when transferring thermal energy from heat source 17. The superheated working medium vapor is then carried out of the second heat exchanger 34 through a line 52 by means of an inlet valve 54 into an expansion device 56.

By means of the expansion device 56, the superheated working medium vapor shall be expanded from the elevated pressure 28 to the lower pressure 20, at the same time reducing the temperature of the working medium. The energy released in the process is transferred as mechanical energy to the expansion device 56, which serves as the drive unit for a generator 58 coupled to the expansion device 56, so as to generate electrical energy.

In the present case, a further expansion device connected in parallel with the expansion device 56 is provided into which the compressed and superheated working medium vapor is carried by means of an associated further inlet valve. For a better overview, the further expansion device together with its associated components is designated by the same reference numerals as the expansion device 56. With such a parallel connection of the expansion devices 56, a particularly uniform expansion of the superheated working medium vapor without large pulsations is possible over time. In addition, a larger amount of working medium vapor can be expanded if necessary. Thus, overall, a uniform and high output can be drawn from the cycle 16. To improve this effect, more than two expansion devices 56 connected in parallel may be provided.

Downstream of the expansion device 56 in circulation direction 24, the expanded working medium vapor is carried through a line or exhaust vapor line 60 out of the expansion device 56 and conducted through a condensation device 62. By means of the condensation device 62, the expanded working medium vapor is cooled and condensed. The condensed working medium is conducted into the collecting tank 18, which is arranged in line 22 downstream of the condensation device 62 in circulation direction 24. With condensation, the thermodynamic cycle 16 is closed and can be repeated as often as required.

Furthermore, the apparatus 10 has an oil supply circuit 64 having an oil supply line 66, through which an oil shall be carried by means of an associated oil inlet valve 68 into the respectively associated expansion device 56. The oil is used for sealing and lubricating components of the expansion device 56. During the expansion of the working medium vapor, the oil in the expansion device 56 can get into the working medium vapor. For this reason, the expanded working medium vapor together with the oil from each expansion device 56 is carried through the associated exhaust vapor line 60 into an associated oil separator 70. By means of the oil separator 70, the oil shall be separated from the expanded working medium vapor. For this purpose, a separating element 71 is arranged at the top of the oil separator 70 and designed as a mechanical oil separator. The separating element 71 separates the oil as liquid from the expanded working medium vapor as gas mechanically and due to different densities of liquid and gas.

The expanded working medium vapor cleaned in this way is carried out of the oil separator 70 through the exhaust vapor line 60 to the condensation device 62 in the cycle 16.

The separated oil is conducted from each oil separator 70 through an associated oil discharge line 72 into an oil collecting tank 74. In this case, the separated oil may contain a proportion of liquid working medium, which has formed during expansion of the working medium vapor in a conventional manner. To remove this proportion of liquid working medium, an oil heater 76 is provided in the oil collecting tank 74. By means of the oil heater 76, the separated oil is heated until the proportion of liquid working medium is almost completely evaporated or expelled from the oil. Between the oil separator 70 and the condensation device 62 in circulation direction 24, a working medium vapor produced in this way is carried from the oil collecting tank 74 back into the exhaust vapor line 60 and thus into the cycle 16 by means of a vapor line 78.

An oil pump 80 is also arranged in the oil supply line 66, by means of which pump the separated oil cleaned of liquid working medium is carried through the oil supply line 66 again into the expansion device 56. In addition, the oil heater 76 comprises a heating circuit line 82 which carries a heating medium and is coupled to the second heat source 17 so as to transmit heat.

FIG. 2 is a schematic log pressure-enthalpy diagram of the thermodynamic cycle 16 of the method 12 which can be carried out by means of the apparatus 10 according to FIG. 1. In this figure, the logarithm of the pressure 83 is plotted on the axis of ordinates, and the enthalpy 84 is plotted on the axis of abscissas. The illustrated curved line represents a phase boundary line 85 of the working medium. As long as the phase boundary line 85 increases, this is the bubble line at which a transition from saturated liquid working medium to wet vapor takes place. If the phase boundary line 85 falls, it represents the dew line marking a transition from the wet vapor to a saturated working medium vapor. In a transition of this kind, the vapor is also referred to as saturated vapor. An area enclosed by the phase boundary line 85 and the axis of abscissas is a wet vapor region 86 of the working medium, in which working medium vapor as gaseous phase and liquid working medium as liquid phase are present at the same time.

Starting from the liquid working medium which is placed under the lower pressure 18, the working medium is placed under the elevated pressure 28 by means of the pressure increasing device 26 in one method step or step 88 of increasing pressure. Ammonia is adjusted from a lower pressure 18 of about 8.4 bar and a temperature of about 23° C. to an elevated pressure 28 of about 37 bar and a temperature of about 30° C.

All pressure values given here should be understood to be absolute pressure values.

By means of the first heat exchanger 32, in a preheating step 90, the working medium under the elevated pressure 28 is heated isobarically to an evaporation temperature value associated with the elevated pressure 28. For ammonia this value is about 76° C. Subsequently, in an evaporation step 92, the working medium, which is still liquid and preheated to the evaporation temperature value, is isobarically evaporated. During step 92, the main component of the thermal energy is supplied to the working medium. During evaporation, the temperature of the working medium remains the same.

Subsequently, by means of the second heat exchanger 34, in a superheating step 94, the working medium vapor produced in step 92 is isobarically superheated to a final temperature. The final temperature for ammonia is about 120° C.

The working medium vapor superheated in this way is adiabatically expanded as superheated ammonia gas in an expansion step 96 by means of the two expansion devices 56 connected in parallel. Adiabatic means that no heat is exchanged with the environment during expansion. During expansion, the actual conversion of thermal energy into mechanical energy takes place. In this case, the working medium entering expansion device 56 has the elevated pressure 28 as the inlet pressure and the temperature of the superheated working medium vapor as the inlet temperature. The working medium leaving the expansion device 56 then has the lower pressure 20 as the exhaust vapor pressure and an exhaust vapor temperature which is lower than the inlet temperature. Incoming ammonia has the elevated pressure 28 of about 37 bar and the inlet temperature of about 120° C., and outgoing ammonia has the lower pressure 20 of about 8.4 bar and the exhaust vapor temperature of about 23° C. A liquid proportion is contained in the exhaust vapor in the outgoing working medium vapor, since both the inlet temperature and the exhaust vapor temperature are subject to certain tolerances. Even at a slightly lower inlet temperature, condensate forms in the exhaust vapor. The exhaust vapor temperature then reached, i.e. the end point of expansion step 96, is in the wet vapor region 86.

Subsequently, the expanded working medium leaving the expansion device 56 is isobarically condensed in a condensation step 98 by means of the condensation device 62 and thus again reaches its initial state in the cycle 16.

FIG. 3 shows a saturation vapor pressure curve or vapor pressure line or vapor curve 100 of the working medium carried in the cycle 16, in this case the vapor curve 100 of ammonia. In this figure, the pressure is plotted on the axis of ordinates and the temperature is plotted on the axis of abscissas. The curved line represents the vapor curve 100 of the working medium and is the phase boundary line between liquid and gaseous working medium. Accordingly, the vapor curve 100 shows which saturated vapor temperature value is associated with a particular pressure of the working medium at which the gaseous working medium begins to condense. The lower pressure 20 is associated with the saturated vapor temperature value 102, which has a value of 23° C. for ammonia at a lower pressure 20 of 8.4 bar.

FIG. 4 and FIG. 7 show a detail of the apparatus 10 where, in contrast to the apparatus 12 according to FIG. 1, an adjustment device 104 is provided for adjusting the exhaust vapor temperature of the working medium after the expansion step 96. By means of the adjustment device 104, the exhaust vapor temperature is adjusted to a defined exhaust vapor temperature value 106 above the saturated vapor temperature value 102 associated with the lower pressure 20. The defined exhaust vapor temperature value 106 is between 4 K and 8 K above the saturated vapor temperature value 102 associated with the lower pressure 20.

According to FIG. 4, the adjustment device 104 comprises a vapor supply 108 for supplying vapor during the expansion step 96 to each expansion device 56. This type of vapor supply is also referred to as intermediate injection. By means of a vapor supply 108 of this kind, the temperature of the working medium vapor can be increased during expansion in such a way that the exhaust vapor temperature of the working medium has the defined exhaust vapor temperature value 106 after step 96.

For this purpose, the vapor supply 108 is designed having in each case a vapor supply line 110 and an additional inlet valve 112 arranged therein, which lead into the associated expansion device 56 downstream of the inlet valve 54 in circulation direction 24. In addition, the vapor supply line 110 is fluidically connected to line 52. With such a connection, the working medium vapor from line 52, which is superheated by means of the second heat exchanger 34, can be conducted through the additional inlet valve 112 into the expansion device 56. The superheated working medium vapor is conducted into the expansion device 56 at an advanced stage, especially toward the end of the expansion step 96.

In addition, the adjustment device 104 according to FIG. 4 comprises a temperature measuring element 114 associated with each expansion device 56, which element is arranged, after expansion, slightly behind each oil separator 70 in circulation direction 24. With such an arrangement, the exhaust vapor temperature of the working medium can be determined by means of the temperature measuring element 114. In addition, a temperature measuring element 116 arranged slightly ahead of the condensation device 62 in circulation direction 24 and a pressure measuring element 118 arranged slightly ahead of said temperature measuring element are provided.

The pressure measuring element 118 and temperature measuring element 116 associated with the condensation device 62 are each coupled to the temperature measuring element 114 associated with an expansion device 56. For this purpose, the measured values can be transferred to a control device 120 associated with each expansion device 56. The control device 120 then opens and closes the additional inlet valve 112 for supplying vapor to the expansion device 56 according to the measurement result.

For this purpose, a pressure value of the lower pressure 20 that is currently valid in the cycle 16 is measured by the pressure measuring element 118 slightly ahead of the condensation device 62. The lower pressure 20 can vary depending on the inlet pressure value of the elevated pressure 28 into the expansion device 56 and depending on the condensation temperature of the condensation device 62.

According to the measured pressure value of the lower pressure 20, the corresponding currently valid saturated vapor temperature value 102 is obtained according to the vapor curve 100 stored in the control device 120. Depending on the valid saturated vapor temperature value 102, the additional inlet valve 112 is opened by means of the control device 120 until the defined exhaust vapor temperature value 106 is measured by the temperature measuring element 114. Depending on the duration and opening width of the inlet valve 112, a corresponding amount of additional vapor is supplied until the defined exhaust vapor temperature value 106 is reached and, in particular, kept constant.

Alternatively or additionally, the temperature value of the working medium ahead of the condensation device 62 can be determined by the temperature measuring element 116. This measured temperature value corresponds to a currently valid saturated vapor temperature value 102, which depends on a cooling capacity of the condensation device 62. The cooling capacity may vary depending on the temperature of the coolant. In particular, if, in a manner which is particularly simple and cost-effective in terms of construction, the coolant is air from the environment, the cooling capacity is directly dependent on the prevailing outside temperature. Depending on the measured, currently valid saturated vapor temperature value 102, the additional inlet valve 112 is opened by means of the control device 120 until the defined exhaust vapor temperature value 106 is measured by the temperature measuring element 114.

Depending on the measured, currently valid saturated vapor temperature value 102, the corresponding saturated vapor pressure value can be determined according to the vapor curve 100. This saturated vapor pressure value corresponds to the current lower pressure 20.

In FIG. 5, in contrast to the diagram according to FIG. 2, there are additional lines which correspond to the isotherms, i.e. lines of the same temperature. 122 denotes the 20° C. isotherm 122, and 124 denotes the 30° C. isotherm 124. In addition, step 96 shows how the temperature of the working medium increases when superheated working medium vapor is supplied toward the end of expansion by means of the vapor supply 108. When the lower pressure 20 is reached, the working medium has the defined exhaust vapor temperature value 106 above the saturated vapor temperature value 102 associated with the lower pressure 20. This means that the end point of step 96 is relatively far outside the wet vapor region 86, such that a condensate is reliably prevented from occurring in the exhaust vapor. For ammonia, the defined exhaust vapor temperature value 106 has a temperature of about 28° C. and is thus about 5 K above the saturated vapor temperature value 102 of about 23° C. at the lower pressure 20 of about 8.4 bar.

FIG. 6 shows the expansion device 56 which is used in the apparatus 10 according to FIG. 4 and is designed having a rotary valve machine in the form of a positive displacement machine. The rotary valve machine is a rotary piston expander which operates in the opposite manner to a rotary piston compressor and is in this case a rotary vane expander.

Such a rotary vane expander has an annular housing 126 comprising an inlet 128 and an outlet 130. The inlet 128 is used for admitting the working medium vapor under the elevated pressure 28 and the outlet 130 is used for discharging the expanded working medium vapor. In this case, each flow direction of the working medium vapor is indicated by a flow arrow. The annular housing 126 is formed having a cylindrical hollow cylinder whose inner lateral face forms an inner annular wall 132. A rotary piston 134 is mounted in the annular housing 126 eccentrically to the axis of the hollow cylinder so as to be rotatable centrally around a shaft 136. The rotary piston 134 has eight grooves 138 along its longitudinal extension, in each of which a corresponding slide 140 is mounted so that it can be moved radially back and forth.

To delimit the annular housing 126, two opposite delimiting surfaces (not shown) are provided in the axial direction. Together with the rotary piston 134, the inner annular wall 132 and the eight gate valves 140, the two delimiting surfaces define eight cells 142, each having a variable volume 144.

The individual variable volume 144 is formed by the fact that the relevant slide 140 is pressed in a sealing manner against the annular wall 132 in the course of a rotation by effective centrifugal forces. As the rotary piston 134 is eccentrically mounted in the annular housing 126, the distance between the rotary piston 134 and the annular wall 132 varies during the rotational movement. For this reason, the relevant slide 140 is pushed back and forth in the corresponding groove 138 when turning. When the distance increases, the slide 140 is pushed out of the corresponding groove 138 until the maximum distance and thus also the maximum volume of the volume 144 is reached. Then the distance decreases again and, when sliding along the annular wall 132, the slide 140 is pushed from the annular wall 132 into the corresponding groove 138 until the minimum distance and thus also the volume minimum of the volume 144 is reached.

The variable volume 144 increases during the rotational movement from the inlet 128 toward the outlet 130, so that when the working medium vapor under the elevated pressure 28 passes through, this working medium vapor expands. When expanding, the working medium vapor presses against a slide 140 in the direction of rotation, so that the rotational movement is started and maintained. This drives the shaft 136, which in turn drives the generator 58 for generating electric current.

The size of the variable volume 144 of each cell 142 depends on a rotation angle associated with the rotational movement, which angle can be divided into individual successive rotation angle zones. The volume 144 has its minimum volume in a rotation angle zone 146. At the inlet 128, the volume 144 slowly increases in a rotation angle zone 148 during the inflow of the compressed working medium vapor and is expanded to its maximum volume in the rotation angle zone 150. During expansion, the temperature of the working medium vapor drops. Before the maximum volume is reached, superheated working medium vapor is supplied or fed by intermediate injection into each cell 142 through the vapor supply line 110 by means of the vapor supply 108. Due to the working medium vapor fed in by intermediate injection, the temperature of the expanding working medium vapor is raised to such an extent that the exhaust vapor temperature of the working medium vapor exiting through the outlet 130 has the defined exhaust vapor temperature value 106. The working medium vapor reheated in this manner and expanded to the maximum volume then flows out of the outlet 130 in a rotation angle zone 152, except for a small residual volume. The working medium vapor exiting through the outlet 130 of each cell 142 is the working medium vapor introduced through the inlet 128 together with the working medium vapor fed in by intermediate injection. The residual volume remains in the relevant cell 142 and is compressed via the rotation angle zone 146 until compressed working medium vapor flows in again at the inlet 128. This process is repeated periodically.

The expansion ratio, i.e. the ratio between the volume 144 at the inlet 128 and the volume 144 at the outlet 130, is set at from 1:3 to 1:4 and thus is specially adapted to the working medium ammonia.

For sealing and lubricating the radial and axial slide gaps occurring between a particular groove 138 and the corresponding slide 140, the oil supply line 66 is provided for supplying oil (FIG. 4). The oil also specifically seals and lubricates the running surface of the slide 140 along the annular wall 132. When the working medium vapor expands, the oil mixes with the working medium vapor as described above and must be discharged from the expansion device 56 through the exhaust vapor line 60 via the oil separator 70. In the oil separator 70, the oil separates again around the working medium vapor. Since a proportion of liquid working medium is reliably prevented from occurring in the separated oil by means of the apparatuses 10 according to FIG. 4 and FIG. 7, the oil heater 76 otherwise required according to FIG. 1 can be omitted so as to save on cost and energy.

In the apparatus 10 according to FIG. 7, a counterpressure shall be generated on the working medium by means of the adjustment device 104 in such a way that the exhaust vapor temperature of the expanded working medium has the defined exhaust vapor temperature value 106 above the saturated vapor temperature value 102 associated with the lower pressure 20. For this purpose, a valve or exhaust vapor control valve 154 is provided as a blocking element 156 by means of which the exhaust vapor line 60 can be shut off. With this kind of shut-off, pressure relief of the working medium in circulation direction 24 is prevented. The working medium is accumulated in the exhaust vapor line 60 against the circulation direction 24 or the flow direction, as a result of which the desired counterpressure can be generated. By opening the exhaust vapor control valve 154, the counterpressure can be relieved again if necessary.

For controlling the exhaust vapor control valve 154, the adjustment device 104 of the apparatus 10 according to FIG. 7 comprises, after expansion, the temperature measuring element 114 slightly ahead of the exhaust vapor control valve 154 in circulation direction 24. The temperature measuring element 116 is arranged downstream of the exhaust vapor control valve 154 and slightly ahead of the condensation device 62, using which element the currently valid saturated vapor temperature value 102 of the working medium (as described with regard to FIG. 4) can be determined. In addition, the pressure measuring element 118 is provided downstream of the exhaust vapor control valve 154 and slightly ahead of the condensation device 62 in circulation direction 24. By means of the pressure measuring element 118, a pressure value of the lower pressure 20, currently valid in the cycle 16, can be measured slightly ahead of the condensation device 62 according to the comments made with regard to FIG. 4.

The temperature measuring elements 114 and 116 as well as the pressure measuring element 118 are coupled to the control device 120 in order to transmit the measured values, which control device closes or opens the exhaust vapor control valve 154 depending on the measurement result. According to the measured pressure value of the lower pressure 20 and thus the currently valid saturated vapor pressure, the corresponding currently valid saturated vapor temperature value 102 is obtained according to the vapor curve 100 stored in the control device 120. Depending on the valid saturated vapor temperature value 102, the exhaust vapor control valve 154 is closed by means of the control device 120 until the defined exhaust vapor temperature value 106 is measured by the temperature measuring element 114 or 116.

FIG. 8 shows that the exhaust vapor pressure is increased to a first lower pressure 158, which is slightly higher than the lower pressure 20, by means of the exhaust vapor control valve 154. In a first expansion stage 160, the superheated working medium vapor is thus initially expanded to the first lower pressure 158 by means of the expansion device 56. For ammonia, this first lower pressure 158 is about 12 bar. This first lower pressure 158 is associated with a saturated vapor temperature of about 33° C. according to the vapor curve 100.

Downstream of the exhaust vapor control valve 154 in circulation direction 24, the first lower pressure 158 is then expanded further in a second expansion stage 162 to a second lower pressure corresponding to the lower pressure 20. The lower pressure 20 is the condensation pressure of the working medium, i.e. the pressure at which the working medium is condensed in the condensation device 62. FIG. 8 shows that the temperature of the working medium after the further expansion at the lower pressure 20 has the defined exhaust vapor temperature value 106 above the saturated vapor temperature value 102 associated with the lower pressure 20. The end point of step 96 is thus outside the wet vapor region 86, which prevents condensation of the working medium vapor.

In another embodiment not shown, the pressure increasing device 26 is designed having a vapor pump. The vapor pump is used to increase the pressure on the working medium under the influence of vapor on the working medium. For this purpose, the vapor pump is coupled to heat source 14 by means of the heat transfer device 30 and a vapor transfer medium. The working medium vapor formed by the heat transfer device 30 is partially transferred from the vapor transfer medium to the vapor pump. This allows the thermal energy of heat source 14 to be utilized particularly well and also saves the electrical energy otherwise required for the pressure increasing device 26. Overall, the efficiency can be increased further.

In addition, a drying process for drying a substance can also be optimized in terms of energy by means of the solution according to the invention. The energy released in step 98 of condensing the working medium is coupled to the drying process so as to transmit energy. In addition, the engine waste heat and the exhaust gas waste heat from an internal combustion process of fuel, in particular biogas, are used as further heat sources 14 and 17 to dry the substance.

LIST OF REFERENCE NUMERALS

10 Apparatus for converting thermal energy

12 Method

14 Heat source

16 Thermodynamic cycle

17 Heat source

18 Collecting tank

20 Lower pressure

22 Line

24 Circulation direction

26 Pressure increasing device

28 Elevated pressure

30 Heat transfer device

32 First heat exchanger

34 Second heat exchanger

36 Line

38 Line

40 Separator

42 Lower region

44 Upper region

46 Line

48 Line

50 Line

52 Line

54 Inlet valve

56 Expansion device

58 Generator

60 Line or exhaust vapor line

62 Condensation device

64 Oil supply circuit

66 Oil supply line or supply device

68 Oil inlet valve

70 Oil separator

71 Separating element

72 Oil discharge line

74 Oil collecting tank

76 Oil heater

78 Vapor line

80 Oil pump

82 Heating circuit line

83 Pressure logarithm

84 Enthalpy

85 Phase boundary line

86 Wet vapor region

88 Step of increasing pressure

90 Preheating step

92 Evaporation step

94 Superheating step

96 Expansion step

98 Condensation step

100 Vapor curve

102 Saturated vapor temperature value

104 Adjustment device

106 Defined exhaust vapor temperature value

108 Vapor supply

110 Vapor supply line

112 Inlet valve

114 Temperature measuring element

116 Temperature measuring element

118 Pressure measuring element

120 Control device

122 Isotherm at 20° C.

124 Isotherm at 30° C.

126 Annular housing

128 Inlet

130 Outlet

132 Inner annular wall

134 Rotary piston

136 Shaft

138 Groove

140 Slide

142 Cell

144 Volume

146 Rotation angle zone

148 Rotation angle zone

150 Rotation angle zone

152 Rotation angle zone

154 Valve or exhaust vapor control valve

156 Blocking element

158 First lower pressure

160 First expansion stage

162 Second expansion stage

Claims

1.-10. (canceled)

11. An apparatus for converting thermal energy from a heat source into mechanical energy by means of a thermodynamic cycle using

a working medium which is carried in the cycle and experiences a changing pressure, wherein a saturated vapor temperature value of the working medium is associated with a particular pressure in each case, and

an expansion device for expanding the working medium from an elevated pressure to a lower pressure, wherein, after expansion to the lower pressure, the working medium has an exhaust vapor temperature,

wherein an adjustment device for adjusting the exhaust vapor temperature to a defined exhaust vapor temperature value above the saturated vapor temperature value associated with the lower pressure is provided.

12. The apparatus according to claim 11,

wherein the defined exhaust vapor temperature value is between 2 K and 12 K above the saturated vapor temperature value associated with the lower pressure.

13. The apparatus according to claim 11,

wherein the defined exhaust vapor temperature value is between 4 K and 8 K above the saturated vapor temperature value associated with the lower pressure.

14. The apparatus according to claim 11,

wherein the defined exhaust vapor temperature value is between 5 K and 6 K above the saturated vapor temperature value associated with the lower pressure.

15. The apparatus according to claim 11,

wherein, by means of the adjustment device, a temperature of the working medium is increased such that the exhaust vapor temperature has the defined exhaust vapor temperature value above the saturated vapor temperature value associated with the lower pressure.

16. The apparatus according to claim 15,

wherein, by means of the adjustment device, the temperature of the working medium within the expansion device is increased.

17. The apparatus according to claim 11,

wherein the adjustment device comprises a vapor supply for supplying vapor to the working medium.

18. The apparatus according to claim 17,

wherein the vapor is superheated.

19. The apparatus according to claim 17,

wherein the vapor is a vapor of the working medium.

20. The apparatus according to claim 11,

wherein a counterpressure is generated on the working medium by means of the adjustment device in such a way that the exhaust vapor temperature has the defined exhaust vapor temperature value above the saturated vapor temperature value associated with the lower pressure.

21. The apparatus according to claim 20,

wherein the adjustment device comprises a blocking element for generating the counterpressure on the working medium, the blocking element having a valve for selectively opening and closing a line carrying the working medium.

21. The apparatus according to claim 11,

wherein the working medium is carried in a circulation direction, and a condensation device for condensing the expanded working medium is provided downstream of the expansion device in circulation direction,

wherein the adjustment device comprises a temperature measuring element for measuring a temperature of the working medium after expansion and before condensation in circulation direction and/or a pressure measuring element for measuring the pressure of the working medium after expansion and before condensation in circulation direction.

22. A method for converting thermal energy from a heat source into mechanical energy by means of a thermodynamic cycle using a working medium which is carried in the cycle and experiences a changing pressure,

wherein a saturated vapor temperature value of the working medium is associated with a particular pressure in each case,

comprising a step of expanding the working medium from an elevated pressure to a lower pressure,

wherein, after expansion to the lower pressure, the working medium has an exhaust vapor temperature, and

wherein the exhaust vapor temperature is adjusted to a defined exhaust vapor temperature value above the saturated vapor temperature value associated with the lower pressure.