DEVICE FOR INCREASING THE HEATING AND COOLING OUTPUT OF A HEAT PUMP IN HEAT RECLAMATION IN AIR CONDITIONING UNITS

Abstract

In order to improve heat reclamation, a circulatory composite system having one heat exchanger each in a supply air volume flow and an exhaust air volume flow is provided in an air treatment system and connected to a buffer reservoir supplied by a heat pump with heat energy. In addition, a method for operating a heat reclamation system with the structure of a circulatory composite system with an integrated heat pump is designed such that the volume flow of the heat exchanger is divided in the line leading to the heat exchanger. The at least two volume flows serve to flow through the heat exchanger (compressor) of the heat pump with a larger or smaller volume flow than the heat exchanger in the supply air.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

This patent application is the national phase of PCT/DE2008/002032, filed Dec. 4. 2008. which claims the benefit of German Patent Application Nos. 102007059332.7, filed Dec. 7, 2007; 102007061617.3, filed Dec. 18, 2007; 102008009860.4, filed Feb. 19, 2008; and 102008032201.6, filed Jul. 9, 2008.

FIELD OF THE INVENTION

The present invention relates generally to heat reclamation and more particularly to a device for multistage heat reclamation with controlled heating and cooling output of an air-conditioning system and to a three-stage heat reclamation system.

BACKGROUND OF THE INVENTION

Heat pumps and interconnected circulating systems are used for heat reclamation in ventilation engineering. In this case, cold external air in the form of supply air can be preheated and also dried, if applicable, by means of a targeted heat transfer from the warm exhaust air. Furthermore, warm external air in the form of supply air can be cooled by means of heat transfer to the exhaust air. In this case, a heat transfer medium (water, brine, etc.) is frequently used for transferring the energy.

Furthermore, interconnected circulating systems with heat pumps integrated therein are known. Such systems are described, for example, in DE 44 08 087 C2 and the book: Wärme- and Kälterückgewinnung in raumlufttechnischen Anlagen [Heat and Cold Reclamation in HVAC Systems], 5th revised edition, 2001; ISBN 3-8041-2233-7. The efficiency of the heat reclamation can be improved with such a combination of an interconnected circulating system and a heat pump.

Heat pumps are also used for connecting several air-conditioning devices with different air volume flows and air temperatures, e.g., as described in WO 2005/072560 A1. In conventional heat reclamation systems, when the heat pump switches on, the heat transfer medium is unevenly heated and cooled because the compressor is switched on and off, leading to uneven supply air temperatures in any air-conditioning system connected thereto. In alternative processes, controlled compressors are used or arrangements are made for controlling the cooling circuit. However, all these measures lead to a decrease in the efficiency and to temperature jumps in the heat transfer medium if the output of a compressor falls below the minimum cooling output, because the compressor needs to be switched off. In the cooling mode, it is also not always possible to transfer the energy introduced into the heat transfer medium by the compressors to the exhaust air without exceeding the permissible condensation temperature. If the exhaust air heat exchanger ices up and a defrosting process needs to be carried out, e.g., by reversing the cooling circuit or with the aid of a bypass circuit, the cold heat exchanger cannot be replaced and the supply air heat exchanger cannot be supplied with sufficiently warm heat transfer medium in an uninterrupted fashion.

According to the device described in DE 44 08 087 C2, a partial flow of the heat transfer medium is decoupled from a heat exchanger such that the heat transfer medium can be once again fed into the flow pipe of the heat exchanger for a thermodynamic treatment. In this system, the volume flows of the heat transfer medium are separated within the heat exchanger during operation. This results in different regions of the heat exchanger being acted upon unevenly and an inferior heat transfer to be adjusted as a consequence thereof. In order to achieve an optimal decoupling in the partial load mode, it would actually be necessary to implement the position of the outlet point variably with respect to the length of the heat exchanger in accordance with the respectively desired output proportioning. Furthermore, the system does not feature a reservoir for excess energy that is directly introduced by the heat pump with the condenser or evaporator in order to purposefully store energy within the interconnected circulating system and to once again withdraw energy therefrom in accordance with demands.

Consequently, the solutions according to the described prior art do not make it possible to achieve a constant temperature of the heat transfer medium at the supply air heat exchanger in order to be able to set a constant supply air temperature in interconnected circulating systems. This also applies to interconnected circulating systems with integrated heat pump, in which the heat transfer medium of the interconnected circulating system directly flows through the evaporator and the condenser, particularly when they are operated in the partial load mode. An optimal heat exchange between the heat transfer medium and air over the entire heat exchanger surface is not possible due to the different mass flows and temperatures of the heat transfer medium. Moreover, a three-stage heat reclamation has not been disclosed so far in the described context.

OBJECTS AND SUMMARY OF THE INVENTION

A device for multistage heat reclamation with controlled heating and cooling output of an air-conditioning system may contain a special unit that features a heat pump with a hydraulic module and an energy-buffering device, as well as a downstream heat exchanger such as, e.g., a lamellar heat exchanger. The three-stage heat reclamation system consists of a regenerative or recuperative heat reclamation system as the first stage of the heat reclamation and an additional two stages of heat reclamation. An interconnected system with integrated heat pump for several air-conditioning systems is provided with interconnected circulating systems for multistage heat reclamation and a low temperature-high temperature shift within the interconnected system for the air-conditioning systems.

The invention therefore is based on the objective of providing a system and method for preventing the aforementioned disadvantages and for substantially increasing the heat reclamation yield while simultaneously achieving adequate controllability of the supply air temperature, directly treating the heat transfer medium thermodynamically with the condenser and the evaporator, delivering excess energy to other consumers, introducing energy from other heat sources and/or heat sinks into the system, and lowering the energy input and the workload for the hydraulic devices.

These objectives are attained with an interconnected circulating system consisting of at least two heat exchangers connected to each other, wherein at least one heat exchanger is respectively arranged in a supply air volume flow and in an exhaust air volume flow of an air-conditioning system, and wherein a buffer reservoir is connected to the interconnected circulating system and a heat pump is integrated into the heat transfer medium circuit by means of the interconnected circulating system. A system is provided for increasing the heat reclamation output in the form of a three-stage heat reclamation system, implemented as an interconnected circulating system described above consisting of several respective heat exchangers in the supply air volume flow and in the exhaust air volume flow of the air-conditioning system, wherein the heat exchangers are connected in parallel pair-by-pair or connected in series in the arrangement in the supply air and exhaust air volume flows.

In one aspect, the invention consists of a heat exchanger system in the form of an interconnected circulating system with integrated heat pump and integrated buffer reservoir with a control valve. The buffer reservoir is preferably realized in the form of a stratified reservoir, wherein excess energy can be purposefully stored in and withdrawn from this reservoir. In addition, one or more downstream heat exchangers such as, e.g., lamellar heat exchangers, are integrated into the interconnected circulating system.

An increase in the return heating output is achieved if a regenerative or recuperative heat reclamation system is provided upstream or downstream. For example, a several respective heat exchangers in the supply air volume flow and in the exhaust air volume flow of the air-conditioning system may be provided, wherein the heat exchangers are connected in parallel pair-by-pair or connected in series in the arrangement in the supply air and exhaust air volume flows.

Due to the connection of several air-conditioning systems to a single interconnected circulating system with integrated heat pump, the invention furthermore makes it possible to shift energy from one air-conditioning system to another.

An economical solution for use in connection with several air-conditioning systems featuring an interconnected circulating system can be realized if the interconnected system with integrated heat pump is also used for the low temperature-high temperature shift between several air-conditioning devices. In this case, the energy withdrawn from one air-conditioning device (the supply air in the air-conditioning device is cooled) is supplied to another air-conditioning device (the supply air in the other air-conditioning device is heated). The compressor only consumes power once, but the energy input has a double use in this case. Air-conditioning devices that feature a regenerative or recuperative heat reclamation system other than an interconnected circulating system as a first stage of the heat reclamation may also be incorporated in this case.

During the operation of the proposed system, the operating modes listed below may be chosen in order to reach the desired supply air temperature with the least effort:

1. Operation of the first stage only

2. Operation of the first stage and the interconnected circulating system (without heat pump WP)

3. Operation of the first stage with the interconnected circulating system and the heat pump WP

4. Supplementing the energy supply with foreign energy from an external heating system in the heating mode, e.g., with PWT PWW

5. Supplementing the energy withdrawal from the supply air with foreign energy from an external cold generator in the cooling mode

6. Supplementing the energy supply by means of geothermal energy in the heating mode, e.g., PWT GeoW

7. Supplementing the energy withdrawal by means of geothermal energy in the cooling mode, e.g., PWT GeoS

8. Delivering energy to external users via PWW or PKW in the heating or cooling mode

9. Low temperature-high temperature shift from one air-conditioning device to another air-conditioning device

10. Low temperature-high temperature shift within an air-conditioning device for a reheater, e.g., in the humidity control in the cooling mode.

Due to the inventive cooperation of the device components, it is possible to keep the supply air temperature constant or to readjust the supply air temperature in accordance with specifications for a maximum energy yield and a minimal input of primary energy. In the terms of VDI 2071, a heat reclamation of up to 100% is achieved, wherein the temperature level of the exhaust air may be higher or lower than the temperature level of the supply air.

Buffer reservoirs are provided in all of the described examples. These buffer reservoirs may be integrated into a heat pump unit, arranged in one of the circuits of the heat pumps in the form of a separate reservoir of various size or replaced with a partial circuit of a heat pump. However, the buffer reservoirs are each assigned, in particular, to an interconnected circulating system in order to be able to buffer the thermal energy obtained at this location and to once again return the thermal energy to this location for heat transfer purposes.

Other objects and advantages of the invention will become apparent upon reading the following detailed description and upon reference to the drawings, in which:

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 illustrates a hydraulic circuit for implementation of the described principles in accordance with an embodiment of the invention;

FIG. 2 illustrates a hydraulic circuit for implementation of the described principles in accordance with a further embodiment of the invention;

FIG. 3 illustrates a hydraulic circuit for implementation of the described principles in accordance with an alternative embodiment of the invention:

FIG. 4 illustrates a hydraulic circuit for implementation of the described principles in accordance with a further embodiment of the invention:

FIG. 5 illustrates a hydraulic circuit for implementation of the described principles in accordance with an alternative embodiment of the invention;

FIG. 6 illustrates a hydraulic circuit for implementation of the described principles in accordance with an alternative embodiment of the invention;

FIG. 7 illustrates a hydraulic circuit for implementation of the described principles in accordance with a further embodiment of the invention;

FIG. 8 illustrates a hydraulic circuit for implementation of the described principles in accordance with an embodiment of the invention;

FIG. 9 illustrates a hydraulic circuit for implementation of the described principles in accordance with an embodiment of the invention;

FIG. 10 illustrates a hydraulic circuit for implementation of the described principles in accordance with an embodiment of the invention;

FIG. 11 illustrates a hydraulic circuit for implementation of the described principles in accordance with an embodiment of the invention;

FIG. 12 illustrates a hydraulic circuit for implementation of the described principles in accordance with an alternative embodiment of the invention;

FIG. 13 illustrates a hydraulic circuit for implementation of the described principles in accordance with a further embodiment of the invention;

FIG. 14 illustrates a hydraulic circuit for implementation of the described principles in accordance with an embodiment of the invention;

FIG. 15 illustrates a hydraulic circuit for implementation of the described principles in accordance with an alternative embodiment of the invention;

FIG. 16 illustrates a hydraulic circuit for implementation of the described principles in accordance with a further embodiment of the invention;

FIG. 17 illustrates a hydraulic circuit for implementation of the described principles in accordance with a further embodiment of the invention; and

FIG. 18 illustrates a hydraulic circuit for implementation of the described principles in accordance with an alternative embodiment of the invention.

While the invention is susceptible of various modifications and alternative constructions, a certain illustrative embodiment thereof has been shown in the drawings and will be described below in detail. It should be understood, however, that there is no intention to limit the invention to the specific form disclosed, but on the contrary, the intention is to cover all modifications, alternative constructions, and equivalents falling within the spirit and scope of the invention.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

In a preferred embodiment, a circuit according to FIG. 1 is used. The hydraulic circuit is connected in such a way that it forms an interconnected circulating system when the compressor of the heat pump WP is switched off. FIG. 1 shows the basic incorporation of a buffer reservoir into an interconnected circulating system. In this case, the buffer reservoir may be realized in the form of a so-called stratified reservoir, wherein thermal energy can be stored in and withdrawn from this reservoir layer-by-layer. This is realized due to the corresponding connection with the supply lines PU, PO and the three-way valve V6. The heat pump WP furthermore is assigned to the buffer reservoir in order to supply thermal energy to this buffer reservoir.

Regarding Operating Mode 1:

Referring to the system of the FIG. 1, Operating mode 1 occurs when the compressor is switched off and without using the heat pump WP.

The heat transfer medium is conveyed in the hydraulic circuit by a pump (e.g., a feed pump of the heat pump WP) and flows through the pipelines and valves of the system in the following sequence: the line L6-A, the valve V5, the line L9, the valve V6, the line L10, the heat exchanger LWT2, the line L4, the valve V1, the lines L1-E, L1-A, the heat exchanger LWT1, the lines L3-A, L3-Z and back into the heat pump WP via the line L6-E.

In this case, the heat transfer medium flows through the condenser and the evaporator of the heat pump WP and no energy is withdrawn or supplied within the heat pump WP that is switched off. The feed pump contained in the heat pump WP is used as a circulating pump for the hydraulic circuit.

Regarding Operating Mode 2:

Referring to the system of the FIG. 1, Operating mode 2 occurs when the compressor is switched off and the buffer reservoir P1-1 is empty:

When the heat pump WP is switched on, the heat transfer medium flowing through the evaporator flows through the pipelines and valves as follows in the heating mode: the line L1-A, the heat exchanger LWT1, the lines L3-A, L7, the valve V1 and back into the heat pump WP via the line L1-E. The heat transfer medium flowing through the condenser of the heat pump WP subsequently flows through the line L6-A, the valve V5, the line L9, the valve V6, the line L10, the heat exchanger LWT2, the lines L4, L8, the valve V4, the line L3-Z and back into the heat pump WP via the line L6-E. Excess energy introduced by the heat pump WP is transported into the buffer reservoir P1-1 with the heat transfer medium via the valve V5 and the line L11 and displaces the cold heat transfer medium stored in the buffer reservoir P1-1, wherein this cold heat transfer medium exits the buffer reservoir P1-1 through the line PU and flows through the line L9 and to the valve V6. The required heat transfer medium temperature for achieving the desired supply air temperature is adjusted with the valve 6.

Regarding Operating Mode 3:

Referring to the system of the FIG. 1, Operating mode 3 occurs when the compressor is switched off and the buffer reservoir P1-1 is full:

The compressors of the heat pump WP are switched off when the buffer reservoir P1-1 is filled with warm heat transfer medium. The hydraulic circuit is connected as described under operating mode 1. The amount of warm heat transfer medium required for reaching the desired temperature in the line L10 is withdrawn from the buffer reservoir P1-1 via the line PO by means of the valve V6. The same quantity of cold heat transfer medium as that withdrawn through the line PO is supplied to the buffer reservoir P1-1 through the line PU 1. In this case, energy is also withdrawn from the exhaust air by means of the heat exchanger LWT1 when the compressors are switched off.

An improvement in the heat reclamation is achieved if the system is realized in the form of a two-stage heat reclamation with a first stage in the form of a regenerative or recuperative heat reclamation system. The corresponding device is illustrated in FIG. 2.

Regarding Operating Mode 4:

Referring to the system of the FIG. 2, Operating mode 4 occurs when the compressor is switched on:

In the system shown in this figure, an interconnected circulating system that is referred to as stage 1 is provided between the supply air channel and the exhaust air channel as the first stage of the heat reclamation. Stage 1 of the heat reclamation withdraws energy from the exhaust air and transfers this energy to the supply air. The second stage of the heat reclamation is connected as follows: the heat transfer medium flows from the evaporator of the heat pump WP through the line L1-A, the valve V8, S2, the lines L3-A and L7, the valve V1 and the line L3-A. The heat transfer medium flows from the condenser of the heat pump WP through the line L6-A, the valve V5, the line L9, the valve V6, the line L10, the heat exchanger LWT2, the line L4, the line L8, the valve V4, the line L3-Z and subsequently the line L6-E. During this process, excess energy can be once again stored in the buffer reservoir P1-2. The heat transfer medium does not flow through the heat exchanger LWT3 in this case.

Operating Mode 5:

Referring to the system of the FIG. 2, Operating mode 5 occurs when the compressor of the heat pump WP is switched off:

An interconnected circulating system is formed when the compressor/compressors of the heat pump WP is/are switched off. The heat transfer medium flows through the valve V1, the valve V7, the heat exchanger LWT3, the line L3A, the line L3-Z, the line L6-E, the line L6-A, the valves V5 and V6, the line L10, the heat exchanger LWT2, the line L4 and once again through the valve V1. If required, energy from the filled buffer reservoir P1-2 can be admixed again.

If ice forms in the heat exchanger LWT1, the valve V8 is closed and the valve V9 is opened. Subsequently, the circulating pump P1 conveys the heat transfer medium through the heat exchanger LWT1 that is heated to temperatures above 0° C. with the electric heater battery Erh in a small circuit.

The invention essentially pertains to a method for operating a heat reclamation system with the structure of an interconnected circulating system with integrated heat pump, in which the volume flow of the heat transfer medium is divided into at least two volume flows in the line leading to the heat exchanger. Due to these measures, a larger or smaller volume flow than that flowing through the heat exchanger in the supply air volume flow can flow through the heat exchanger (evaporator) of the heat pump WP. This makes it possible to adjust the largest temperature difference possible in the heat exchangers of the interconnected circulating system and the smallest temperature difference possible in the heat exchangers of the heat pump. The first effect results in an exceptionally efficient heat transfer in the interconnected circulating system. The latter effect has very positive effects on the operating mode of the heat pump and its compressors.

The core of the invention is, in particular, a method for operating an interconnected circulating system with integrated heat pump, in which a partial flow of the heat transfer medium is decoupled between the exhaust air heat exchanger and the supply air heat exchanger. The decoupled partial flow is subsequently treated thermodynamically by adding thermal energy to or withdrawing thermal energy from this partial flow. Prior to entering the supply air heat exchanger, the decoupled and now altered partial flow of the heat transfer medium is once again combined with the previously remaining other partial flow. Due to the mixing of the two partial flows with different temperatures, the heat transfer medium temperature can be precisely mixed to the heat transfer medium temperature required for reaching the supply air temperature prior to entering the supply air heat exchanger. The partial flow decoupled for the thermodynamic treatment is conveyed through the condenser by means of a circulating pump integrated into the heat pump in the heating mode and through the evaporator in the cooling mode. Due to these measures, a larger or smaller volume flow than that flowing through the (lamellar) heat exchanger in the supply air can flow through the heat exchanger (e.g., evaporator or condenser) of the heat pump. Consequently, the largest possible temperature difference can be adjusted in the heat exchangers of the interconnected circulating system and the smallest possible temperature difference can be adjusted in the heat exchangers of the heat pump. This results in a very effective heat transfer in the interconnected circulating system and a significantly improved operating mode of the heat pump and its compressors. It is important that a reservoir is provided in the system for buffering excess energy that might be introduced into the system by the compressor.

An additional increase of the heat reclamation is achieved with a circuit according to FIG. 9.

In this case, the division of the different volume flows of the heat transfer medium for the operation of the heat pump and the lamellar heat exchanger is preferably realized with an admixing circuit or with an injecting circuit for the incorporation of the condenser and the evaporator. In order to increase the return heating output, several heat exchangers may be connected in series in the supply air volume flow, as well as in the exhaust air volume flow. An additional increase of the return cooling output of the heat pump WP during the cooling of the supply air is achieved if an adiabatic humidifier is placed between the heat exchangers LWT2-1 and LWT2-3. Due to the incorporation of devices supplying geothermal energy into the line L2V-E, the geothermal heat can also be introduced into the system in the heating mode such that the performance of the heat pump WP is further improved.

In case ice forms on the heat exchangers LWT2-1 or LWT2-3, the return heating output of the heat exchangers can be reduced for defrosting purposes. During the defrosting process, the heat pump WP withdraws the required energy from the device that supplies geothermal energy.

Regarding Operating Mode 6:

Referring to the system of the FIG. 3, Operating mode 6 occurs when the compressor of the heat pump WP is switched on:

A circulating pump (feed pump of the heat pump WP) conveys the heat transfer medium through the evaporator of the switched-on heat pump WP that cools down during this process. The heat transfer medium subsequently flows through the line L2V-A. A partial flow is returned to the evaporator of the heat pump WP via the line L2-4, the valve V2-3 and the line L2V-E and the remaining volume flow enters the line L2-3, flows through the heat exchanger LWT2-1 and into the line L2-1. A partial flow is withdrawn from the line L2-1 via the line L2K-E, flows to the condenser of the heat pump WP via the valve V2-2, through an optional buffer reservoir P2-1 and the line L2K-A and then back into the line L2-1. A partial flow is previously returned to the condenser via the line L2-2, the valve V2-2 and the line L2K-E in order to increase the volume flow. The heat transfer medium flows from the line L2-1 into the heat exchanger LWT2-2, the line L2-3, the valve V2-1 and then into the heat exchanger LWT2-1. A partial flow is previously withdrawn and returned to the evaporator via the line L2V-E and the valve V2-3.

Regarding Operating Mode 7:

Referring to the system of the FIG. 3, Operating mode 7 occurs when the compressor of the heat pump WP is switched off:

The heat transfer medium flows through the heat exchanger LWT2-1, the line L2-1, the valve V2-2, the line L2K-E, the buffer reservoir P2-1, the line L2K-A, the line L2-1, the heat exchanger LWT2-2, the line L2-3 and then the valve V2-1. At high energy content in the buffer reservoir P2-1, a partial flow of the heat transfer medium can be returned to the condenser of the heat pump WP during this process via the line L2-2 and the valve V2-2.

In FIG. 4, the reservoir is moved out of the heat pump WP and realized in the form of a stratified reservoir.

Regarding Operating Mode 8:

Referring to the system of the FIG. 4, Operating mode 8 occurs when the compressor of the heat pump WP is switched on:

A circulating pump (feed pump of the heat pump WP) conveys the heat transfer medium through the evaporator of the switched-on heat pump WP that cools down during this process. Subsequently, the heat transfer medium flows through a line L2V-A. A partial flow is returned to the evaporator via a line L2-4, the valve V2-3 and the line L2V-E and the remaining volume flow enters the line L2-3 and flows through the heat exchanger LWT2-1 and into the line L2-1. A partial flow is withdrawn from the line L2-1 via the line L2K-E and flows to the condenser of the WP via the valve V2-2. The heat transfer medium flows back into the line L2-1 via the line L2K-A, the valve V2-5, the line L2-7, the valve V2-6 and the line L2-9. A partial flow for increasing the volume flow is previously returned to the condenser via line L2-2, valve V2-2, and line L2K-E. If excessive energy is introduced, a portion of the heat transfer medium is stored in the reservoir. The heat transfer medium flows from the line L2-1 into the heat exchanger LWT2-2, then through the line L2-3 and the valve V2-1 and is subsequently divided. A partial flow is sucked into the line L2V-E for this purpose.

Regarding Operating Mode 9:

Referring to the system of the FIG. 4, Operating mode 9 occurs when the compressor of the heat pump WP is switched off:

The circulating pump (feed pump of the heat pump WP) conveys the heat transfer medium through the evaporator of the heat pump WP. The heat transfer medium subsequently flows through the line L2V-A, enters the line L2-3 and flows through the heat exchanger LWT2-1 and into the line L2-1. A partial flow is withdrawn from the line L2-1 via the line L2K-E and flows to the condenser of the heat pump WP via the valve V2-2. The heat transfer medium flows back into the line L2-1 via the line L2K-A, the valve V2-5, the line L2-7, the valve V2-6 and the line L2-9. If the heat transfer medium is not sufficiently warm for reaching the desired supply air temperature, warm heat transfer medium from the buffer reservoir P2-1 is admixed. The heat transfer medium flows from the line L2-1 into the heat exchanger LWT2-2, then through the line L2-3 and the valve V2-1 and reenters the heat exchanger LWT2-1.

Regarding Operating Mode 10:

Referring to the system of the FIG. 5:

Corresponds to FIG. 4 with simpler energy buffering in a buffer reservoir outside the heat pump module.

Regarding Operating Mode 11:

Referring to the system of the FIG. 6, Operating mode 11 occurs when the compressor switched on while cooling the supply air volume flow:

The supply air is cooled to the desired temperature with the previously cooled heat transfer medium in the heat exchanger LWT2-2 such that the heat transfer medium is heated up. Subsequently, the heat transfer medium flows into the line L2-3, from which a partial flow is withdrawn via the line L2-5 and flows into the line L2-1 via the valve V2-4. After the withdrawal from the line L2-3, the heat transfer medium flows into the line L2V-E via the valve V2-1, wherein the heat transfer medium flows from the valve V2-3 to the condenser of the heat pump WP and is pumped into the line L2V-4 leading to the heat exchanger LWT2-1 by the integrated circulating pump of the hydraulic module of the heat pump WP. A partial flow is once again withdrawn via the line L2-4 and flows to the condenser that again raises the temperature level via the valve V2-3. The heat transfer medium cools down in the heat exchanger LWT2-1. The heat exchanger LWT2-1 is realized in the form of a hybrid cooler such that a high return cooling output of the heat exchanger LWT2-1 is achieved. The required cooling of the air and the oversaturation with water is realized with the humidifier 2-1. The heat transfer medium reaches the heat exchanger LWT2-3 via S2-2 and additionally cools down therein.

The heat transfer medium continues to flow to the geothermal station GeoS via the line L2.1, in which energy can be optionally withdrawn by means of a device for incorporating geothermal energy. Subsequently, the volume flow of the heat transfer medium is once again divided, wherein one partial flow continues to flow in the direction of the heat exchanger LWT2-2 and the other partial flow flows to the evaporator of the heat pump WP via the line L2K-E and the valve V2-2. The circulating pump integrated into the hydraulic module of the heat pump WP additionally conveys the heat transfer medium into the line L2-1 via the line L2K-A and the heat exchanger ENW-A. A partial flow once again is previously withdrawn from the line L2K-A via the line L2-2 and the valve V2-2 and returned to the evaporator in order to be additionally cooled. During the humidity control of the supply air volume flow, the air that was previously cooled by means of the heat exchanger LWT2-2 is brought to the desired supply air temperature.

Regarding Operating Mode 12:

Referring to the system of the FIG. 6, Operating mode 12 occurs when the compressor is switched off while cooling the supply air volume flow:

The heat transfer medium flows through the heat exchanger LWT2-2 such that the supply air is cooled down, wherein the heat transfer medium subsequently flows through the line L2-3, the valve V2-1, the line L2V-E, the heat exchanger LWT2-1, S2-2, the heat exchanger LWT2-3 and the line L2-1 and then reenters the heat exchanger LWT2-2. A partial flow is previously withdrawn via the line L2K-E and conveyed to the evaporator via the valve V2-2. The cold energy transfer medium from the buffer reservoir is admixed to the heat transfer medium in the hydraulic module until the heat transfer medium has the temperature required for reaching the supply air temperature.

Regarding Operating Mode 13:

Referring to the system of the FIG. 6, Operating mode 13 occurs when the compressor switched on while heating the supply air volume flow:

The supply air is heated to the desired temperature with previously heated heat transfer medium in the heat exchanger LWT2-2, wherein the heat transfer medium subsequently cools down, exits the heat exchanger LWT2-2 via the line L2-3 and flows into the heat exchanger ENK-E, in which energy obtained, e.g., from geothermal sources or waste water can be supplied to the heat transfer medium, via the valve V2-1, the line L2V-E and the valve V2-3. Subsequently, the circulating pump conveys the heat transfer medium through the evaporator such that it exits the heat pump WP via the line L2V-A and flows into the heat exchanger ENK-A, in which energy can be decoupled, for example, in order to cool a server space. A partial flow once again flows into the evaporator circuit via the line L2-4 and the valve V2-3 while the other partial flow flows in the direction of the heat exchanger LWT2-1, is supplied with energy therein and then flows to the heat exchanger LWT2-3, in which the heat transfer medium is additionally heated, via the line S2-2. From the heat exchanger LWT2-3, the heat transfer medium flows into the line L2-1 leading to the heat exchanger LWT2-2. A partial flow is withdrawn from the line L2-1 via the line L2K-E and pumped to the condenser of the heat pump WP, in which the heat transfer medium is heated, via the valve V2-2. The heat transfer medium subsequently flows to the heat exchanger ENW-A via the line L2K-A. The heat exchanger ENW-A makes it possible to decouple energy, e.g., in order to supply a floor heater or concrete core activation. The volume flow once again divides at the connection of the line L2-2 to the line L2K-A and one partial flow flows to the heat exchanger LWT2-2 while the other partial flow is returned to the condenser via the line L2-2, the valve V2-2 and the line L2K-E.

During an adiabatic humidification of the supply air volume flow, the air cooled by the humidifier 2-3 is brought to the desired supply air temperature.

Regarding Operating Mode 14:

Referring to the system of the FIG. 6, Operating mode 14 occurs when the compressor switched off while heating the supply air volume flow:

The heat transfer medium flows through the heat exchanger LWT2-2 such that the supply air is heated, wherein the heat transfer medium subsequently flows through the line L2-3, the valve V2-1, the line L2V-E, the heat exchanger LWT2-1, S2-2, the heat exchanger LWT2-3, the line L2-1 and the geothermal station GeoS and then reenters the heat exchanger LWT2-2. A partial flow is previously withdrawn via the line L2K-E and conveyed to the condenser via the valve V2-2. Warm heat transfer medium from the buffer reservoir is admixed to the heat transfer medium in the hydraulic module until the heat transfer medium has the temperature required for reaching the supply air temperature.

Regarding Operating Mode 15:

Illustrated in FIG. 7:

The heat transfer medium flows through the heat exchanger LWT2-2, subsequently through the line L2-3, the valve V2-1, the heat exchanger LWT2-1 and the line L2-1 and then back into the heat exchanger LWT2-2. A partial flow is withdrawn from the line L2-1 via the line L2K-E, conveyed via the valve V2-2 to the condenser in the heating mode or to the evaporator in the cooling mode through the buffer reservoir of the hydraulic module by means of the first circulating pump contained in the hydraulic module of the heat pump WP and then flows into the line L2-1 via the line L2K-A.

A partial flow is again previously withdrawn via the line L2-2 and conveyed to the condenser or evaporator via the valve V2-2 and the line L2K-E. In order to transfer the energy of the heat pump WP to the exhaust air volume flow, the second circulating pump contained in the hydraulic module of the heat pump WP conveys the heat transfer medium through the line L2M-A, the heat exchanger LWT2-5 and the line L2M-A.

Regarding Operating Mode 16:

Illustrated in FIG. 8:

In this illustration, the device corresponds to above-described operating mode 15. However, a supplementary main circulating pump P2 is provided and subsequently conveys the heat transfer medium in such a way that a constant or controlled flow through the lamellar heat exchangers LWT2-1 and LWT2-2 is ensured.

Regarding Operating Mode 17:

Illustrated in FIG. 9:

In this case, the device is realized in accordance with the devices described above with reference to operating mode 6. A supplementary main circulating pump P2 is also provided in this case in order to achieve a constant or controlled flow through the lamellar heat exchangers LWT2-1 and LWT2-2.

Another embodiment is illustrated in FIGS. 10 and 11.

Regarding Operating Mode 18:

Illustrated in FIG. 10:

The heat transfer medium flows from the heat exchanger LWT2-2 into the line L2-3 and back into the heat exchanger LWT2-2 via the valve V2-1, the heat exchanger LWT2-1 and the line L2-1. A partial flow of the heat transfer medium is then withdrawn from the line L2-1 via the line L2K-E, wherein the partial flow is conveyed via the valve V2-2 to the combined condenser/evaporator through the buffer reservoir of the hydraulic module by means of the circulating pump contained in the hydraulic module of a heat pump WP and subsequently flows into the line L2-1 via the line L2K-A. A partial flow of the heat transfer medium once again is previously withdrawn via the line L2-2 and conveyed to the combined condenser/evaporator via the valve V2-2 and the line L2K-E. The transfer of the energy of the heat pump WP to the heat exchanger LWT2-5 in the exhaust air volume flow is realized with the coolant lines L2M-A and L2M-A.

Regarding Operating Mode 19:

Illustrated in FIG. 11:

In this case, a constant or controlled flow through the lamellar heat exchangers LWT2-1 and LWT2-2 is realized in accordance with operating mode 18, however, with a main circulating pump P2.

Another embodiment is illustrated in FIGS. 12, 13 and 14.

Regarding Operating Mode 20:

Illustrated in FIG. 12 for heat reclamation:

A heat exchanger for introducing additional energy from a heat pump is integrated into an interconnected circulating system that is referred to as 1st stage 4-1. The heat pump withdraws additional energy from the exhaust air flow downstream of the interconnected circulating system by means of lamellar heat exchangers LWT4-1 or/and LWT4-2 and delivers this energy to the supply air by means of the heat exchanger integrated into the interconnected circulating system, in which the heat transfer medium from the interconnected circulating system with the heat exchanger is additionally heated. The respectively required heat transfer medium is conveyed to the heat exchanger with the aid of the valve group V4-G, wherein the feed pipe and the return pipe for the warm or the cold heat transfer medium are each opened during this process.

Regarding Operating Mode 21:

Illustrated in FIG. 12 for low temperature-high temperature shift:

The three-way valve in the interconnected circulating system 1st stage 4-1 is adjusted such that no heat transfer medium can flow through the exhaust air heat exchanger. Energy is withdrawn from the heat transfer medium with the heat pump by means of the heat exchanger incorporated into the interconnected circulating system such that the supply air of an HVAC device RLG1 is cooled. The withdrawn energy is delivered to the interconnected circulating system 1st stage 4-2 for the supply air of an HVAC device RLG2 via the hydraulic circuit of the heat pump by additionally heating the heat transfer medium by means of the interconnected circulating system 1st stage 4-2 with the integrated heat exchanger.

Regarding Operating Mode 22:

Illustrated in FIG. 13:

FIG. 13 shows a somewhat less complicated pipe arrangement that makes it possible to simultaneously utilize both HVAC devices RLG1, RLG2 for heating or for cooling purposes.

Regarding Operating Mode 23:

Illustrated in FIG. 14:

FIG. 14 shows the utilization of an interconnected circulating system as the first stage of the HVAC device RLG1 and a rotating air-to-air heat exchanger as the first stage of the HVAC device RLG2. The connection of the HVAC devices RLG1 and RLG2 is produced by the heat pump WP with integrated hydraulic module as described above with reference to operating mode 20 and operating mode 22.

Regarding Operating Mode 33:

FIG. 15 essentially shows the illustration according to FIG. 12 or 13 in which a KVS is used as the first stage of the HVAC device RLG1 and a KVSs is used as the first stage of the HVAC device RLG2. The connection of the HVAC devices RLG1 and RLG2 is produced by the heat pump WP with integrated hydraulic module as described above with reference to operating mode 20 and operating mode 22. In this case, no heat exchanger is provided for the heat transfer into the circuit of the heat pump WP such that the same heat transfer medium as in the interconnected circulating systems is used in this case.

A recooling device eK is illustrated outside of each of the air-conditioning units in numerous figures. In the cooling mode, the recooling device eK makes it possible to transfer a quantity of energy to the outside air that could not be transferred or that could be transferred only inefficiently with the heat exchangers in the exhaust air volume flow. In this case, it is particularly advantageous if the heat transfer medium initially flows through the recooler outside the air-conditioning units because the outside air used for cooling purposes is generally warmer than the exhaust air temperature. The heat transfer medium can then be cooled down to a lower temperature level with the exhaust air temperature.

LIST OF REFERENCE SYMBOLS

AU Outside air volume flow

AB Exhaust air volume flow

2-1 A diabatic Adiabatic humidifier

2-2 A diabatic humidifier

2-3 A diabatic humidifier

LWT1 Lamellar heat exchanger, exhaust air

LWT2 Lamellar heat exchanger, supply air

LWT3 Lamellar heat exchanger, exhaust air

LWT2-1 Lamellar heat exchanger, exhaust air

LWT2-2 Lamellar heat exchanger, supply air

LWT2-3 Lamellar heat exchanger, exhaust air

LWT2-4 Lamellar heat exchanger, supply air

LWT2-5 Lamellar heat exchanger, exhaust air

LWT2-6 Lamellar heat exchanger, exhaust air realized in the form of a combined condenser/evaporator

L3 A Pipeline

L3 Z Pipeline

L6 E Pipeline

L6 A Pipeline

L7 Pipeline

L8 Pipeline

L9 Pipeline

L10 Pipeline

L11 Pipeline

L2F A Coolant pipeline

L2F E Coolant pipeline

L2K A Pipeline

L2K E Pipeline

L2M A Pipeline

L2M E Pipeline

L2N A Pipeline

L2N E Pipeline

L2V A Pipeline

L2V E Pipeline

L2-1 Pipeline

L2-2 Pipeline

L2-3 Pipeline

L2-4 Pipeline

L2-5 Pipeline

L2-6 Pipeline

L2-7 Pipeline

L2-8 Pipeline

L2-9 Pipeline

S2-2 Pipeline

ENK-A Heat exchanger for decoupling energy for external consumers at low temperature level

ENK-E Heat exchanger for introducing external energy, e.g., geothermal energy or

energy obtained from wastewater

ENW-A A Heat exchanger for decoupling energy for external consumers at high temperature level

PO Pipeline

PU Pipeline

PWW Heat exchanger for introducing external energy, e.g., with pumped hot water

PKW Heat exchanger for introducing external energy, e.g., with pumped cold water

V1 Valve

V2-1 Valve

V2-2 Valve

V2-3 Valve

V2-4 Valve

V2-5 Valve

V2-6 Valve

V4 Valve

V4 Valve

V4-G Valve group

V5 Valve

V6 Valve

V7 Valve

V8 Valve

V9 Valve

VSR Balancing valve or volume flow controller

WP Heat pump with integrated hydraulic module including circulating pumps

and buffer reservoirs and change-over valves for reversible operation

K Optional recooler for transferring excess energy to outside air

P1 Circulating pump

Buffer reservoir External reservoir for buffering energy; stratified reservoir

P2-1 External reservoir for buffering energy realized in the form of a stratified reservoir

P2-2 External reservoir

Stage 1 Regenerative or recuperative heat reclamation system

RLG1HVAC device 1

RLG2HVAC device 2

Claims

1-34. (canceled)

35. An interconnected circulating system consisting of at least two heat exchangers connected to each other, wherein at least one heat exchanger is respectively arranged in a supply air volume flow and in an exhaust air volume flow of an air-conditioning system, and wherein a buffer reservoir is connected to the interconnected circulating system and a heat pump is integrated into the heat transfer medium circuit by means of the interconnected circulating system.

36. The interconnected circulating system according to claim 35 consisting of several respective heat exchangers in the supply air volume flow and in the exhaust air volume flow of the air-conditioning system, wherein the heat exchangers are connected in parallel pair-by-pair or connected in series in the arrangement in the supply air and exhaust air volume flows.

37. The interconnected circulating system according to claim 35 with one or more respective heat exchangers in the supply air and exhaust air volume flows, wherein a buffer reservoir is integrated into the heat transfer medium circuit by means of the heat exchanger or connected to the interconnected circulating system.

38. The interconnected circulating system according to claim 37, wherein the buffer reservoir is arranged in the flow of the heat transfer medium downstream of the device for thermodynamically treating the heat transfer medium and upstream of a heat exchanger in the supply air volume flow and/or exhaust air volume flow.

39. The interconnected circulating system according to claim 35, in which the buffer reservoir is integrated into the heat transfer medium circuit of the condenser or the buffer reservoir is integrated into the heat transfer medium circuit of the evaporator.

40. The interconnected circulating system according to claim 35, in which the buffer reservoir is integrated into the heat transfer medium circuit of a combined condenser/evaporator of a heat pump that can be changed over in the cooling circuit.

41. The interconnected circulating system according to claim 35, in which the buffer reservoir is integrated into the heat transfer medium circuit of an active evaporator or active condenser of a heat pump that can be changed over on the hydraulic side, wherein the active evaporator or the active condenser is used for the supply air.

42. The interconnected circulating system according to claim 35 with integrated heat pump, wherein a partial flow of the heat transfer medium is decoupled between the exhaust air and supply air heat exchangers, wherein the decoupled partial flow of the heat transfer medium is conveyed to a thermodynamic treatment device and recombined with the remaining partial flow of the heat transfer medium before entering the supply air heat exchanger.

43. A method for operating a heat reclamation system with the structure of a interconnected circulating system that respectively features one or more heat exchangers in a supply air volume flow and an exhaust air volume flow, as well as an integrated heat pump,

characterized in

that the volume flow of the heat transfer medium is divided into at least two volume flows in the line leading to the heat exchanger such that a larger or smaller volume flow than that flowing through the heat exchanger in the supply air volume flow can flow through the heat exchanger (such as the evaporator or condenser) of the heat pump.

44. The method according to claim 43, wherein the method is controlled in such a way that a larger or smaller volume than that flowing through the heat exchanger in the exhaust air can flow through the heat exchanger (condenser) of the heat pump.

45. The method according to claim 43, wherein the method is controlled in such a way that a larger or smaller volume flow than that flowing through the heat exchanger in the supply air can flow through the heat exchanger (combined condenser/evaporator) of the heat pump that can be changed over on the cooling side.

46. The method according to claim 43, wherein the method is controlled in such a way that a larger or smaller volume flow than that flowing through the heat exchanger in the supply air can flow through the heat exchanger, condenser or evaporator of the heat pump that is active in the supply air volume flow and can be changed over on the hydraulic side.

47. The method according to claim 43, in which external energy is introduced into the partial circuit of the evaporator.

48. The method according to claim 43, in which energy for an external consumer is decoupled into the partial circuit of the evaporator or energy for an external consumer is decoupled into the partial circuit of the condenser.

49. The method according to claim 43, in which a humidifier is incorporated into the exhaust air volume flow between two series-connected heat exchangers for the adiabatic humidification.

50. A device for three-stage heat reclamation consisting of an interconnected circulating system with at least one respective heat exchanger arranged in an exhaust air volume flow and in a supply air volume flow, with an integrated heat pump and with an upstream or downstream regenerative or recuperative heat exchanger.

51. The Device according to claim 50 with multiple heat exchangers that are connected in series in the supply air volume flow and/or with several heat exchangers that are connected in series in the exhaust air volume flow.

52. The Device according to claim 50 with a defrosting device featuring an electric heater for the heat exchanger in the exhaust air.

53. The Device according to claim 50 with a heat exchanger and external energy from a heating system.

54. The Device according to claim 50 with additional electric heating rods in the heat exchanger in the exhaust air.

55. The Device according to claim 50 for connecting multiple HVAC devices for multistage heat reclamation, wherein the first stage of the heat reclamation of the air-conditioning devices consists of an interconnected circulating system.

56. The Device according to claim 50 for connecting multiple HVAC devices for multistage heat reclamation, wherein the first stage of the heat reclamation of the air-conditioning devices selectively consists of an interconnected circulating system or another regenerative or recuperative heat reclamation system.