DE10323287A1 - Method and device for energy recovery - Google Patents

Abstract

FIELD: technological processes. ^ SUBSTANCE: method and device are intended for energy regeneration. Method of energy regeneration in air conditioning and ventilation equipment sets, comprising device for direction of volume flow of plenum air, device for direction of exhaust air volume flow and system of heat regeneration, includes the following stages: exchange of heat energy in volume flow of exhaust air coming out of heat regeneration system by means of the first heat exchanger connected to heat pump; transfer of exchanged heat energy by means of heat pump and the second heat exchanger connected to heat pump to accumulation circuit, which is connected to heat exchanger for heat energy transfer and comprises energy accumulator; transfer of heat energy sent to accumulation circuit by means of the third heat exchanger to volume flow of plenum air coming out of heat regeneration system with the purpose to cool or heat volume flow of plenum air; control of portion of transferred heat energy in heat exchanger, given to volume flow of plenum air, by control of circulating fluid amount contained in accumulation circuit, passing through energy accumulator and heat exchanger. ^ EFFECT: higher coefficient of heat return. ^ 25 cl, 4 dwg

Description

The invention relates to a method for energy recovery according to the preamble of claim 1 and an associated device according to the preamble of claim 9.

Heat recovery systems Systems with recuperative and regenerative heat exchangers as well as systems with Intermediate medium or heat pumps, are used in air conditioning and ventilation technology for energy recovery used from the exhaust air or exhaust air.

In the literature, heat recovery systems diverse described. Such systems are known in ventilation technology and are often used. According to the literature, this allows so-called heat recovery figures of up to 0.8.

In the publication “Recknagel, Sprenger, Schramek; Paperback for heating + air conditioning 01/02, Edition 2001, Oldenbourg Industrieverlag München ", various pages on pages 1367 ff Heat recovery techniques described. Among other things, a system with a heat pump called.

Further information on systems for Heat recovery in ventilation systems are in the publication “Handbuch der Klimatechnik, 3rd edition, C.F. Müller GmbH, Karlsruhe, volume 2; Calculation and control " pages 115 ff.

In the conventional heat recovery systems where different types of heat exchangers used, the heat output decreases linear with the temperature difference between the exhaust air that of delivered to a ventilation system and the outside air, that of the ventilation system supplied will, from. So the temperature of the outside air rises when heating on, the temperature difference between the outside air decreases and that by means of the ventilation system dissipated Exhaust airflow. There can be less energy from the exhaust air volume flow are recorded and to the outside air to be supplied as the supply air volume flow be delivered. The outside air must therefore subsequently reheated with a heater become.

In the case of cooling, the exhaust air can forming exhaust air volume flow for the same reason, that is because of the drop in the temperature of the outside air, only a portion of the Energy can be extracted.

The outside air must then be used when heating reheated with a heater be or in the cooling case with a cooler aftercooled become.

It is also known with cooling integrated cooling after a heat exchanger undertake or the heating with a heat pump downstream a heat pipe perform. Both mentioned systems can only be regulated to a limited extent, e.g. by step switching, switch on and off or by means of a speed-controlled compressor. The Cooling will sometimes with a hot gas bypass control customized. This procedure is due to the associated Wasted energy less and less used.

A sliding regulation on the entire range of different outside temperatures is with none of the systems possible without reducing the so-called performance figure. variable Volume flows, like they can be used more and more frequently in modern air conditioning systems systems not cooled or be heated.

With the systems known until today is a switchover from the cooling to heating mode and vice versa not effective or not or only with poorer efficiency over Air admixture adjustable.

From the document DE 9218937 U1 a device for climate design in building rooms is known. This device has a regenerative heat exchanger between the supply air and exhaust air volume flow. An evaporator of a heat pump is arranged after this heat exchanger. Another regenerative heat exchanger and the condenser of the heat pump are arranged in the exhaust air volume flow. To increase the energy yield, a second outside air flow is provided in parallel with the outside air flow supplying the building rooms. The evaporator and the condenser of the heat pump are arranged in the respective other outside air flow, so that energy can be transferred from the first outside air flow into the second outside air flow by means of the heat pump.

Furthermore, from the DE 19500527 A1 an air conditioner known. This air conditioner has a supply air and an exhaust air volume flow, both of which are passed through a heat exchanger. The evaporator or condenser of a heat pump is connected downstream of the heat exchanger in the supply air volume flow or in the exhaust air volume flow. The heat pump enables optimal energy recovery only for a specific application. This is derived from the design of the heat pump's output.

Finally, from the DE 19851889 A1 known a heat pump air conditioning system with energy recycling. In the air conditioning system, the supply air and extract air are routed through a common heat exchanger. In the supply air, the heat exchanger is followed, inter alia, by a further heat exchanger coupled to a hot water tank in a first coupling circuit. The hot water tank is coupled to the condenser of a heat pump in a second coupling circuit. A partial flow of the exhaust air can be applied to the evaporator of the heat pump. Another part of the exhaust air is passed through the heat exchanger and another, smaller one Part of the exhaust air mixed with the supply air. The air conditioning system is complex, difficult to control and requires an additional cooling unit for cooling, which must be switched on by means of a further heat exchanger in the supply air.

From the described prior art consequently for a conventional ventilation system a not inconsiderable device technology Additional effort for the warming or after cooling the supply air volume flow to be generated.

The object of the invention is therefore in a method according to the preamble of claim 1 or in a device according to the preamble of claim 9 To avoid disadvantages and the yield of heat recovery with good controllability significantly increase.

Designed to solve this task yourself in a process according to the characterizing features of the claim 1 or a device according to the characterizing features of Claim 9.

The invention consists of a combination of one the known heat recovery systems with a system from a heat pump, a storage circuit and one coupled to the storage circuit Heat exchanger, the heat recovery system is connected downstream in the supply air volume flow. Another heat exchanger is the heat recovery system downstream in the exhaust air volume flow. The two heat exchangers are by means of heat pump coupled, also on the side of the supply air treatment, the heat pump by means of another Heat exchanger with the storage circuit with an energy storage and a mixing valve is provided, is connected.

Through the interaction of the components mentioned Is it possible, the heat transfer too regulate. Among other things, this is for it is necessary to limit the supply air temperature.

The temperature in the circulatory fluid in the storage circuit is set so high that for operation the heat pump a sufficiently high condensing temperature is achieved. This is calculated according to the manufacturer's instructions considering the compressor the temperature of the exhaust air volume flow, the type of the arranged there heat exchanger and the evaporation temperature. Is to reach the average temperature difference in the heat exchanger a higher in the supply air volume flow Circulatory fluid temperature necessary, so the temperature is necessary to reach the medium temperature difference selected. This way, always reached an optimal performance figure of the heat pump, but also guaranteed that the heat exchange in the heat exchanger possible in the supply air volume flow is.

The supply air temperature is controlled via the Mixing valve regulated, for example as a 3-way valve with a Regulator and a motor can be formed. In the case of heating, for example If the required supply air temperature is undershot, the volume flow is reduced of circulatory fluid to the heat exchanger increased in the supply air volume flow. If exceed the required supply air temperature becomes the volume flow of circulatory fluid to the heat exchanger reduced in the supply air volume flow.

Should the exhaust air volume flow be off any reason become smaller, the evaporation temperature drops because less heat is supplied becomes. A decrease in the evaporation temperature is over a Pressure sensor in front of the compressor, alternatively via a Temperature sensor. The evaporation temperature drops below a preset value the controller switches off the compressor. The supply air volume flow is then over the thermal energy heated from the energy storage. After the expiry of the compressor switches the compressor downtime required back to.

If the heat pump is due to reaching one Maximum temperature in the circulating liquid is switched off the supply air volume flow is regulated with energy from the energy storage kept at a constant temperature by the mixing valve. Is the circulatory fluid cooled down again, switches the heat pump again to get energy from the exhaust air volume flow into the circulating liquid and to transfer the energy storage.

A constant switching off and on takes place for heat pumps with a compressor. More powerful Heat pumps are equipped with several compressors. Are in the heat pump If several compressors are installed, the Compressor in a sequential circuit. As a compressor too speed-controlled models are used. In this case the energy storage can be dimensioned somewhat smaller, but what in certain circumstances the performance figure is reduced.

The energy storage is made of content designed so large that the time interval for a complete revolution of the fluid volume longer lasts for this as the downtime of the smallest compressor of the heat pump necessary is. To avoid turbulent flows in the The incoming volume flow of the circulating fluid can save energy preferably with a nozzle tube led into the energy storage. This will be a cheap one laminar flow causes in the energy storage.

The exhaust air volume flow is cooled down as much as is necessary for heat transfer for reasons of the greatest possible energy generation. If icing on the heat exchanger in the exhaust air volume flow is not a hindrance, or no icing takes place due to the exhaust air condition, the desired supply air temperature can be obtained after the heat exchanger in the supply air volume flow with a correspondingly powerful heat pump can be reached without further heating.

By using the heat pump and the for the operation of the heat pump required electrical Power consumption, it is possible to the outside air to pass more energy than can be extracted from the exhaust air.

With the described invention, can in cooling the outside air be cooled to process the supply air volume flow. this happens by reversing the refrigeration cycle the heat pump. Also it is possible to set a constant supply air temperature.

• 1. Es wird eine extrem große Wärmerückgewinnung erzielt. Die mit dem Wärmerückgewinnungssystem erzielte Übertragungsleistung WRG, wird ergänzt durch das in der beschriebenen Kombination gestaltete Wärmepumpensystem. Es ist möglich, dem Abluftvolumenstrom mehr Energie zu entziehen als für die Erwärmung des Zuluftvolumenstromes notwendig ist. Die überschüssige Energie kann optional auch zur Brauchwassererwärmung genutzt werden, z. B. auch zum Heizen nach der adiabatischen Befeuchtung des Zuluftvolumenstromes. Gegenüber anderen Wärmerückgewinnungssystemen kann, auf Grund des regelbaren Wärmerückgewinnungssystems, der Wert der Rückwärmzahl von 1 überschritten werden, wohingegen bei anderen, bekannten Wärmerückgewinnungssystemen maximal eine wirtschaftliche Rückwärmzahl von 0,8 erreicht wird. Beispiel:
  
  Der Abluftvolumenstrom wird mit einem Kreislaufverbundsystem, mit einer Rückwärmzahl von 0,47, in Kombination mit dem Wärmepumpensystem, von 24°C bei 50% relativer Feuchte auf 6,8°C gekühlt: h_EIN = 43,2 h_AUS = 21,6 Δh = 21,5 Die Außenluft tritt mit 10°C bei 70% relativer Feuchte ein. Der Zuluftvolumenstrom wird durch die Behandlung daraufhin in den Zustand mit 31 °C bei 19% relativer Feuchte überführt: h_EIN = 23,4 h_AUS = 43,7 Δh = 21,5 Daraus folgt für den Wert der Rückwärmzahl:
  
  24°C – 10°C
• 2. In den überwiegenden Bedarfsfällen für den Heizfall wird eine weitere Erwärmung des Zuluftvolumenstromes ZU, mit einem zusätzlichen Erhitzer, nicht notwendig sein.
• 3. In den meisten Bedarfsfällen im Kühlfall kann die Außenluft AU so weit gekühlt werden, dass eine weitere Kühlung mit einem zusätzlichen Kühler nicht erforderlich wird. Der Kühler kann im Lüftungsgerät eingespart werden.
• 4. Die von dem Zuluftventilator aufgenommene Leistung an der Welle wird kleiner, weil durch den Wegfall des Luftkühlers die hierfür erforderliche dynamische Druckdifferenz entfällt.
• 5. Die Zuluftgeräte werden durch den Wegfall des Lufterhitzers kleiner und leichter.
• 6. Für die Zuluftkühlung und für die dezentrale Gebäudekühlung ist in den meisten Fällen keine weitere Kältemaschine mehr erforderlich.
• 7. Die Erfindung kann dezentral genutzt oder zentral in einer Luftbehandlungseinheit integriert werden.

The advantages that can be achieved with the invention include the advantageous effects described below:

• 1. An extremely large heat recovery is achieved. The heat transfer system WRG achieved with the heat recovery system is supplemented by the heat pump system designed in the combination described. It is possible to extract more energy from the exhaust air volume flow than is necessary to heat the supply air volume flow. The excess energy can optionally also be used for domestic water heating, e.g. B. also for heating after adiabatic humidification of the supply air volume flow. Compared to other heat recovery systems, the value of the heat recovery rate of 1 can be exceeded due to the controllable heat recovery system, whereas with other known heat recovery systems a maximum economic heat recovery rate of 0.8 is achieved. Example:
  
  The exhaust air volume flow is cooled from 24 ° C at 50% relative humidity to 6.8 ° C with a closed loop system with a heat recovery rate of 0.47, in combination with the heat pump system: h _ON = 43.2 h _OFF = 21.6 Δh = 21.5 The outside air enters at 10 ° C with 70% relative humidity. As a result of the treatment, the supply air volume flow is then converted to the state at 31 ° C with 19% relative humidity: h _ON = 23.4 h _OFF = 43.7 Δh = 21.5
  
  24 ° C - 10 ° C
• 2. In the predominant needs for heating, further heating of the supply air volume flow ZU, with an additional heater, will not be necessary.
• 3. In most cooling cases, the outside air AU can be cooled to such an extent that further cooling with an additional cooler is not necessary. The cooler can be saved in the ventilation unit.
• 4. The power consumed by the supply air fan on the shaft becomes smaller because the dynamic pressure difference required for this is eliminated due to the absence of the air cooler.
• 5. The supply air devices become smaller and lighter due to the elimination of the air heater.
• 6. In most cases, no additional chiller is required for supply air cooling and decentralized building cooling.
• 7. The invention can be used decentrally or can be integrated centrally in an air treatment unit.

The invention is illustrated by two Process schemes are shown as an example and will be described below described in more detail.

Show here

1 a diagram of a first variant of the invention and

2 a diagram of a second variant of the invention.

According to the first embodiment of the invention 1 is converted into an exhaust air volume flow AB, which is converted into exhaust air FO by ventilation treatment, according to a heat recovery system 10 a heat exchanger 2 placed. The heat recovery system 10 is, on the other hand, coupled with a supply air volume flow ZU which is obtained from the outside air AU by ventilation treatment. The heat recovery system 10 can be designed according to one of the known types, for example as a KVS (circulation system) system, rotary or plate heat exchanger, smooth tube heat exchanger, storage mass heat exchanger or heat pipe. The heat exchanger 2 is with a heat pump 3 coupled and acts as an evaporator in the heating case and as a condenser of the heat pump in the optional cooling case 3 ,

In the cooling circuit of the heat pump 3 is another heat exchanger 4 arranged, which is used as a condenser in the heating case and as an evaporator in the cooling case.

There is also a heat exchanger in the supply air volume flow ZU 1 the heat recovery system 10 downstream. The heat exchanger 1 is in a storage cycle 9 coupled. In this storage cycle 9 is also the one with the heat pump pe 3 coupled heat exchangers 4 coupled. Still in the storage cycle 9 an energy storage 9.1 intended. The storage cycle 9 and the energy storage 9.1 are filled with a heat-storing circulating liquid that is circulated by a pump.

The circulating liquid for heat transfer between the heat exchanger 1 and the heat exchanger 4 can be water, a water-glycol mixture or another liquid commonly used in refrigeration and air conditioning technology.

In the case of heating, the temperature of the circulating liquid in the storage circuit 9 chosen so high that the minimum required condensing temperature for the heat pump 3 is guaranteed, but also the average temperature difference in the heat exchanger 1 is so large that the thermal energy can be transferred to the outside air AU, which forms the supply air volume flow ZU after the ventilation treatment described. In the optional cooling case, the temperature of the circulating liquid in the storage circuit 9 chosen so small that the outside air AU is cooled to the desired supply air temperature in the supply air volume flow CL.

The temperature level of the circulating liquid and thus the regulation of the temperature of the supply air volume flow ZU is achieved with a mixing valve 6 or alternatively set with a hydraulic switch. The mixing valve 6 can be designed as a 3-way valve with controller and motor.

The mixing valve is used to regulate the temperature level of the circulating liquid 6 in a branch of the storage cycle 9 arranged in the two branches A and B of the storage circuit 9 are merged. A branch A of the branch is as a return line directly to the heat exchanger 1 connected. A second branch B is with that of the energy store 9.1 coming supply line for the heat exchanger 1 connected. The mixing valve can be adjusted 6 Now different amounts of circulating liquid flow through the two branches A and B and thus form a mixed flow AB. In this way, the heat throughput at the heat exchanger 1 be regulated from a maximum to a minimum level. In the maximum case, the circulating liquid is completely through the heat exchanger 1 led and in the minimum case the heat exchanger 1 no circulating fluid supplied. The energy storage 9.1 that of the heat exchanger 4 directly downstream, the entire amount of liquid flows through and takes the heat pump 3 delivered, but not from the heat exchanger 1 converted amount of heat. Likewise, when the heat pump is switched off 3 the thermal energy from the energy storage 9.1 via the heat exchanger 1 to the supply air volume flow ZU.

Should it be in the heat exchanger 2 annoying ice build-up, the temperature of the circulating fluid is raised. If the thickness of the ice build-up is not acceptable, the refrigeration cycle is interrupted for a short time, causing the heat exchanger 2 is not cooled by the heat pump, and the exhaust air volume flow AB melts the ice deposit again. Alternatively, a separate defrost heater for the heat exchanger can also be installed at this point 2 be used. A differential pressure meter can be used to determine whether ice is present 5 on the exhaust air volume flow (AB) in front of and behind the heat exchanger 2 be determined. Alternatively, the ice build-up can also occur via the increase in air pressure in the exhaust air volume flow AB in front of the heat exchanger 2 be determined.

The heat pump 3 is switched on and off via temperature sensors commonly used in refrigeration technology. Is the temperature in the cooling circuit of the heat pump 3 too high, the compressors are switched off, or in the case of larger, for example multi-stage heat pumps, the compressors are switched on or off depending on the temperatures. The compressors also switch off when the temperature falls below the permissible temperature in the refrigeration cycle.

An additional heat source that may be required can transfer its energy via an optional heat exchanger 16 which is in the supply line to the heat exchanger 1 into the storage cycle 9 is coupled in. The control of the transfer of this thermal energy takes place in a simple manner by means of the mixing valve 6 ,

In the case of recirculation mode, in which heat recovery does not take place, and also in the post-heating mode of the ventilation system, the storage circuit can be used 9 can be used in an additional way. Here, the PWW (pump hot water) of the heating system, which is the storage circuit 9 via the heat exchanger 16 heated, operated with low flow and return temperatures. This in turn enables the use of condensing technology as a heating system in ventilation technology. This can be done using the heat exchanger 16 , for example, a plate heat exchanger is used, preferably a condensing boiler can be connected, which works very effectively even at low temperatures.

The optional function for cooling the outside air AU for a cooled supply air volume flow ZU is done by switching the refrigeration circuit through known devices on the heat pump 3 reached.

Another heat exchanger is used for an optional humidity control of the supply air volume flow ZU in the cooling case 7 after the heat exchanger 1 placed in the supply air volume flow ZU. The heat exchanger 7 emits heat to the supply air volume flow ZU, which has previously been cooled down further for dehumidification, via energy available from the refrigerant, almost free of charge. The temperature of the supply air volume flow ZU is controlled with a mixing valve 8th regulated.

An optional humidity control of the supply air volume flow CLOSE in the heating case, however, is with the energy storage 9 coupled and will be described below in the second embodiment.

To improve heat dissipation in the cooling case, a device for adiabatic cooling between the heat recovery system can be installed in the exhaust air volume flow AB 10 and the heat exchanger 2 the heat pump 3 be provided. The heat transfer at this point is thus greatly improved in a simple manner.

To influence the air treatment can in the channels between supply air volume flow ZU and exhaust air volume flow AB to known Way air flaps for the feeder from mixed air from the exhaust air volume flow AB to the supply air volume flow CLOSE or to carry out a recirculation mode, as mentioned above, can be provided.

When using mixed air, more heat energy can be taken over by the condenser by increasing the air volume flow via the air flap at a low air temperature. This means that cold water can also be generated for any decentralized cooling. The cold water can come from the energy storage 9.1 be removed.

The evaporation and liquefaction temperature can alternatively also via Pressure transducers are regulated.

In the refrigeration cycle can be used for domestic water heating high temperature level an additional Heaters can be installed.

A second embodiment of the invention serves to improve the transfer of thermal energy in the case of variable volume flows of the supply air and / or the exhaust air. Such a system for the generation of variable volume flows is in 2 shown.

The further development according to the invention points to the supply air side of the heat pump 3 an arrangement of the storage circuit 9 with the heat exchanger 1 , the heat exchanger 4 and the energy storage 9.1 and the mixing valve 6 between branches A and B of the storage circuit 9 on how higher up they are below 1 has been described.

In the order after 2 becomes the heat exchanger 2 but not from the refrigerant from the heat pump 3 flows through. Here is the heat exchanger 2 used as a liquid / air heat exchanger. The heat pump 3 there is another storage circuit on the exhaust side of the system 12 with an energy storage 12.1 assigned. The storage cycle 12 is by means of a fourth heat exchanger 13 coupled with the heat pump. In this case the heat exchanger works 13 optionally as an evaporator or condenser for the heat pump 3 , Thus the performance of the compressor (s) of the heat pump 3 fully utilized in cooling and heating. The storage cycle 12 and the energy storage 12.1 are also filled with a heat-storing circulating liquid that is circulated by a pump. The regulation of the liquid throughput in the storage circuit 12 takes place by means of a mixing valve 14 , The mixing valve 14 are branches A and B of the storage circuit 12 assigned. A branch A is directly as a return line with the heat exchanger 2 connected. A branch B is with that of the energy store 12.1 coming to the heat exchanger 2 leading supply line connected. By setting on the mixing valve 14 the flow of the circulating fluid in the storage circuit 12 from the extreme conditions with full throughput through the heat exchanger 2 until the heat exchanger is switched off 2 be managed. The energy storage 12.1 is the heat exchanger 13 directly downstream and the entire amount of liquid flows through.

The thermal energy is transferred to the circulating liquid by means of the heat exchanger 2 transferred to the exhaust air FO. If the differential pressure due to ice build-up on the heat exchanger 2 a predetermined value is exceeded at the mixing valve 14 the flow from branch B to AB is open and that from the heat pump 3 any thermal energy that is introduced is in the storage circuit 12 cached. Here is the heat exchanger 2 stopped. After melting the ice deposit in the heat exchanger 2 and thus the reduction in the differential pressure opens the mixing valve 14 in the storage circuit 12 the branch from A to AB and the thermal energy is further via the heat exchanger 2 to the exhaust air volume flow AB and thus to the exhaust air FO.

In addition to a moisture control for cooling (summer) as in the first embodiment 1 described, a humidity control for heating (winter) can also be provided. There is another heat exchanger in the supply air volume flow ZU 11 arranged. This is with the energy storage 12.1 of the further storage cycle 12 connected and arranged downstream of a humidification device in the supply air volume flow. A mixing valve 15 regulates the flow rate and thus the final temperature of the supply air volume flow ZU.

The transferred energy is in the energy storage 9.1 and 12.1 stored and continuously transmitted to the outside air AU or the supply air volume flow ZU and the exhaust air volume flow AB or the exhaust air FO even when the compressor is at a standstill. In particular the energy storage 9.1 can be directly or indirectly via the storage circuit 9 be connected to additional heat supply or removal devices to better utilize its energy capacity.

Any additional heating source that may be required transfers the energy via the optional heat exchanger 16 to the storage circuit 9 , The control of the transfer of this thermal energy takes place with the mixing valve 6 ,

As already described under the first embodiment, the system can be at this point be supplemented by a heating device based on condensing technology. This is possible if the ventilation system is operated in recirculation mode or in post-heating mode at low water temperatures. Here, the pump warm water of the heating system, which is the storage circuit 9 via the heat exchanger 16 heated, operated with low flow and return temperatures.

The described invention is both Can be operated with single and multi-stage heat pumps.

In addition to the necessary elements described, other elements for air treatment such as filters, silencers or humidifiers can be used in the ventilation ducts in the usual way. To increase the performance figure of the heat pump 3 and for full heat dissipation with variable volume flows, the admixture of outside air to exhaust air, which is common in air conditioning technology, can also take place via a mixed air flap. Likewise, as already mentioned above, the system is suitable for circulating air operation.

The invention is in connection with Air conditioning and ventilation systems of any size can be used, for example also for indoor air conditioning or Hall heaters.

Finally, the invention is also in a very advantageous way for retrofitting existing systems suitable because the heat pump with the storage circuit or the storage circuits as a structural unit on existing ventilation systems can be coupled.

The invention can also be used for operation can be used by combination systems. In doing so, a heat pump in a very rational way Storage circuit or the storage circuits with multiple ventilation systems connected.

The invention is not based on the described embodiment limited, but can within the framework of the professional Knowledge also carried out differently become.

TO

supply air

FROM

Exhaust air flow

FO

Exhaust air

AU

outside air

A

branch

B

branch

FROM

branch

1

heat exchangers

2

heat exchangers

3

heat pump

4

heat exchangers

5

Differential pressure gauge

6

mixing valve

7

heat exchangers

8th

control valve

9

Memory circuit

9.1

energy storage

10

heat recovery system

11

heat exchangers

12

Memory circuit

12.1

energy storage

13

heat exchangers

14

mixing valve

15

control valve

16

heat exchangers

Claims (22)

Process for energy recovery in systems of air conditioning and ventilation technology, with a device for guiding an inlet air volume flow (ZU) and a device for guiding an exhaust air volume flow (AB), with an inlet and outlet air volume flow for the purpose of heat transfer between the inlet and the Exhaust air volume flow connecting heat recovery system formed from one or more heat exchangers ( 10 ) and with a heat pump ( 3 ) which, for the purpose of supplementary energy transport between the supply air volume flow (ZU) and the exhaust air volume flow (AB), the heat recovery system ( 10 ) assigned and coupled by means of heat exchangers to the supply air volume flow (ZU) and / or the exhaust air volume flow (AB), characterized by - exchange of thermal energy in the from the heat recovery system ( 10 ) emerging exhaust air volume flow (AB) by means of a heat pump ( 3 ) coupled first heat exchanger ( 2 ), - transfer of the exchanged thermal energy by means of the heat pump ( 3 ) and a second one with the heat pump ( 3 ) coupled heat exchanger ( 4 ) to a storage circuit ( 9 ), which is used to transfer thermal energy with the heat exchanger ( 4 ) is coupled and an energy store ( 9.1 ) contains, and - transferring the data to the storage circuit ( 9 ) about transferred thermal energy by means of a third heat exchanger ( 1 ) from the heat recovery system ( 10 ) emerging supply air volume flow (ZU) for the purpose of cooling or heating the supply air volume flow (ZU). A method according to claim 1, characterized by - taking thermal energy from the heat recovery system ( 10 ) emerging exhaust air volume flow (AB) by means of the heat pump ( 3 ) coupled heat exchanger ( 2 ), - transferring at least a part of the extracted energy by means of the heat pump ( 3 ) and in the storage cycle ( 9 ) coupled heat exchanger ( 4 ) in the storage circuit ( 9 ) or the energy storage ( 9.1 ), and - Transfer the from the exhaust air volume flow (AB) into the storage circuit ( 9 ) transferred energy by means of the heat exchanger ( 1 ) for heating to the heat recovery system ( 10 ) emerging supply air volume flow (ZU). A method according to claim 1, characterized by - extracting thermal energy from the heat recovery system ( 10 ) incoming supply air volume flow (ZU) for the purpose of cooling the supply air volume flow (ZU) by means of the storage circuit ( 9 ) coupled heat exchanger ( 1 ), - Removing at least part of the extracted thermal energy by means of the heat pump ( 3 ) and in the storage cycle ( 9 ) coupled heat exchanger ( 4 ) from the storage circuit ( 9 ), and - transfer the data from the storage circuit ( 9 ) extracted thermal energy by means of the heat pump ( 3 ) and the heat exchanger ( 2 ) from the heat recovery system ( 10 ) emerging exhaust air volume flow (AB). A method according to claim 3, characterized by - extracting thermal energy from the heat recovery system ( 10 ) emerging exhaust air volume flow (AB) for the purpose of cooling the exhaust air volume flow (AB) by means of adiabatic cooling, and - supplying the cooled exhaust air volume flow (AB) to the heat exchanger ( 2 ) for the purpose of transferring the data from the storage circuit ( 9 ) extracted thermal energy to the cooled exhaust air volume flow (AB). A method according to claim 3 or 4, characterized by - supplying thermal energy to the from with the storage circuit ( 9 ) connected heat exchanger ( 1 ) emerging supply air volume flow (ZU) for reheating for humidity control of the cooled supply air volume flow (ZU) by means of a preferably with the hot gas circuit of the heat pump ( 3 ) coupled further heat exchanger ( 7 ), and - supplying the heated supply air volume flow (AB) to an air-conditioned room. Method according to Claims 1 to 5, characterized by regulating the proportion of the heat energy transferred in the heat exchanger (ZU) associated with the supply air volume flow (ZU) 1 ) by controlling the flow rate in the storage circuit ( 9 ) contained circulating fluid through the energy storage ( 9.1 ) and the heat exchanger ( 1 ). Method according to one of claims 1 to 6, characterized by a variable volume flow control of the exhaust air volume flow (AB) and / or the supply air volume flow (ZU) by the following process steps - exchange of thermal energy in the heat recovery system ( 10 ) emerging exhaust air volume flow (AB) by means of the heat exchanger ( 2 ) with another another energy storage ( 12.1 ) containing storage circuit ( 12 ), - transferring at least a part of the exchanged thermal energy by means of a heat pump ( 3 ) coupled fourth heat exchanger ( 13 ) and the heat pump ( 3 ) from the further storage cycle ( 12 ) with which the energy storage ( 9.1 ) containing the first storage circuit ( 9 ) coupled heat exchanger ( 4 ) in the first storage cycle ( 9 ), and - transferring at least part of the data to the first storage circuit ( 9 ) transferred heat energy by means of the heat exchanger ( 1 ) from the heat recovery system ( 10 ) emerging supply air volume flow (ZU). Method according to Claim 7, characterized by regulating the proportion of the heat energy transferred in the heat exchanger (AB) assigned to the exhaust air volume flow (AB) 2 ) by controlling the flow rate in the storage circuit ( 12 ) contained circulating fluid through the energy storage ( 12.1 ) and the heat exchanger ( 2 ). Device for energy recovery in a system of air conditioning and ventilation technology, with one supply air volume flow (ZU) and one exhaust air volume flow (AB), with the supply air (ZU) and the exhaust air volume flow (AB) for the purpose of heat transfer between the supply air (ZU) and the heat recovery system connecting the exhaust air volume flow (AB) ( 10 ), which contains a regenerative heat exchanger or a recuperative heat exchanger or a storage mass heat exchanger or a heat pipe, and a heat pump ( 3 ) for the purpose of transporting energy to the supply air volume flow (ZU) or to the exhaust air volume flow (AB) to the heat recovery system ( 10 ) and is coupled by means of heat exchangers to the supply air volume flow (ZU) and / or the exhaust air volume flow (AB), characterized by a storage circuit ( 9 ) between the heat pump ( 3 ) and one in the supply air volume flow (ZU) the heat recovery system ( 10 ) downstream heat exchanger ( 1 ) is arranged, the heat transport in the storage circuit ( 9 ) is adjustable. Apparatus according to claim 9, characterized by a arranged in the exhaust air volume flow (AB) and with the heat pump ( 3 ) coupled heat exchanger ( 2 ), which by means of a second heat exchanger ( 4 ) with the heat pump ( 3 ) coupled storage circuit ( 9 ), one in the storage circuit ( 9 ) coupled energy storage ( 9.1 ) with the storage circuit ( 9 ) coupled heat exchanger ( 1 ), which is arranged in the supply air volume flow (ZU), and a device ( 6 ) to regulate the supply air temperature of the supply air volume flow (ZU), which determines the flow of the circulating liquid in the storage circuit ( 9 ) through the heat exchanger ( 1 ) and the energy storage ( 9.1 ) controls. Apparatus according to claim 10, characterized by the arrangement of the first heat exchanger ( 2 ) as evaporator or condenser of the heat pump ( 3 ). Apparatus according to claim 10, characterized by the arrangement of the second heat exchanger ( 4 ) as a condenser or evaporator of the heat pump ( 3 ). Device according to claim 10 or 12, characterized by a further storage circuit ( 12 ) which is connected to another heat exchanger ( 13 ) with the heat pump ( 3 ) is coupled into the further storage circuit ( 12 ) coupled further energy storage ( 12.1 ) and a facility ( 14 ) to regulate the delivery of thermal energy to the exhaust air volume flow (AB), which determines the flow of the circulating liquid in the further storage circuit ( 12 ) through the heat exchanger ( 13 ) and the other energy storage ( 12.1 ) controls, with a variable volume flow control in the supply air (ZU) and / or exhaust air volume flow (AB). Device according to claim 13, characterized by the arrangement of the heat exchanger ( 13 ) as evaporator or condenser of the heat pump ( 3 ). Device according to claims 9 to 13, characterized in that the heat pump ( 3 ) is switchable. Apparatus according to claims 9 to 15, characterized by a device for adiabatic cooling of the exhaust air volume flow (AB) before entering the condenser of the heat pump ( 3 ) to improve the performance figure in the case of cooling the supply air volume flow (ZU). Apparatus according to claim 9 to 15, characterized by a device for the reheating of the from the heat exchanger ( 1 ) emerging supply air volume flow (ZU) for humidity control of the supply air volume flow (ZU) by means of a heat exchanger arranged in the supply air volume flow (ZU) ( 7 ) supplied heat energy of the heat pump ( 3 ), preferably from the hot gas of the heat pump ( 3 ). Apparatus according to claims 9 to 17, characterized by a device for additional heating, an additional heating system via a separate heat exchanger ( 16 ) in the storage circuit ( 9 ) is coupled. Device according to claim 18, characterized by Use of a device according to the condensing technology as an additional Heating system. Device according to one or all of claims 9 to 19, characterized by the combination of several supply and exhaust devices into a single energy recovery system, only one heat pump ( 3 ) and only one storage circuit ( 9 ) with an energy storage ( 9.1 ) is provided. Device according to one or all of claims 13 to 19, characterized by the combination of several supply and exhaust devices into a single energy recovery system, only one heat pump ( 3 ) and only one storage circuit ( 12 ) with an energy storage ( 12.1 ) is provided. Device according to one or all of claims 9 to 21, characterized by the arrangement of one or more of the heat pump ( 3 ) independent transfer points or facilities for the transport of thermal energy on the storage circuit ( 9 ) and / or on the energy storage ( 9.1 ) and / or on the storage circuit ( 12 ) and / or on the energy storage ( 12.1 ).