DE102016204153A1 - Heat pump system with pumps, method for operating a heat pump system and method for producing a heat pump system - Google Patents

Abstract

A heat pump system comprises: a heat pump unit having at least one heat pump stage (200), the at least one heat pump stage (200) having an evaporator (202), a compressor (204) and a condenser (206); a first heat exchanger (212) on a side to be cooled; a second heat exchanger (214) on a side to be heated; a first pump (208) coupled to the first heat exchanger (212); and a second pump (210) coupled to the second heat exchanger (214), the heat pump system having an operating position, the heat pump system having an operating position, the heat pump unit being in the operating position above the first pump (208) and the second pump (210), wherein in the operating position, the first pump (208) or the second pump (210) are arranged at a lower end of the heat pump system, and wherein in the operating position of the first heat exchanger (212) and the second heat exchanger (214) are also disposed below the heat pump unit at the lower end adjacent to the first pump (208) or the second pump (210).

Description

The present invention relates to heat pumps for heating, cooling or for any other application of a heat pump.

8A and 8B represent a heat pump, as described in the European patent EP 2016349 B1 is described. The heat pump initially includes an evaporator 10 to evaporate water as a working fluid to the output side, a steam in a working steam line 12 to create. The evaporator comprises an evaporation space (in 8A not shown) and is designed to generate an evaporation pressure of less than 20 hPa in the evaporation space, so that the water evaporates at temperatures below 15 ° C in the evaporation space. The water is z. As groundwater, free in the ground or in collector pipes circulating brine, so water with a certain salinity, river water, seawater or seawater. It can be used all types of water, ie calcareous water, lime-free water, saline water or salt-free water. This is because all types of water, that is, all of these "hydrogens", have the favorable water property, namely that water, also known as "R 718", is an enthalpy difference ratio useful for the heat pump process of 6 has, which is more than 2 times the typical usable enthalpy difference ratio of z. B. R134a corresponds.

The water vapor gets through the suction line 12 a compressor / condenser system 14 supplied, which is a turbomachine such. B. has a centrifugal compressor, for example in the form of a turbocompressor, in 8A With 16 is designated. The turbomachine is designed to compress the working steam to a vapor pressure at least greater than 25 hPa. 25 hPa corresponds to a liquefaction temperature of about 22 ° C, which can already be a sufficient heating flow temperature of a floor heating, at least on relatively warm days. In order to generate higher flow temperatures, pressures greater than 30 hPa can be achieved with the turbomachine 16 wherein a pressure of 30 hPa has a liquefaction temperature of 24 ° C, a pressure of 60 hPa has a liquefaction temperature of 36 ° C, and a pressure of 100 hPa corresponds to a liquefaction temperature of 45 ° C. Underfloor heating systems are designed to heat sufficiently with a flow temperature of 45 ° C, even on very cold days.

The turbomachine is with a condenser 18 coupled, which is adapted to liquefy the compressed working steam. By liquefying the energy contained in the working steam is the condenser 18 then fed over the flow 20a to be supplied to a heating system. About the return 20b the working fluid flows back into the condenser.

According to the invention, it is preferable to extract from the high-energy steam directly through the colder heating water the heat (energy) which is taken up by the heating water so that it heats up. The steam is so much energy withdrawn that this is liquefied and also participates in the heating circuit.

Thus, a material entry takes place in the condenser or the heating system, which by a sequence 22 is regulated, such that the condenser has a water level in its condenser, which remains despite the constant supply of water vapor and thus condensate always below a maximum level.

As has already been stated, it is preferred to take an open circuit, ie to evaporate the water, which is the heat source, directly without a heat exchanger. Alternatively, however, the water to be evaporated could first be heated by a heat exchanger from an external heat source. In addition, in order to avoid losses for the second heat exchanger, which has so far necessarily been present on the condenser side, the medium is also used directly there, when thinking of a house with underfloor heating, the water originating from the evaporator to circulate directly in the underfloor heating.

Alternatively, however, a heat exchanger can be arranged on the condenser side, with the flow 20a is fed and the return 20b wherein this heat exchanger cools the water in the condenser and thus heats a separate underfloor heating liquid, which will typically be water.

Due to the fact that water is used as the working medium, and due to the fact that only the evaporated portion of the groundwater is fed into the turbomachine, the purity of the water does not matter. The turbomachine, as well as the condenser and possibly directly coupled underfloor heating always supplied with distilled water, so that the system has a reduced maintenance compared to today's systems. In other words, the system is self-cleaning because the system is always fed only distilled water and the water in the drain 22 thus not polluted.

In addition, it should be noted that turbomachines have the properties that they - similar to an aircraft turbine - the compressed medium not with problematic substances, such as oil, in connection. Instead, the water vapor is compressed only by the turbine or the turbocompressor, but not associated with oil or other purity impairing medium and thus contaminated.

The distilled water discharged through the drain can thus - if no other regulations stand in the way - be readily returned to the groundwater. Alternatively, however, it may also be z. B. in the garden or in an open space to be seeped, or it can be supplied via the channel, if regulations dictate - a sewage treatment plant.

The combination of water as a working fluid with the two times better usable enthalpy difference ratio compared to R134a and because of the reduced requirements for the closed system, and due to the use of the turbomachine, by the efficient and without purity impairments required compression factors are achieved, an efficient and environmentally neutral heat pump process is created.

8B shows a table to illustrate various pressures and the associated evaporation pressures associated with these pressures, which results in that, in particular for water as the working medium quite low pressures in the evaporator are to be selected.

The DE 4431887 A1 discloses a heat pump system with a lightweight, large capacity, high performance centrifugal compressor. A vapor exiting a second stage compressor has a saturation temperature which exceeds the ambient temperature or that of available cooling water, thereby allowing for heat removal. The compressed vapor is transferred from the second stage compressor to the condenser unit consisting of a packed bed provided inside a cooling water sprayer at an upper surface supplied by a water circulating pump. The compressed water vapor rises in the condenser through the packed bed where it passes in direct countercurrent contact with the downwardly flowing cooling water. The vapor condenses and the latent heat of condensation absorbed by the cooling water is expelled to the atmosphere via the condensate and the cooling water, which are removed together from the system. The condenser is continuously purged with non-condensable gases by means of a vacuum pump via a pipeline.

The WO 2014072239 A1 discloses a condenser with a condensation zone for condensing vapor to be condensed in a working fluid. The condensation zone is formed as a volume zone and has a lateral boundary between the upper end of the condensation zone and the lower end. Further, the condenser comprises a steam introduction zone which extends along the lateral end of the condensation zone and is designed to supply condensing vapor laterally across the lateral boundary into the condensation zone. Thus, without increasing the volume of the condenser, the actual condensation is made into a volume condensation, because the vapor to be liquefied is introduced not only head-on from one side into a condensation volume or into the condensation zone, but laterally and preferably from all sides. This not only ensures that the condensation volume provided is increased at the same external dimensions compared to a direct countercurrent condensation, but that at the same time the efficiency of the capacitor is improved because the vapor to be liquefied in the condensation zone, a current direction transverse to the flow direction having the condensation liquid.

In heat pump systems, in particular, when heat pump systems are to be used for heating or cooling, for example, but not exclusively in the area of low or medium power disadvantageous if the heat pump systems run unreliable or very bulky. Such a problem can occur when the working fluid z. B. is maintained at a relatively low pressure, as is the case for example with water as the working fluid. Then, especially when using pumps, it must be ensured that the pressure in the working fluid on the suction side of the pump does not become too low. If this were to occur, then the activity of the pump, namely, when the pump impels energy to the fluid, would cause bubbles to form in the fluid. These bubbles then collapse again. This process is called "cavitating". If a cavitation takes place at all or with a specific intensity, this can lead in the long run to damage to the pump wheels and thus to a reduced service life of the heat pump system. In addition, an already damaged but still running impeller causes the pumping efficiency to decrease. If this decreasing efficiency of the pump is absorbed with a higher pumping power, this leads to an energy consumption, which in principle would not have to be and thus to a reduced efficiency of the Heat pump system. If, on the other hand, the pumping power is not compensated, a pump which has already been damaged by excessive cavitation but is still able to run results in the pumped volume pumped becoming smaller, which likewise results in a reduced efficiency of the heat pump system.

Other aspects of a heat pump system with heat exchangers is how the heat pump system can be put into operation, which are to be filled at a first commissioning or commissioning after a maintenance stop, the heat exchanger. Thus, in principle, a heat exchanger on the cold water side and a heat exchanger on the hot water or cooling water side is provided. For these heat exchangers, which are typically very heavy, it is important that they are coupled with pumps and heat pump stages, and that they are additionally easy to maintain and in particular also installed such that commissioning or decommissioning of the heat pump system as simple and therefore safe and easy to service can take place.

Another point that plays a significant role is the use of several heat pump stages in a heat pump plant and the coupling of the heat pump stages with each other or with various pumps or various heat exchangers to create an optimal heat pump system that works efficiently, which has a good life, or which can be used flexibly for various operating conditions.

The object of the present invention is to provide an improved heat pump system, a method for manufacturing a heat pump system and a method for operating a heat pump system.

This object is achieved by a heat pump system according to claim 1, a method for manufacturing a heat pump system according to claim 31 or a method for operating a heat pump system according to claim 32.

In one aspect of the present invention, the heat exchangers are located at the bottom of the heat pump system, below the pumps. Such a heat pump system comprises a heat pump unit with at least one and preferably several heat pump stages. Furthermore, a first heat exchanger is provided on a side to be cooled. In addition, a second heat exchanger is provided on a side to be heated. Further, there is a first pump coupled to the first heat exchanger and a second pump coupled to the second heat exchanger. The heat pump system has an operating position in which the first pump and the second pump are arranged above the first and second heat exchangers. In addition, the heat pump unit is disposed with the one or more heat pump stages above the first and second pumps.

Advantages of this arrangement according to one aspect of the invention is the low center of gravity. The heat exchangers are typically the heaviest. Above the heat exchangers, the pump module is arranged in the exemplary embodiment, wherein, optionally, when using a plurality of heat pump stages, a mixer module is again arranged above the pump module. The one or more containers with the one of the plurality of compressors of the heat pump stages are arranged at the highest point. A particular advantage with the arrangements of the compressors at the highest point is that they are dry in the off-state. Then, namely, the working fluid, such as water, runs downwards due to gravity.

This arrangement with below provided heat exchangers is characterized by a lightweight construction. First, the heat exchanger z. B. mounted in a heat pump system frame. Then the pump module, optionally the mixer or Wegemodul and finally the one or more heat pump stages is placed. Preferably, the heat exchangers are arranged lying here. This means that when filling the heat pump system at a first startup or commissioning after a maintenance interval no air bubbles take place, so that the heat pump system is self-venting.

In addition, it is preferred in this embodiment that all pumps are arranged in downpipes, not in risers. In particular, the pumps are arranged so that the suction side of the pump is arranged as far down in the downpipe. Thus, kinetic energy is already obtained from the head of the water column and the pressure on the suction side of the pump is higher than in a bottom-up riser. Thus, the minimum water column on the suction side of the pump is smaller than required by the pump manufacturer. On the one hand cavitation at all or excessive cavitation can be prevented. On the other hand, a compact heat pump system is achieved, which does not require a particularly large space for use. This is because the pipe connections in front of the suction side of the pump can be made short. This makes the entire system more compact and thus less bulky. Also Weight savings can be achieved through a more compact design.

In a second aspect of the present invention, the heat pump system is provided with pumps located at the bottom. Therefore, alternatively to the described first aspect according to the second aspect of the present invention, in the operating position, the first and second pumps are disposed below the heat pump unit at a lower end of the heat pump unit. Moreover, in this arrangement, in the operating position, the first heat exchanger and the second heat exchanger are also disposed below the heat pump unit at the lower end adjacent to the pumps. In order to efficiently prevent cavitation, the pumps are arranged at the lowest point of the heat pump system. In addition, the pumps are installed horizontally, so that the maximum back pressure exists in front of the suction side of the pump. This avoids cavitation efficiently and thus damaging the pump wheels. The necessary dynamic pressure upstream of the suction side of the pump determines the smallest possible height difference between the heat pump stage, ie the container with condenser, evaporator and compressor and the corresponding pump. Preferably, the heat exchanger is mounted upright in the second aspect, so that air pockets are avoided during filling. In addition, due to the vertical position of the heat exchanger, the necessary pipe connection from the heat exchanger back into the evaporator or in the condenser shorter, because the heat exchanger itself, which may typically have considerable lengths, is effectively used as a double connection line.

In a third aspect of the present invention, the heat pump system is not operated with only a single heat pump stage, but with two or more heat pump stages. Here, the heat pump stage is connected with a first compressor, a first condenser and a first evaporator in a sense in chain with a second or further heat pump stage with a second compressor, a second condenser and a second evaporator. For this purpose, the first condenser outlet of the first condenser is connected to a second evaporator inlet of the second evaporator of the further heat pump stage via a connecting line. Thus, the warmest liquid of the heat pump stage is introduced into the evaporator, so the coldest area of the further heat pump stage to be cooled there again. The heat pump stages are therefore not connected in parallel, but in chain. Depending on the implementation of the input of the condenser of the first heat pump stage can be coupled to the output of the evaporator of the other heat pump stage or, as is preferred in certain embodiments, be guided in a controllable path module to the heat pump system with the heat pump stage and the other heat pump stage in to operate various operating modes optimally adapted to the heating or cooling task.

In preferred embodiments of the third aspect of the present invention, which relates to the derailleur of two heat pump stages, the first condenser of the heat pump stage is arranged in the operating position above the second evaporator of the further heat pump stage, so that the working fluid due to gravity from the first condenser into the second evaporator flows in the connecting line. This can be saved here a pump. A DC link pump is only necessary to bring working fluid from the evaporator of the further heat pump stage back to a higher level with respect to the operating position in the condenser of the heat pump stage, ie the first heat pump stage. Thus, a heat pump system with two heat pump stages can be operated efficiently with only three pumps, namely a first pump coupled to the input to the cold side heat exchanger, a second pump coupled to the input to the heat side heat exchanger, and a DC link pump. which is coupled to the outlet of the evaporator of the further heat pump stage.

The arrangement of further heat pump stages can also take place as a chain circuit, in turn, when the respective condenser of the lower heat pump stage above the respective evaporator of the higher heat pump stage are arranged, again pumps can be saved. Alternatively or additionally, the third stage or further stages can also be coupled in parallel or in series or in another way with the two heat pumps connected in chain.

The space that results below the higher level heat pump stage is preferably used to accommodate a path module that is controllable to implement various modes of operation. Various modes of operation include a high power mode, a mid power mode, a free cooling mode or a low power mode, and according to the third aspect of the present invention, a controller is provided to set the controllable path module to implement at least two of these four modes of operation. In other embodiments, three and in still other embodiments, all four modes of operation are implemented. By using a larger number of heat pump stages can Further operating modes, so more than four operating modes are implemented.

Due to the arrangement of the pumps and the heat exchangers according to the first or the second aspect almost only point-to-point connections are achieved, which are favorable for a compact construction and a Kavitationsvermeidung.

Due to the difference in height of the two containers, it can be dispensed with a pump between the condenser outlet of the higher container and the evaporator inlet of the lower container, as has been explained. The resulting from the difference in height of the two containers space is used for the controllable way switch, through which the heat pump system can be switched to different modes to achieve optimum adaptation to various operating conditions.

The arrangement of the two heat pump stages and the interconnection of the heat pump stages according to a chain circuit, ie by connecting the condenser outlet of the first stage condenser with the evaporator inlet of the further stage allows the existing infrastructure to be used in each operating mode. Both heat pump stages are therefore regardless of whether they are active, so whether the respective compressor is running or not, flows through the working fluid. Thus, no bypass lines or valves are needed. Instead, to get from one mode of operation to another mode of operation, the paths are switched in a 2 × 2-way switch array.

This makes it possible for an inactive heat pump stage, ie a heat pump stage, in which the compressor is not active, ie where the same pressure prevails on the evaporator and condenser side, to be put into operation without further measures by starting the compressor. The system is thus designed so that no special start-up or evacuation measures are necessary, but a heat pump stage is started when the compressor is put into operation, and is stopped when the compressor is taken out of service. Nevertheless, the feeds for the evaporator and the condenser and the processes from the evaporator and the condenser of a stage are still flowed through despite disabled compressor. This ensures that optimum readiness is achieved without the need for special energy consumption.

In another embodiment, an efficient working fluid transport device is used. It has been found that working fluid accumulates in the evaporator of the lower stage, ie the stage which is thermodynamically arranged on the side to be heated. To allow compensation here again to the evaporator in the higher-lying container, a self-regulating system, the z. B. may have an overflow and a U-tube used. The U-tube is connected to a bottleneck in front of a pump in the evaporator circuit of the higher tank. Due to the increased flow speed in front of the pump, the pressure drops and water from the U-tube can be absorbed. The system is self-regulating insofar as a stable water level is established in the U-tube, which is sufficient for the pressure in front of the pump in the constriction and in the evaporator of the lower tank.

Preferred embodiments of the present invention will be explained below in detail with reference to the accompanying drawings. Show it:

1 a schematic diagram of a heat pump stage with entangled evaporator / condenser assembly;

2A a schematic representation of a heat pump system with bottom heat exchangers according to the first aspect of the present invention;

2 B a schematic representation of a heat pump system with bottom pump according to the second aspect of the present invention;

3A a schematic representation of a heat pump system with chain connected first and further heat pump stage according to the third aspect of the present invention;

3B a schematic representation of two fixed-chain heat pump stages;

4A a schematic representation of coupled with controllable directional switches in chain heat pump stages.

4B a schematic representation of a controllable roadside module with three inputs and three outputs;

4C a table showing the various connections of the controllable road module for different modes of operation;

5 a schematic representation of the heat pump system of 4A with additional self-regulating fluid equalization between the heat pump stages;

6A a schematic representation of the heat pump system with two stages, which is operated in the high performance mode (HLM);

6B a schematic representation of the heat pump system with two stages, which is operated in the middle power mode (MKM);

6C a schematic representation of the heat pump system with two stages, which is operated in free cooling mode (FKM);

6D a schematic representation of the heat pump system with two stages, which is operated in low power mode (NLM);

7A a table showing the operating states of various components in the various operating modes;

7B a table showing the operating states of the two coupled controllable 2 × 2-way switch;

7C a table showing the temperature ranges for which the operation modes are appropriate;

7D a schematic representation of the coarse / fine control of the operating modes on the one hand and the speed control on the other;

8A a schematic representation of a known heat pump system with water as a working fluid; and

8B a table showing various pressure / temperature situations for water as working fluid.

1 shows a heat pump 100 with an evaporator for evaporating working fluid in an evaporator space 102 , The heat pump further includes a condenser for liquefying vaporized working fluid in a condenser space 104 coming from a capacitor ground 106 is limited. As it is in 1 is shown, which can be regarded as a sectional view or as a side view, the evaporator chamber 102 at least partially from the condenser space 104 surround. Further, the evaporator room 102 through the condenser bottom 106 from the condenser room 104 separated. In addition, the condenser bottom is with an evaporator bottom 108 connected to the evaporator room 102 define. In one implementation, it is above the evaporator space 102 or somewhere else a compressor 110 provided in 1 is not detailed, however, which is designed in principle to compress vaporized working fluid and as a compressed vapor 112 in the condenser room 104 to lead. The condenser space is also outwardly through a condenser wall 114 limited. The capacitor wall 114 is also like the capacitor bottom 106 at the bottom of the evaporator 108 attached. In particular, the dimensioning of the capacitor bottom 106 in the area that is the interface to the evaporator floor 108 forms, so that the capacitor bottom at the in 1 shown embodiment of the entire condenser space wall 114 is surrounded. This means that the condenser space, as it is in 1 shown extends to the bottom of the evaporator, and that the evaporator space at the same time very far up, typically almost through almost the entire condenser space 104 extends.

This "entangled" or interlocking arrangement of condenser and evaporator, which is characterized in that the condenser bottom is connected to the evaporator bottom, provides a particularly high heat pump efficiency and therefore allows a particularly compact design of a heat pump. The order of magnitude is the dimensioning of the heat pump z. B. in a cylindrical shape so that the capacitor wall 114 represents a cylinder with a diameter between 30 and 90 cm and a height between 40 and 100 cm. However, the dimensioning can be selected depending on the required power class of the heat pump, but preferably takes place in the dimensions mentioned. Thus, a very compact design is achieved, which is also easy and inexpensive to produce, because the number of interfaces, especially for the almost vacuum evaporator space can be easily reduced if the evaporator bottom is carried out in accordance with preferred embodiments of the present invention, that it includes all liquid inlets and outlets and thus no liquid supply and discharge lines from the side or from the top are needed.

It should also be noted that the operating direction of the heat pump is as shown in 1 is shown. This means that the evaporator bottom defines in operation the lower portion of the heat pump, but apart from connecting lines with other heat pumps or to corresponding pump units. This means that in operation, the steam generated in the evaporator chamber rises and is deflected by the motor and is fed from top to bottom in the condenser space, and that the condenser liquid is guided from bottom to top, and then fed from above into the condenser space and then in the condenser room from the top to flows down, such as by individual droplets or by small liquid streams to react with the preferably cross-fed compressed steam for purposes of condensation.

This intertwined arrangement, in that the evaporator is located almost completely or even completely within the condenser, allows for a very efficient heat pump design with optimum space utilization. After the condenser space extends to the evaporator bottom, the condenser space is formed within the entire "height" of the heat pump or at least within a substantial portion of the heat pump. At the same time, however, the evaporation space is as large as possible because it also extends almost almost over the entire height of the heat pump. By interlocking arrangement in contrast to an arrangement in which the evaporator is arranged below the condenser, the space is used optimally. This allows for a particularly efficient operation of the heat pump and on the other a particularly space-saving and compact design, because both the evaporator and the condenser extend over the entire height. Although this is the "thickness" of the evaporator chamber and the condenser space back. However, it has been found that the reduction of the "thickness" of the evaporator space, which tapers within the condenser, is straightforward, because the main evaporation takes place in the lower area, where the evaporator space fills up almost all of the available volume. On the other hand, the reduction of the thickness of the condenser space, especially in the lower area, ie where the evaporator space fills almost the entire available area, uncritical, because the main condensation takes place above, ie where the evaporator chamber is already relatively thin and thus sufficient space for leaves the condenser room. The interlocking arrangement is thus optimal in that each functional space there is given the large volume, where this functional space also requires the large volume. The evaporator compartment has the large volume below while the condenser compartment has the large volume at the top. Nevertheless, also contributes to the corresponding small volume that remains there for the respective function space where the other functional space has the large volume, to an increase in efficiency compared to a heat pump in which the two functional elements are arranged one above the other, as z. B. in the WO 2014072239 A1 the case is.

In preferred embodiments, the compressor is arranged at the top of the condenser space such that the compressed steam is deflected by the compressor on the one hand and at the same time fed into an edge gap of the condenser space. Thus, a condensation is achieved with a particularly high efficiency, because a cross-flow direction of the steam is achieved to a downflowing condensation liquid. This cross-flow condensation is particularly effective in the upper area where the evaporator space is large, and does not require a particularly large area in the lower area where the condenser space is small in favor of the evaporator space, yet still allows condensation of vapor particles penetrated up to this area allow.

An evaporator bottom, which is connected to the condenser bottom, is preferably designed so that it receives the condenser inlet and outlet and the evaporator inlet and outlet in which, in addition to certain bushings for sensors in the evaporator or in the Capacitor can be present. This ensures that no feedthroughs of lines for the condenser inlet and outlet are required by the near-vacuum evaporator. This will make the entire heat pump less prone to failure because any passage through the evaporator would be a potential leak. For this purpose, the condenser bottom is at the points where the condenser feeds and outlets are provided with a respective recess, going to the extent that in the evaporator space, which is defined by the condenser bottom, no capacitor to / discharges.

The condenser space is limited by a condenser wall, which is also attachable to the evaporator bottom. The evaporator bottom thus has an interface for both the condenser wall and the condenser bottom and additionally has all liquid feeds for both the evaporator and the condenser.

In certain embodiments, the evaporator bottom is configured to have spigots for the individual feeders that have a cross section that is different from a cross section of the opening on the other side of the evaporator bottom. The shape of the individual connecting pieces is then designed so that the shape or cross-sectional shape changes over the length of the connecting piece, but the pipe diameter, which plays a role for the flow velocity, is almost equal within a tolerance of ± 10%. This prevents water flowing through the connection pipe from cavitating. This ensures due to the good obtained by the formation of the connecting pieces flow conditions that the corresponding pipes / lines can be made as short as possible, which in turn contributes to a compact design of the entire heat pump.

In a specific implementation of the evaporator bottom of the condenser feed is almost divided in the form of a "glasses" in a two- or multi-part flow. Thus, it is possible to simultaneously feed the capacitor liquid in the condenser at its upper portion at two or more points. Thus, a strong and at the same time particularly uniform condenser flow is achieved from top to bottom, which makes it possible that a highly efficient condensation of the steam also introduced from above into the condenser is achieved.

Another smaller dimensioned feed in the evaporator bottom for condenser water may also be provided to connect a hose which supplies cooling fluid to the compressor motor of the heat pump, not the cold, the liquid supplied to the evaporator is used for cooling, but the warmer, the condenser supplied Liquid, which is still cool enough in typical operating situations to cool the heat pump motor.

The evaporator bottom is characterized by the fact that it has a combination functionality. On the one hand, it ensures that no capacitor feed lines have to be passed through the evaporator, which is under very low pressure. On the other hand, it represents an interface to the outside, which preferably has a circular shape, as in a circular shape as much evaporator surface remains. All inlets and outlets pass through one evaporator base and from there into either the evaporator space or the condenser space. In particular, a production of the evaporator bottom of plastic injection molding is particularly advantageous because the advantageous relatively complicated shapes of the inlet / outlet nozzles in plastic injection molding can be performed easily and inexpensively. On the other hand, it is due to the execution of the evaporator bottom as easily accessible workpiece readily possible to produce the evaporator bottom with sufficient structural stability, so that he can withstand the low evaporator pressure in particular without further ado.

In the present application, like reference numerals refer to like or equivalent elements, and not all reference numerals are repeated in all drawings as they repeat themselves.

2A shows a heat pump system with a heat pump unit, the at least one heat pump stage 200 comprising, wherein the at least one heat pump stage 200 an evaporator 202 , a compressor 204 and a liquefier 206 having. Furthermore, a first heat exchanger 212 provided on a side to be cooled. In addition, a second heat exchanger 214 provided on a side to be heated. The heat pump system also includes a first pump 208 that with the first heat exchanger 212 coupled, and a second pump 210 connected to the second heat exchanger 214 is coupled. The heat pump system has an operating position, ie a position in which it is normally operated. This operating position is the same as in 2A is shown. In the operating position are the first pump 208 and the second pump 210 above the first heat exchanger 212 and the second heat exchanger 214 arranged. In addition, the heat pump unit, which is the at least one heat pump stage 200 includes, above the first pump 208 and the second pump 210 arranged.

The first heat exchanger 212 includes an inlet 240 and a process 241 , The feed 240 and the process 241 are coupled to the heat pump unit. In the implementation where the heat pump unit has only a single heat pump stage, as exemplified in FIG 2A at 200 is shown, is the inlet 240 in the heat exchanger 212 over the pump 208 with an evaporator drain 220 over a pipeline 208 in front of the pump 208 and a pipeline 230 after the pump 208 coupled. In addition, the process is 241 from the heat exchanger 212 with the evaporator inlet 222 of the evaporator 202 over a pipeline 234 coupled. In addition, a Kondensiererablauf 224 of the condenser or condenser 206 over the pump 210 and a pipe 236 with a feed 242 in the second heat exchanger 214 coupled. There is also a process 243 of the second heat exchanger 214 via a pipe with a condenser or condenser feed 226 of the liquefier 206 coupled. It should be noted, however, that the pipes 228 . 232 . 234 . 238 can also be coupled to other elements, especially if the heat pump unit not only the one stage 208 but has two stages, as exemplified in the 3A . 3B . 4A . 5 . 6A to 6D is shown. It should be noted, however, that the heat pump unit may comprise any number of stages, that is to say, for example, other than two stages, also three stages, four, five, etc. stages.

At the in 2A shown embodiment, the inlet and the outlet of the first heat exchanger in the operating position are arranged perpendicular or at least at an angle less than 45 ° to a vertical. Further, a suction side of the pump 208 over the pipe 228 with the heat pump unit and here by way of example with the evaporator sequence 220 coupled. It should also be noted that in the line 228 as well as in the line 234 as indicated by the arrows is shown in operation, a flow of working fluid flows from top to bottom. Accordingly, the feed 242 in the second heat exchanger and the drain 243 from the second heat exchanger with pipes 234 . 236 . 238 connected, with the intervening pump 208 respectively. 210 These tubes are as far as possible vertically and in any case at an angle less than 45 °. This optimum alignment of the heat pump system and in particular the individual components of the heat pump system is achieved, because especially the suction sides of the pump 208 . 210 each in a vertical vertical downpipe 228 respectively. 234 are arranged. Thus, an optimal back pressure is present in front of the respective pump, to the effect that the pumps 208 . 210 work without or only with very little cavitation.

In addition, it is preferred that the heat exchangers 212 . 214 are arranged horizontally. This has the advantage that when filling the system no air pockets in the heat exchanger take place, so that the heat exchanger are self-venting. Lying also means that the heat exchangers are parallelepiped-shaped, and thus have a base area which is smaller in area than the side surface. The heat exchanger 212 and the heat exchanger 214 thus have an elongated shape, wherein the longer side of the cuboid lying, that is horizontal or at an angle less than 45 ° with respect to the horizontal is arranged.

It should also be noted that the two pumps 208 . 210 closer to the first heat exchanger or the second heat exchanger 214 are arranged as at a connection point on the heat pump unit. This means that the pipe 228 longer than the tube 230 is, and that too the pipe 234 longer than the tube 236 is.

Further, the heat pump unit is configured such that at least one inlet or outlet of an evaporator or condenser of a heat pump stage connected to the first heat exchanger or the second heat exchanger is arranged to be vertically downwardly or vertically out of the heat pump stage in the operating position Angle less than 45 ° from a vertical exit from the heat pump stage. The outlets 220 . 234 or the inlets 222 . 226 are drawn vertically, this position is preferred. In addition, the heat pump stage 200 preferably formed in the entangled arrangement, as they are also based on 1 has been described that, namely, a steam supply channel 250 , through the steam from the evaporator 202 to the compressor 204 is passed in the corresponding capacitor extends. In addition, the heat pump stage 200 preferably formed in the entangled arrangement, as they are also based on 1 has been described that, namely, a steam supply channel 250 , through the steam from the evaporator 202 to the compressor 204 passed through the liquefier 206 extends. In addition, the steam supply duct is between the compressor 204 and the condenser 206 who at 251 is drawn above the condenser 206 appropriate.

In addition, the liquefier 204 as it is in 2A is also shown arranged above the condenser 206 extends so that in an off-state working fluid from the compressor away due to gravity. So the compressor is in a dry state when the heat pump stage 200 is deactivated, which is done by the fact that the compressor motor 204 is turned off.

In addition, it should be noted that water is preferably used as the working medium, wherein the at least one heat pump stage is designed to hold a pressure at which the water can evaporate at temperatures below 50 ° C. In particular, in the two-stage arrangement, with reference still to 3A . 3B . 4A . 6A to 6D and 5 is pointed out, the evaporation will take place in the first heat pump stage, for example, at temperatures of 20 ° C to 30 ° C and the evaporation in the second heat pump stage z. B. at temperatures between 40 ° C and 50 ° C take place. Depending on the implementation, however, the temperatures may be lower, as exemplified by 8th or 7C is shown.

Preferably, the entire heat pump system is mounted on a support frame, which is not shown. In particular, the first and second heat exchangers 212 . 214 attached to the bottom of the support frame. In addition, the first pump and the second pump are connected by a pump holder and are as a pump module to the support frame above the first and the second heat exchanger 212 . 214 attached. The at least one heat pump stage is then arranged above the pump carrier.

In preferred embodiments, the heat pump system is formed with two stages and has a height that is less than 2.50 m, a width that is less than 2 m, and a depth that is less than 1 m.

2A shows the first aspect, in which the heat pump system arranged at a lower end having the heat exchanger.

On the other hand shows 2 B the second aspect, in which the pumps are arranged at the bottom and in preferred implementations of the second aspect, the heat exchangers 212 . 214 standing and / or arranged next to the pumps. In particular, according to the second aspect is in 2 B a heat pump system shown the heat pump stage 200 with the first compressor 204 , the first liquefier 206 and the first evaporator 202 having. In addition, as it is in 2A shown is an expansion organ 207 provided to the liquid balance between the condenser 206 and the evaporator 202 to accomplish. In addition, the first heat exchanger 212 and the second heat exchanger 214 associated with a side to be cooled or a side to be heated. In addition, the first pump 208 and the second pump 210 provided, the first pump 208 with the first heat exchanger 212 coupled, and wherein the second pump 210 with the second heat exchanger 214 is coupled. Again, the heat pump plant has an operating position that is as shown schematically in FIG 2 B is shown.

The first and second pumps are in the operating position below the heat pump unit 200 arranged at a lower end of the heat pump system. Moreover, in the operating position, the first heat exchanger and the second heat exchanger are also below the heat pump unit at the lower end adjacent to the pumps 208 . 210 arranged as it is schematic in 2 B is shown. In particular, the first pump 208 and the second pump 210 arranged so that a pumping direction of the respective pump in the operating position is horizontal or deviates by at most ± 45 ° from the horizontal. In addition, the two heat exchangers 212 . 214 or at least one of the two heat exchangers 212 . 214 arranged standing, wherein the first connection 240 . 242 of the first and second heat exchanger 212 . 214 with a pump side of the respective pump 208 . 210 is coupled, and wherein the second port 241 . 243 of the first and second heat exchanger 212 respectively. 214 above the respective first connection 240 . 242 the corresponding heat exchanger is arranged. In other words, the heat exchanger 212 arranged so that the second connection 241 which is the drain from the first heat exchanger 212 represents, in the operating direction above the first port 240 is arranged, which represents the inlet. Accordingly, in the second heat exchanger 214 the sequence, ie the second connection 243 in operating position above the inlet 242 or the first connection 242 of the second heat exchanger 214 arranged. The standing arrangement is advantageous because it avoids trapped air when filling the heat exchanger. In addition, by the vertical position of the heat exchanger, the pipe connection, and in particular the pipe 232 respectively. 238 shorter compared to a horizontal arrangement. This is due to the fact that the extent of the heat exchanger is used in a sense already as a connecting pipe. The heat exchanger is thus used not only as a heat exchanger element, but also as a connecting line.

In addition, the pumps are arranged as far down as possible, and preferably horizontally, so that the necessary back pressure before the suction side of the pump by a maximum long vertical pipe in front of the pump at a given height of the entire heat pump system is readily achieved to a pump cavitation avoid. Furthermore, the first tube comprises 228 through which the evaporator outlet 220 with the suction side of the pump 208 coupled, a curvature, wherein it is preferred that the curvature closer to the suction side of the pump 208 as at the evaporator exit 220 is arranged. Accordingly, the curvature in the second tube 234 from the condenser output 224 to the suction side of the pump 210 closer to the pump than to the condenser exit 224 arranged to have as long as possible vertical distance, through which the necessary back pressure is achieved, so already receives the falling working fluid a good boost of kinetic energy.

3A shows a third aspect of a heat pump system, wherein the heat pump system of the third stage may have any arrangement of pumps or heat exchangers, however, as still with reference to the 3B . 4A . 5 is preferred, it is preferred to use the arrangement according to the first aspect. Alternatively, however, the arrangement according to the second aspect, ie with as far as possible arranged below pumps and preferably stationary heat exchangers can be used.

In particular, a heat pump system, as in 3A a heat pump stage is shown 200 ie the stage n + 1 with a first evaporator 202 , a first compressor 204 and a first liquefier 206 , where the evaporator 202 over the steam channel 250 with the compressor 204 coupled, and once the compressor 204 over the steam channel 251 with the liquefier 206 is coupled. It is preferred to use the entangled arrangement again, but any arrangements in the heat pump stage may be used 200 be used. The entrance 222 in the evaporator 202 and the exit 220 from the evaporator 202 Depending on the implementation, either with an area to be cooled or with a heat exchanger, such as the heat exchanger 212 to the area to be cooled or with another pre-arranged heat pump stage, namely for example the Heat pump stage n connected, where n is an integer greater than or equal to zero.

In addition, the heat pump system includes in 3A another heat pump stage 300 ie stage n + 2, with a second evaporator 302 , a second compressor 304 and a second condenser 306. , In particular, the output is 224 of the first condenser with an evaporator inlet 322 of the second evaporator 320 over a connecting line 332 connected. The exit 320 of the evaporator 302 the further heat pump stage 300 Depending on the implementation with the inlet to the condenser 206 the first heat pump stage 200 be connected, as indicated by a dashed connection line 334 is shown. The exit 320 of the evaporator 302 However, as it is still based on the 4A . 6A to 6D and 5 shown connected to a controllable way module to achieve alternative implementations. Generally, however, due to the fixed connection of the condenser outlet 224 the first heat pump stage with the evaporator inlet 322 the other heat pump stage reaches a derailleur.

This derailleur ensures that each heat pump stage must work with the lowest possible temperature spread, so with the smallest possible difference between the heated working fluid and the cooled working fluid. By connecting in series, so by a chain circuit such heat pump stages is thus achieved that nevertheless a sufficiently large total spread is achieved. The total spread is thus divided into several individual spreads. The derailleur is particularly of particular advantage because it allows much more efficient work. The consumption of compressor power for two stages, each of which has to cope with a smaller temperature spread, is smaller than the compressor power for a single heat pump stage, which must reach a large temperature spread. In addition, the requirements for the individual components with two stages connected in chain are technically more relaxed.

As it is in 3A shown, the condenser outlet 324 of the liquefier 306. the further heat pump stage 300 coupled with the area to be heated, as z. B. Referring to 3B by the heat exchanger 214 is shown. Alternatively, however, the output 324 of the liquefier 306. the second heat pump stage again be coupled via a connecting pipe with an evaporator of another heat pump stage, so the (n + 3) heat pump stage. 3A Thus, depending on the implementation, a chain circuit of z. B. four heat pump stages, when n = 1 is taken. However, if n is taken arbitrarily, shows 3A a derailleur of any number of heat pump stages, in particular the derailleur of the heat pump stage (n + 1), with 200 is designated, and the further heat pump stage 300 , which is denoted by (n + 2), is carried out in more detail and the n-type heat pump stage as well as the (n + 3) heat pump stage can not be designed as a heat pump stage, but each as a heat exchanger or as to be cooled or heated area ,

Preferably, as it is z. In 3B is shown, the condenser of the first heat pump stage 200 above the evaporator 302 arranged the second heat pump stage, so that the working fluid through the connecting line 332 flowing due to gravity. Especially at the in 3B shown special implementation of the individual heat pump stages, the condenser is arranged anyway above the evaporator. This implementation is particularly advantageous because, even with heat pump stages aligned with one another, the liquid already passes from the first stage condenser to the second stage evaporator through the connection line 332 flows. In addition, however, it is preferred to achieve a height difference that includes at least 5 cm between the top of the first stage and the top of the second stage. This dimension, at 340 in 3B is shown, but is preferably 20 cm, since then for the implementation described optimum water supply from the first stage 200 to the second stage 300 over the connecting line 332 takes place. This also ensures that in the connecting line 332 no special pump is needed. This pump is therefore saved. It will only be the DC link pump 330 needed to get out of the exit 320 the evaporator of the second stage 300 , which is arranged lower than the first stage, the working fluid back into the first-stage condenser, ie in the input 226 bring to. This is the output 320 over the pipeline 334 with the suction side of the pump 330 connected. The pump side of the pump 330 is over the pipe 336 with the entrance 226 connected to the condenser. In the 3B shown chain circuit of the two stages corresponds 3A with the connection 334 , Preferably, the intermediate circuit pump 330 also like the other two pumps 208 and 210 arranged below, because then in the intermediate circuit 334 Cavitation can be prevented because of the placement of the DC link pump 330 in the downpipe 334 a sufficient back pressure of the pump is achieved.

Although in 3B the configuration according to the first aspect is shown, that is the heat exchangers 212 . 214 below the pumps 208 . 210 and 330 can also be arranged, the arrangement of the pumps 208 . 210 next to the heat exchangers 212 . 214 used as set forth in the second aspect.

As it is in 3B is shown, the first stage comprises the expansion element 207 and the second stage an expansion element 307 , However, because of the connecting line 332 anyway working fluid from the condenser 206 The first stage exit is the expansion element 207 dispensable. In contrast, the expansion element 307 preferably used in the lower step. Thus, in one embodiment, the first stage can be built without an expansion element, and it merely becomes an expansion element 307 provided in the second stage. However, since it is preferred to build all stages the same, it is also in the heat pump stage 200 the expansion element 207 intended. If implemented to support bubble boiling, then the expansion element is 207 despite the fact that it may not conduct liquefied working fluid into the evaporator, but only heated steam, also helpful.

Nevertheless, it has been found that at the in 3B shown arrangement working fluid in the evaporator 302 the second heat pump stage 300 accumulates. It will, therefore, as it is in 5 is shown a measure made to remove working fluid from the evaporator 302 the second heat pump stage 300 in the evaporator circuit of the first stage 200 bring to. This is an overflow arrangement 502 in the second evaporator 302 the second heat pump stage arranged to from a predefined maximum working fluid level in the second evaporator 302 Leading away working fluid. Further, a liquid line 504 . 506 . 508 provided, on the one hand with the overflow arrangement 502 coupled, on the other hand, with a suction side of the first pump 208 at a coupling point 512 is coupled. At the coupling point 512 is a pressure reducer 510 present, which is preferably designed as a pressure reducer to Bernoulli, so as a pipe or Schlauchengstelle. The fluid conduit includes a first connection portion 504 , a U-shaped section 506 and a second connecting portion 508 , Preferably, the U-shaped section 506 a vertical height in the operating position which is at least equal to 5 cm and preferably 15 cm. This provides a self-regulating system that operates without a pump. If the water level in the evaporator is too high 302 of the lower container 300 working fluid runs over the connecting line 504 in the U-tube 506 , The U-tube is over the connecting line 508 at the coupling point 512 on the pressure reducer with the suction side of the pump 208 coupled. Due to the increased flow speed in front of the pump due to the bottleneck 510 decreases the pressure and water from the U-tube 506 can be recorded. In the U-tube, a stable water level is established, which is sufficient for the pressure in front of the pump in the constriction and in the evaporator of the lower tank. At the same time, the U-tube represents 506 but a vapor barrier, in that no vapor from the evaporator 302 into the suction side of the pump 208 can get. The expansion organs 207 respectively. 307 are preferably also designed as overflow arrangements, in order to bring working fluid into the respective evaporator when a predetermined level in a respective condenser is exceeded. Thus, the levels of all containers, so all condenser and evaporator in both heat pump stages automatically, without effort and without pumps but set self-regulating.

This is particularly advantageous because it allows heat pump stages to be run or shut down depending on the operating mode.

4A and 5 already show a detailed representation of a controllable roadside module due to the upper 2 × 2-way switch 421 and the lower 2 × 2-way switch 422 , 4B shows a general implementation of the controllable roadside module 420 that through the two serially connected 2 × 2-way switches 421 and 422 can be implemented, but also implemented alternatively. can.

The controllable way module 420 from 4B is with a controller 430 coupled to from this via a control line 431 to be controlled. The controller receives as input signals sensor signals 432 and provides output pump control signals 436 and / or compressor motor control signals 434 , The compressor motor control signals 434 lead to the compressor motors 204 . 304 as they are for example in 4A are shown, and the pump control signals 436 lead to the pumps 208 . 210 . 330 , Depending on the implementation, the pumps can 208 . 210 However, fixed, so run uncontrolled because they anyway in each of the basis of the 7A . 7B run operating modes described. Only the intermediate circuit pump 330 could therefore be due to a pump control signal 436 to be controlled.

The controllable way module 420 includes a first entrance 401 , a second entrance 402 and a third entrance 403 , As it is for example in 4A is shown, is the first input 401 with the process 241 of the first heat exchanger 212 connected. In addition, the second entrance 402 the controllable way module with the return or expiration 243 of the second heat exchanger 214 connected. In addition, the third entrance 403 of the controllable way module 420 with a pump side of the intermediate circuit pump 330 connected.

A first exit 411 of the controllable way module 420 is with an entrance 222 in the first heat pump stage 200 coupled. A second exit 412 of the controllable way module 420 is with an entrance 226 into the liquefier 206 connected to the first heat pump stage. In addition, there is a third exit 413 of the controllable way module 420 with the entrance 326 into the liquefier 306. the second heat pump stage 300 connected.

The various input / output connections through the controllable way module 420 be reached are in 4C shown.

In one mode, high performance mode (HLM) is the first input 401 with the first exit 411 connected. Furthermore, the second entrance 402 with the third exit 413 connected. In addition, the third entrance 403 with the second exit 412 connected as it is in the line 451 from 4C is shown.

In mid-power mode (MLM), in which only the first stage is active and the second stage is inactive, ie the compressor motor 304 the second stage 300 is turned off, is the first input 401 with the first exit 411 connected. Furthermore, the second entrance 402 with the second exit 412 connected. In addition, the third entrance 403 with the third exit 413 connected as it is in line 452 is shown. row 453 shows the free cooling mode in which the first input is connected to the second output, so the input 401 with the exit 412 , In addition, the second entrance 402 with the first exit 411 connected. Finally, the third entrance 403 with the third exit 413 connected.

In low power mode (NLM), in line 454 is shown, is the first input 401 with the third exit 413 connected. In addition, the second entrance 402 with the first exit 411 connected. Finally, the third entrance 403 with the second exit 412 connected.

It is preferred that the controllable path module through the two serially arranged 2-way switch 421 and 422 to implement, as z. In 4A are shown, or as they are in the 6A to 6D are shown. Here is the first 2-way switch 421 the first entrance 401 , the second entrance 402 , the first exit 411 and a second exit 414 that has an interconnect 406 with an entrance 404 of the second 2-way switch 422 is coupled. The 2-way switch has the third input 403 as an additional input and the second output 412 as output and the third output 413 also as an exit.

The positions of the two 2 × 2-way switches 421 are in 7B tabulated. 6A shows the two positions of the switches 421 . 422 in high performance mode (HLM). This corresponds to the first line in 7B , 6B shows the position of the two switches in mid-power mode. The upper switch 421 is exactly the same in mid-power mode as it is in high-performance mode. Only the lower switch 422 has been switched. In the free cooling mode, the in 6C is shown, the bottom switch is the same as in mid-power mode. Only the upper switch has been switched. In low power mode, finally, the bottom switch 422 switched over in the free cooling mode, while the upper switch in low power mode is equal to its position in the free cooling mode. This ensures that only one switch needs to be switched from one neighboring mode to the next mode, while the other switch can remain in its position. This simplifies the entire switching action from one operating mode to the next.

7A shows the activities of each compressor motors and pumps in the different modes. In all modes are the first pump 208 and the second pump 210 active. The intermediate circuit pump is active in the high power mode, the mid power mode, and the free cooling mode, but is deactivated in the low power mode.

The compressor motor 204 The first stage is active in high power mode, mid power mode, and free cooling mode, and is disabled in low power mode. In addition, the second stage compressor motor is only active in high power mode but disabled in mid power mode, free cooling mode and low power mode.

It should be noted that 4A represents the low power mode in which the two motors 204 . 304 are disabled, and in which also the intermediate circuit pump 330 is activated. On the other hand shows 3B the so-called high performance mode, where both motors and pumps are active. 5 again shows the high power mode, in which the switch positions are such that exactly the configuration according to 3B is obtained.

6A and 6C also show various temperature sensors. A sensor 602 measures the temperature at the outlet of the first one heat exchanger 212 , ie at the return from the side to be cooled. A second sensor 604 Measures the temperature at the return of the side to be heated, ie from the second heat exchanger 214 , Furthermore, measures another temperature sensor 606 the temperature at the exit 220 the evaporator of the first stage, wherein this temperature is typically the coldest temperature. In addition, another temperature sensor 608 provided that the temperature in the connecting line 332 measures, so at the output of the first stage of the condenser, in other figures with 224 is designated. In addition, the temperature sensor measures 610 the temperature at the outlet of the second stage evaporator 300 So at the exit 320 from 3B for example.

Finally, the temperature sensor measures 612 the temperature at the exit 324 of the liquefier 306. the second stage 300 In the full power mode, this temperature is the warmest temperature in the system.

Hereinafter, referring to the 7C and 7D on the various stages or operating modes of the heat pump system, as for example, based on the 6A to 6D is shown, and also illustrated with reference to the other figures, received.

The DE 10 2012 208 174 A1 discloses a heat pump with a free cooling mode. In the free cooling mode, the evaporator inlet is connected to a return from the area to be heated. Further, the condenser inlet is connected to a return from the area to be cooled. By free cooling mode, a considerable increase in efficiency is already achieved, in particular for outdoor temperatures less than z. 22 ° C.

This free cooling mode or (FKM) is in line 453 in 4C is shown and is particularly in 6C shown. In particular, the output of the cold side heat exchanger is connected to the input to the first stage condenser. In addition, the output is from the heat-side heat exchanger 214 coupled to the evaporator inlet of the first stage, and is the entrance to the heat-side heat exchanger 214 with the second stage condenser drain 300 connected. However, the second stage is deactivated, so that the Kondensiererablauf 338 from 6C for example, the same temperature as the condenser inlet 413 Has. In addition, also has the evaporator process 334 the second stage the same temperature as the condenser inlet 413 the second stage, so that the second stage 300 thermodynamically "short-circuited" as it were. However, although the compressor motor is deactivated, this stage is flowed through by working fluid. The second stage is therefore still used as infrastructure, but is disabled due to the compressor motor switched off.

Should now z. B. switched from the middle power mode in the high performance mode, ie from a mode in which the second stage is deactivated and the first stage is active, in a mode in which both stages are active, it is preferred, first the compressor motor a certain time, for example, is greater than one minute, and preferably 5 minutes to let run, before then the switch 422 from the in 6B shown switch position in the in 6A switch position shown is switched.

A heat pump according to one aspect includes an evaporator having an evaporator inlet and an evaporator outlet and a condenser having a condenser inlet and a condenser outlet. In addition, a switching device is provided to operate the heat pump in an operating mode or other operating mode. In the one operating mode, the low-power mode, the heat pump is completely bypassed, in that the return of the area to be cooled is connected directly to the trace of the area to be heated. Moreover, in this lock-up mode or low-power mode, the return of the area to be heated is connected to the trace of the area to be cooled. Typically, the evaporator is assigned to the area to be cooled and the condenser is assigned to the area to be heated.

However, in the bridging mode, the evaporator is not connected to the area to be cooled, nor is the condenser connected to the area to be cooled, but both areas are effectively "shorted". In the second alternative mode of operation, on the other hand, the heat pump is not bypassed, but is operated at still relatively low temperatures, typically in the free cooling mode, or in normal mode with one or two stages. In the free cooling mode, the switching means is arranged to connect a return of the area to be cooled with the condenser inlet and to connect a return of the heating area with the evaporator inlet. In contrast, the switching means is formed in the normal mode to connect the return of the area to be cooled with the evaporator inlet and to connect the return of the area to be heated with the condenser inlet.

Depending on the embodiment, at the output of the heat pump, so the condenser side, or at the entrance of the heat pump, so the evaporator side, a heat exchanger may be provided to fluidly decouple the inner heat pump cycle from the outer circuit. In this case, the evaporator inlet is the inlet of the heat exchanger coupled to the evaporator. Moreover, in this case, the evaporator outlet constitutes the outlet of the heat exchanger, which in turn is coupled to the evaporator.

Similarly, at the condenser side, the condenser outlet is a heat exchanger outlet, and the condenser inlet is a heat exchanger inlet, on the side of the heat exchanger that is not coupled to the actual condenser.

Alternatively, however, the heat pump can be operated without input-side or output-side heat exchanger. Then z. B. at the entrance into the area to be cooled or at the entrance to the area to be heated in each case a heat exchanger may be provided, which then comprises the return or trace to the cooling area or to the area to be heated.

In preferred embodiments, the heat pump is used for cooling, so that the area to be cooled, for example, in the space of a building, a computer room or a refrigerator in general, while the area to be heated z. B. is a roof of a building or a similar location where a heat dissipation device can be placed to deliver heat to the environment. However, if the heat pump is alternatively used for heating, the area to be cooled is the environment from which energy is to be extracted and the area to be heated is the "utility", such as the interior of a building, a house or a room to be tempered.

The heat pump is thus capable of switching from the bypass mode to either the free cooling mode or, if such free cooling mode is not established, to the normal mode.

In general, the heat pump is advantageous in that it is particularly efficient when outside temperatures are present, the z. B. are less than 16 ° C, which is often the case, at least in the northern and southern hemisphere distant from the equator.

This ensures that outside temperatures, where direct cooling is possible, the heat pump can be completely taken out of service. In the case of a heat pump with a radial compressor between the evaporator and the condenser, the radial wheel can be stopped and no energy needs to be put into the heat pump. Alternatively, however, the heat pump may still be in a standby mode or the like, but since it is only a standby mode, it will consume only a small amount of power. Especially with valveless heat pumps, as they are preferably used, a thermal short circuit can be avoided by complete bridging of the heat pump in contrast to the free cooling mode.

Moreover, it is preferred that in the first operating mode, ie in the low-power or bypass mode, the switching device completely separates the return of the area to be cooled or the trace of the area to be cooled from the evaporator, so that no fluid connection between the inlet and outlet of the evaporator and more to the area to be cooled. This complete separation will also be beneficial on the condenser side.

In implementations, a temperature sensing device is provided that senses a first temperature with respect to the evaporator or a second temperature with respect to the condenser. Furthermore, the heat pump has a controller, which is coupled to the temperature sensor device and is designed to control the switching device depending on one or more temperatures detected in the heat pump, so that the switching device switches from the first to the second operating mode or vice versa. The implementation of the switching device can be implemented by an input switch and an output switch, each having four inputs and four outputs and switchable depending on the mode. Alternatively, however, the switching device can also be implemented by a plurality of individual cascaded switches, each having an input and two outputs.

Furthermore, as a coupling element for coupling the bridging line with the Hinlauf in the area to be heated or the coupler for coupling the bridging line with the Hinlauf in the area to be cooled as a simple three-terminal combination may be formed, ie as a liquid adder. In implementations, however, in order to have optimal decoupling, it is preferred that the couplers also be implemented as switches or integrated in the input / output switch.

In addition, a first temperature sensor is used on the evaporator side as a special temperature sensor and is used as a second temperature sensor, a second temperature sensor on the condenser side, with a more direct Measurement is preferred. The evaporator-side measurement is used in particular to a speed control of Temperaturanhebers so z. As a compressor of the first and / or second stage to make while the condenser-side measurement or even an ambient temperature measurement is used to perform a mode control, ie the heat pump z. B. switch from the lock-up mode in the free cooling mode when a temperature is no longer in the very cold temperature range, but in the medium-temperature temperature range. However, if the temperature is higher, ie in a warm temperature range, then the switching device will bring the heat pump into a normal mode with first active stage or with two active stages.

In a two-stage heat pump, however, in this normal mode, which corresponds to the medium power mode, only a first stage will be active, while the second stage is still inactive, so is not powered and therefore requires no energy. Only when the temperature continues to rise, in a very warm area, in addition to the first heat pump stage or in addition to the first pressure stage, a second pressure stage is activated, which in turn has an evaporator, a temperature booster typically in the form of a radial compressor and a condenser. The second pressure stage can be connected in series or in parallel or serially / parallel to the first pressure stage.

To ensure that in the bypass mode, ie when the outside temperatures are already relatively cold, the cold from the outside does not completely penetrate the heat pump system and beyond in the room to be cooled, making the room to be cooled even colder than it should be, For example, it is preferable to provide a control signal from a sensor signal on the trace into the area to be cooled or at the return of the area to be cooled, which can be used by a heat dissipation device mounted outside the heat pump to control heat dissipation; H. then, when the temperatures get too cold, reduce. The heat dissipation device is, for example, a liquid / air heat exchanger, with a pump for circulating the liquid brought into the area to be heated. Further, the heat dissipation device may include a fan to transport air into the air heat exchanger. Additionally or alternatively, a three-way mixer may be provided to partially or completely short the air heat exchanger. Depending on the trace in the area to be cooled, which is connected in this bridging mode but not with the evaporator outlet, but with the return from the area to be heated, the heat dissipation device, so for example, the pump, the fan or the three-way mixer in order to further reduce the heat output so that a temperature level is maintained, in the heat pump system and in the area to be cooled, which in this case may be above the outside temperature level. Thus, the waste heat can even be used for heating the "room to be cooled" if the outside temperatures are too cold.

In a further aspect, an entire control of the heat pump is made so that a "fine control" of the heat pump is made depending on a temperature sensor output signal of a temperature sensor on the evaporator side, so a speed control in the different modes, ie z. The free-cooling mode, the first-stage normal mode and the second-stage normal mode, and also a heat release device control in the bypass mode, while a mode switching is performed based on a temperature sensor output of a condenser temperature sensor as coarse control. Thus, only on the basis of a condenser-side temperature sensor operating mode switching from the bypass mode (or NLM) in the free cooling mode (or FKM) and / or in the normal mode (MLM or HLM) made, wherein the decision whether a switch takes place, the evaporator-side temperature output signal is not taken becomes. However, only the evaporator-side temperature output signal is used for the speed control of the centrifugal compressor or for the control of the heat dissipation devices, but not the condenser-side sensor output signal.

It should be noted that the various aspects of the present invention regarding the arrangement and the two-stage, as well as the use of the bypass mode, the control of the heat dissipation device in the lock-up mode or free cooling mode and the control of the centrifugal compressor in the free cooling mode or the normal operating mode or with respect to Using two sensors, one sensor for operating mode switching and the other fine-tuning sensor, can be used independently. However, these aspects can also be combined in pairs, or in larger groups or together.

7A to 7D show an overview of different modes in which the heat pump according to 1 . 2 . 8A . 9A is operable. If the temperature of the area to be heated is very cold, such as less than 16 ° C, then the operating mode selection will activate the first operating mode in which the heat pump bypasses is and the control signal 36b for the heat dissipation device in the area to be heated 16 is produced. Is the temperature of the area to be heated, ie the area 16 from 1 in a medium cold temperature range, ie z. B. in a range between 16 ° C and 22 ° C, the operating mode control will activate the free cooling mode, in which due to the low temperature spread, the first stage of the heat pump can work low power. However, if the temperature of the area to be heated in a warm temperature range, for example between 22 ° C and 28 ° C, the heat pump is operated in the normal mode, but in the normal mode with a first heat pump stage. However, if the outside temperature is very warm, ie in a temperature range between 28 ° C and 40 ° C, a second heat pump stage is activated, which also works in normal mode and already supports the first stage continuously.

Preferably, a speed control or "fine control" of a centrifugal compressor within the Temperaturanhebers 34 from 1 in the temperature ranges "medium cold", "warm", "very warm" in order to operate the heat pump only with the heat / cooling capacity that is required by the actual requirements.

Preferably, the mode switching is controlled by a condenser-side temperature sensor, while the fine control or the control signal for the first operating mode depends on an evaporator-side temperature.

It should be noted that the temperature ranges are "very cold", "medium cold", "warm", "very warm" for different temperature ranges, the respective average temperature of very cold to medium cold, too warm, too hot respectively larger. The areas can, as it is based on 7C has been shown, directly adjacent to each other. However, in embodiments, the regions may also overlap and be at the stated temperature level or at any other higher or lower temperature level. Furthermore, the heat pump is preferably operated with water as a working medium. However, other means may be used depending on the requirement.

This is in 7D tabulated. If the condenser temperature is in a very cold temperature range, in response to the control 430 the first operating mode is set. If it is found in this mode that the evaporator temperature is lower than a setpoint temperature, a reduction in the heat output is achieved by a control signal at the heat dissipation device. However, if the condenser temperature is in the medium-cold range, then in response to a switch to the free cooling mode of the controller 430 to expect it through the pipes 431 and 434 is shown. If the evaporator temperature is greater than a setpoint temperature, this will result in an increase in the speed of the compressor radial compressor via the control line 434 , In turn, if it is determined that the condenser temperature is in a warm temperature range, in response to this, the first stage is put into normal operation, indicated by a signal on the line 434 happens. In turn, if it is found that at a certain speed of the compressor, the evaporator temperature is still greater than a desired temperature, then this leads to an increase in the speed of the first stage again via the control signal on the line 434 , Finally, if it is found that the condenser temperature is in a very warm temperature range, a second stage is activated in normal operation in response to this, again by a signal on the line 434 happens. Depending on whether the evaporator temperature is greater or less than a target temperature, as indicated by signals on the line 432 is signaled, then a control of the first and / or the second stage is made to respond to a changed situation.

Thus, a transparent and efficient control is achieved, on the one hand, a "coarse tuning" due to the mode switching and on the other a "fine-tuning" due to the temperature-dependent speed adjustment, to the effect that always only as much energy must be consumed, as is actually needed , This procedure, in which there is also no permanent on-off in a heat pump, such as in known heat pumps with hysteresis also ensures that due to the continuous operation no start-up losses.

Preferably, a speed control or "fine control" of a centrifugal compressor within the compressor motor of 1 in the temperature ranges "medium cold", "warm", "very warm" in order to operate the heat pump only with the heat / cooling capacity that is required by the actual requirements.

Preferably, the mode switching is controlled by a condenser-side temperature sensor, while the fine control or the control signal for the first operating mode depends on an evaporator-side temperature.

In mode switching, the controller is 430 is configured to detect a condition for a transition from the middle power mode to the high power module. Then the compressor 304 in the further heat pump stage 300 started. Only after a predetermined time greater than one minute has elapsed, and preferably even greater than four or even five minutes, will the controllable path module switch from the mid-power mode to the high-power mode. This ensures that can be easily switched from a standstill, with the running of the compressor motor before switching ensures that the pressure in the evaporator is smaller than the pressure in the compressor.

It should be noted that the temperature ranges in 7C can be varied. In particular, the threshold temperatures, between a very cold temperature and a medium cold temperature, ie the value 16 ° C in 7C and between the medium cold temperature and the warm temperature, ie the value 22 ° C in 7C and the value between the warm and the very warm temperature, that is the value 28 ° C in 7C only as an example. Preferably, the threshold temperature between warm and very warm, in which a switchover from the mid-power mode to the high-power mode takes place, is between 25 and 30 ° C. Further, the threshold temperature between warm and medium cold, that is, when switching between the free cooling mode and the medium power mode, in a temperature range between 18 and 24 ° C. Finally, the threshold temperature at which switching between the medium cold mode and the very cold mode is in a range between 12 and 20 ° C, the values are preferably selected as shown in the table in FIG 7C However, as mentioned, can be set differently in the above areas.

Depending on the implementation and requirement profile, however, the heat pump system can also operate in four operating modes, which are also different, but all are at a different absolute level, so that the terms "very cold", "medium cold", "warm", "very warm "Are to be understood only relative to each other, but are not intended to represent absolute temperature values.

Although certain elements are described as device elements, it should be understood that this description is likewise to be regarded as a description of steps of a method and vice versa. For example, in the 6A to 6D described block diagrams alike flowcharts of a corresponding method according to the invention.

Furthermore, it should be noted that the control, for example, by the element 430 in 4B can be implemented as software or hardware, and this also applies to the tables in the 4C . 4D , or 7A . 7B . 7C . 7D applies. The implementation of the controller may be on a non-volatile storage medium, a digital or other storage medium, in particular a floppy disk or CD with electronically readable control signals, which may interact with a programmable computer system such that the corresponding method of pumping heat or operating a heat pump is running. In general, the invention thus also comprises a computer program product with a program code stored on a machine-readable carrier for carrying out the method when the computer program product runs on a computer. In other words, the invention can thus also be realized as a computer program with a program code for carrying out the method when the computer program runs on a computer.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 2016349 B1 [0002]
• DE 4431887 A1 [0014]
• WO 2014072239 A1 [0015, 0058]
• DE 102012208174 A1 [0107]

Claims (32)

Heat pump system having the following features: a heat pump unit with at least one heat pump stage ( 200 ), wherein the at least one heat pump stage ( 200 ) an evaporator ( 202 ), a compressor ( 204 ) and a liquefier ( 206 ) having; a first heat exchanger ( 212 ) on a side to be cooled; a second heat exchanger ( 214 ) on a side to be heated; a first pump ( 208 ) connected to the first heat exchanger ( 212 ) is coupled; and a second pump ( 210 ) connected to the second heat exchanger ( 214 ), wherein the heat pump system has an operating position, wherein the heat pump unit in the operating position above the first pump ( 208 ) and the second pump ( 210 ), wherein in the operating position the first pump ( 208 ) or the second pump ( 210 ) are arranged at a lower end of the heat pump system, and wherein in the operating position of the first heat exchanger ( 212 ) and the second heat exchanger ( 214 ) also below the heat pump unit at the lower end adjacent to the first pump ( 208 ) or the second pump ( 210 ) are arranged. Heat pump system according to claim 1, wherein the first pump ( 208 ) and the second pump ( 210 ) are arranged so that a pumping direction of the pump in the operating position is horizontal or deviates by at most ± 45 ° from the horizontal. Heat pump installation according to one of the preceding claims, in which the first heat exchanger ( 212 ) or the second heat exchanger ( 214 ) are arranged standing, wherein a first connection ( 240 . 242 ) of the first heat exchanger ( 212 ) or the second heat exchanger ( 214 ) with a pump side of the first pump ( 208 ) or the second pump ( 210 ), and a second port ( 241 ) of the first heat exchanger ( 212 ) or a second connection ( 243 ) of the second heat exchanger ( 214 ) above the first port ( 240 ) or (242) is arranged. Heat pump installation according to one of the preceding claims, in which an inlet ( 240 ) in the first heat exchanger ( 212 ) with an evaporator outlet ( 220 ) the at least one heat pump stage via a first tube ( 228 ), wherein the first tube ( 228 ) has a curvature closer to a suction side of the first pump ( 208 ) than at the evaporator outlet ( 220 ), wherein an inlet ( 242 ) in the second heat exchanger ( 214 ) with a condenser outlet ( 224 ) a heat pump stage or another heat pump stage via a second tube ( 234 ), wherein the second tube ( 234 ) has a curvature closer to a suction side of the second pump ( 210 ) than at the condenser outlet ( 224 ) is arranged. Heat pump system according to one of the preceding claims, in which the first pump ( 208 ) or the second pump ( 210 ) closer to the first heat exchanger ( 212 ) or at the second heat exchanger ( 214 ) are arranged as a connection point on the heat pump unit. Heat pump system according to one of the preceding claims, wherein the heat pump unit is formed so that at least one outlet of an evaporator or condenser of a heat pump stage, which is connected to the first heat exchanger or the second heat exchanger is arranged so that it from the heat pump stage in the operating position perpendicular down or at an angle less than 45 ° from a vertical exit from the heat pump stage. Heat pump system according to one of the preceding claims, wherein the heat pump unit is formed so that at least one inlet ( 222 . 226 ) of an evaporator or condenser of a heat pump stage, which is connected to the first heat exchanger or the second heat exchanger, is designed so that it emerges from the heat pump stage in the operating position vertically downwards or at an angle less than 45 ° from a vertical from the heat pump stage. Heat pump system according to one of the preceding claims, wherein the heat pump stage is formed so that a Dampfansaugkanal ( 250 ) extends through the condenser. Heat pump system according to one of the preceding claims, wherein the heat pump stage is designed so that the compressor ( 204 ) above the liquefier ( 206 ) so that in an off state of the compressor ( 204 ) Fluid is moving away from the compressor due to gravity. Heat pump system according to one of the preceding claims, which is designed to use water as a working medium, wherein the at least one heat pump stage is designed to hold a pressure at which the water can evaporate at temperatures below 60 ° C. Heat pump system according to one of the preceding claims, further comprising the following features: a support frame, wherein the first heat exchanger ( 212 ) and the second heat exchanger ( 214 ) are secured to the bottom of the support frame, wherein the first pump ( 208 ) and the second pump ( 210 ) are fastened together by a pump holder, and wherein the pump holder is attached to the support frame next to the first heat exchanger ( 212 ) or the second heat exchanger ( 214 ), and wherein the at least one heat pump stage is arranged above the pump holder. Heat pump system according to one of the preceding claims, wherein the heat pump unit, the heat pump stage ( 200 ) and another heat pump stage ( 300 ) having. Heat pump installation according to one of the preceding claims, in which an evaporator outlet ( 220 ) of the heat pump stage via a first downpipe ( 228 ) with a suction side of the first pump ( 208 ), wherein the drop tube is in the operating position perpendicular or at an angle of at most 45 ° to a vertical. Heat pump system according to claim 12 or 13, wherein a condenser exit ( 224 ) of the further heat pump stage ( 300 ) via a second downpipe ( 338 ) with a suction side of the second pump ( 210 ), wherein the downpipe ( 338 ) is vertical in operating position or has an angle of at most 45 ° to a vertical. Heat pump installation according to one of the preceding claims, in which a condenser outlet ( 224 ) of the heat pump stage ( 200 ) with an evaporator inlet ( 322 ) of the further heat pump stage ( 300 ) by an intermediate circuit tube ( 332 ), wherein in the intermediate circuit tube ( 332 ) no pump is arranged, and wherein the heat pump stage ( 200 ) and the further heat pump stage ( 300 ) are configured and arranged so that in operation a condenser working fluid level of the heat pump stage is higher than an evaporator working fluid level in the further heat pump stage ( 300 ). Heat pump system according to one of claims 12 to 15, further comprising a DC link pump ( 330 ) located below the heat pump stage ( 200 ) and the further heat pump stage ( 300 ) and with an evaporator outlet ( 320 ) of the further heat pump stage ( 300 ) via a downpipe ( 334 ) connected to a suction side of the intermediate circuit pump ( 330 ) connected is. Heat pump system according to one of claims 12 to 16, wherein the heat pump stage ( 200 ) and the further heat pump stage ( 300 ) each have a compressor ( 204 . 304 ) above a respective condenser ( 206 . 306. ), and wherein the heat pump stage ( 200 ) and the further heat pump stage ( 300 ) are arranged relative to each other such that a radial wheel of the second compressor is at least 5 cm deeper than a radial wheel of the first compressor ( 204 ) is arranged. Heat pump system according to one of claims 12 to 17, wherein the heat pump stage ( 200 ) and the further heat pump stage ( 300 ) have an outer casing dimension that is equal to within a tolerance of 5 cm, the casing of the heat pump stage ( 200 ) higher than the housing of the further heat pump stage ( 300 ) is arranged so that a bottom of the housing of the heat pump stage ( 200 ) higher than a bottom of the housing of the further heat pump stage ( 300 ). Heat pump system according to claim 18, wherein below the heat pump stage ( 200 ) and above the first pump ( 208 ), the second pump ( 210 ) or the DC link pump ( 330 ) a controllable path module ( 420 ) to connect at least two inputs to the path module with at least two outputs from the path module. Heat pump system according to claim 19, wherein the controllable path module ( 420 ) has the following connections: a return from the first heat exchanger ( 212 ) as the first input ( 404 ); a return from the second heat exchanger ( 214 ) as a second input ( 402 ); a pump side of a DC link pump ( 330 ) as a third input ( 403 ); an inlet into the evaporator ( 204 ) of the heat pump stage ( 200 ) as the first output ( 411 ); an inlet into the condenser ( 206 ) of the heat pump stage ( 200 ) as a second output ( 412 ); and an inlet into the condenser ( 306. ) of the further heat pump stage ( 300 ) as the third output ( 413 ), and wherein the controllable path module ( 420 ) is designed to be dependent on a control signal ( 431 ) to connect one or more inputs to one or more outputs. Heat pump system according to claim 19 or 20, further comprising a controller ( 430 ) to the heat pump unit and the controllable path module ( 420 ) to operate the heat pump system in one of at least two different modes, the heat pump system being configured to perform at least two modes selected from a group of modes having the following modes: a high performance mode in which the heat pump stage ( 100 ) and the further heat pump stage ( 200 ) are active; a mid-power mode in which the heat pump stage ( 200 ) is active and the further heat pump stage ( 300 ) is inactive; a free cooling mode in which the heat pump stage ( 200 ) is active and the further heat pump stage ( 300 ) is inactive and the second heat exchanger ( 214 ) with an evaporator inlet ( 222 ) of the heat pump stage ( 200 ) is coupled; and a low power mode in which the heat pump stage ( 200 ) and the further heat pump stage ( 300 ) are inactive. Heat pump system according to claim 21, wherein the heat pump stage ( 200 ) or the further heat pump stage ( 300 ) is inactive when a compressor motor ( 204 . 304 ) of the corresponding heat pump stage is switched off. Heat pump system according to claim 21 or 22, wherein in the high-performance mode and in the medium-power mode and in the free-cooling mode, the first pump ( 208 ), the second pump ( 210 ) and the intermediate circuit pump ( 330 ) are active, and in low-power mode, the first pump and the second pump are active, and the intermediate circuit pump ( 330 ) is inactive. Heat pump installation according to one of Claims 19 to 23, in which the controllable path module ( 420 ) is designed to be in a high performance mode the first input ( 401 ) with the first output ( 411 ) to connect the second input ( 402 ) with a third output ( 413 ), and around the third entrance ( 403 ) to connect to the third output in order to provide the first input in a mid-power mode ( 401 ) with the first output ( 411 ), the second input ( 402 ) with the second output ( 412 ), and the third input ( 403 ) with the third output ( 413 ) in a free-cooling mode the first input ( 401 ) to connect to the second output, the second input ( 402 ) to connect to the first output, and the third input ( 403 ) to connect to the third output and, in a low power mode, to connect the first input ( 401 ) to connect to the third output, the second input ( 402 ) to connect to the first output, and the third input ( 403 ) with the second output ( 412 ) connect to. Heat pump installation according to one of Claims 19 to 24, in which the controllable path module ( 420 ) a first switch ( 421 ) with two switch positions and a second switch ( 422 ) having two switch positions, one output ( 14 ) of the first switch with an input ( 404 ) of the second switch is connected ( 406 ). Heat pump system according to claim 25, wherein the respective two switch positions define four operating modes with different power levels, wherein when switching from one power level to a next higher or next lower power level always only one switch is switched and the other switch remains in position. Heat pump system according to one of claims 19 to 26, wherein the controllable path switch ( 420 ) a first switch ( 421 ) and a second switch ( 422 ), each having two switch positions, the first switch having the following features: a first switch input connected to the first input ( 401 ), a second switch input connected to the second input ( 402 ), a first switch output connected to the first output ( 411 ) and a second switch output, wherein the second switch ( 422 ) has the following features: a first switch input coupled to the second switch output of the first switch, a second switch input connected to the third input ( 413 ), a first switch output connected to the second output ( 412 ) and a second switch output connected to the third output ( 413 ) is coupled. The heat pump system of claim 27, wherein the first switch is configured to connect the first switch input to the first switch output in a first switch position and connect the second switch input to the second switch output, and to connect the first switch input to the second switch input in a second switch position To connect the switch output, and to connect the second switch input to the first switch output, or wherein the second switch ( 422 ) is configured to connect the first switch input to the first switch output in a first switch position, and to connect the second switch input to the second switch output, and to connect the first switch input to the second switch output in a second switch position, and to second switch input to connect to the first switch output. Heat pump system according to claim 28, wherein the controllable path module ( 420 ) is adapted to operate in a high performance mode, the first switch in the first switch position, and the second switch ( 422 ) in the first switch position, or in a mid-power mode, the first switch ( 421 ) in the first switch position and the second switch ( 422 ) in the second switch position, or in a free cooling mode the first switch ( 421 ) in the second switch position and the second switch ( 422 ) in the first switch position, or in a low power mode, the first switch ( 421 ) in the second switch position, and the second switch ( 422 ) in the second switch position. Heat pump system according to one of the preceding claims, wherein a height of the heat pump system is smaller than 2.50 m, in which a width of the heat pump system is less than 2 m, and in which a depth of the heat pump system is less than 1 m. Method for producing a heat pump system with a heat pump unit with at least one heat pump stage ( 200 ), wherein the at least one heat pump stage ( 200 ) an evaporator ( 202 ), a compressor ( 204 ) and a liquefier ( 206 ) having; a first heat exchanger ( 212 ) on a side to be cooled; a second heat exchanger ( 214 ) on a side to be heated; a first pump ( 208 ) connected to the first heat exchanger ( 212 ) is coupled; and a second pump ( 210 ) connected to the second heat exchanger ( 214 ), comprising the following steps: arranging the first pump ( 208 ) or the second pump ( 210 ) below the heat pump unit at a lower end of the heat pump system; and arranging the first heat exchanger ( 212 ) and the second heat exchanger ( 214 ) also below the heat pump unit at the lower end adjacent to the first pump ( 208 ) or the second pump ( 210 ). Method for operating a heat pump system with a heat pump unit having at least one heat pump stage ( 200 ), wherein the at least one heat pump stage ( 200 ) an evaporator ( 202 ), a compressor ( 204 ) and a liquefier ( 206 ) having; a first heat exchanger ( 212 ) on a side to be cooled; a second heat exchanger ( 214 ) on a side to be heated; a first pump ( 208 ) connected to the first heat exchanger ( 212 ) is coupled; and a second pump ( 210 ) connected to the second heat exchanger ( 214 ), comprising the following steps: bringing the heat pump system into an operating position, wherein in the operating position the first pump ( 208 ) or the second pump ( 210 ) are arranged below the heat pump unit at a lower end of the heat pump system, and wherein in the operating position of the first heat exchanger ( 212 ) and the second heat exchanger ( 214 ) also below the heat pump unit at the lower end adjacent to the first pump ( 208 ) or the second pump ( 210 ) are arranged; and activating the heat pump stage in the operating position.

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