EP4591011A2 - Ensemble pompe à chaleur, procédé pour le faire fonctionner et bâtiment en étant équipé - Google Patents

Ensemble pompe à chaleur, procédé pour le faire fonctionner et bâtiment en étant équipé

Info

Publication number
EP4591011A2
EP4591011A2 EP23773223.5A EP23773223A EP4591011A2 EP 4591011 A2 EP4591011 A2 EP 4591011A2 EP 23773223 A EP23773223 A EP 23773223A EP 4591011 A2 EP4591011 A2 EP 4591011A2
Authority
EP
European Patent Office
Prior art keywords
heat
heat pump
pump
flow
return
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP23773223.5A
Other languages
German (de)
English (en)
Inventor
Jakob Metz
Tim Haselwander
Danny Günther
Dirk Ludwig
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Viessmann Climate Solutions SE
Fraunhofer Gesellschaft zur Foerderung der Angewandten Forschung eV
Original Assignee
Viessmann Climate Solutions SE
Fraunhofer Gesellschaft zur Foerderung der Angewandten Forschung eV
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Viessmann Climate Solutions SE, Fraunhofer Gesellschaft zur Foerderung der Angewandten Forschung eV filed Critical Viessmann Climate Solutions SE
Publication of EP4591011A2 publication Critical patent/EP4591011A2/fr
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F25B27/002—Machines, plants or systems, using particular sources of energy using solar energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/06—Heat pumps characterised by the source of low potential heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/06—Several compression cycles arranged in parallel

Definitions

  • the invention relates to a heat pump arrangement with at least a first heat pump, with a flow and a return, at least a second heat pump, with a flow and a return, at least a first heat source with a flow and a return and at least a second heat source with a flow and a return. Furthermore, the invention relates to a method for operating such a heat pump arrangement and a building equipped with it.
  • the invention may relate to a heat pump arrangement.
  • This can contain at least a first heat pump with a flow and a return and/or at least a second heat pump with a flow and a return.
  • each heat pump can have a condenser and an evaporator and a compressor in a manner known per se, whereby a working medium can be evaporated while absorbing heat in the evaporator and can be condensed while releasing heat in the condenser.
  • the gaseous working fluid can be compressed using an optional compressor and the liquefied working fluid can be returned via an optional throttle valve.
  • the heat pumps that can be used can be of standard design. The invention does not teach the use of special heat pumps as a solution principle.
  • the heat pump arrangement can have at least a first heat source and/or at least a second heat source.
  • the two heat sources can be of the same or of different types.
  • at least one heat source can be or contain a geothermal collector installed horizontally beneath the earth's surface and/or a geothermal probe installed in a deep borehole, each of which draws heat from the ground.
  • At least one heat source may be or contain an air heat exchanger in order to utilize heat from the outside air.
  • at least one heat source may be selected from a solar thermal collector and/or a photovoltaic Thermal collector and/or a solar absorber to make solar heat radiation usable as domestic heat.
  • at least one heat source can be or contain a groundwater well in order to make heat stored in the groundwater usable as industrial heat.
  • at least one heat source can contain or consist of a heat exchanger, which makes waste heat usable as industrial heat. The waste heat can come from a combustion process and/or an industrial manufacturing process and/or a wastewater stream and/or a cooling water stream.
  • the heat can be transported between the evaporators of the heat pump arrangement and the heat sources by a heat transfer fluid circulating in pipes.
  • the heat transfer fluid can be liquid.
  • the heat transfer fluid can be gaseous.
  • the heat transfer fluid can undergo a phase transition when heat is supplied or released.
  • the heat transfer fluid can be a frost-proof liquid.
  • the heat transfer fluid can be selected from a salt solution or Brine and/or a water/glycol mixture and/or a thermal oil.
  • the heat pump arrangement further has a collector and a distributor, wherein the flow of the first and second heat pumps and the return of the first and second heat sources are connected to the distributor and the return of the first and second heat pumps and the flow of the first and second heat sources are connected to the collector.
  • the heat transfer fluid flows from the collector through a heat source, absorbs heat there and then flows into the distributor.
  • the heat transfer fluid is fed from the distributor to the evaporator of a heat pump, where it releases heat and cools down.
  • the cooled heat transfer fluid flows back into the collector.
  • a connecting pipe is arranged between the collector and the distributor.
  • the connecting pipe serves as a hydraulic zero point and thus makes it possible to derive a control variable for the heat pump arrangement.
  • the heat pump arrangement according to the invention can have a larger variety of operating states and/or a simplified control system.
  • the heat pump arrangement can further contain a first pump, which is set up to convey the heat transfer fluid from the distributor into the first heat pump.
  • the heat pump arrangement can alternatively or additionally contain a second pump, which is set up to convey a heat transfer fluid from the distributor into the second heat pump.
  • the heat pump arrangement can alternatively or additionally contain a third pump, which is set up to convey a heat transfer fluid from the collector into the first heat source.
  • the heat pump arrangement can alternatively or additionally contain a fourth pump, which is designed to convey a heat transfer fluid from the collector into the second heat source.
  • At least one flow meter can be present in the connecting pipe.
  • at least one temperature sensor can alternatively or additionally be present in the connecting pipe.
  • two or three temperature sensors can be present in the connecting pipe. Since the connecting pipe represents the hydraulic zero point of the pipe network used for the heat transfer fluid, the flow of the heat transfer fluid is controlled or regulated in such a way that the flow within the connecting pipe is below a predeterminable limit value. In some embodiments of the invention, the flow in the connecting pipe comes to a complete standstill. reaches a value that can no longer be measured by the sensor technology used.
  • a flow meter can be used in the connecting pipe to measure the flow within the connecting pipe.
  • the temperature or a temperature gradient in the connecting pipe can be determined.
  • the temperature in the middle of the connecting pipe will be approximately the average of the temperature of the collector and the distributor. If more than one temperature sensor is used, these can be placed in the middle of the connecting pipe and at both ends of the connecting pipe.
  • the heat pump assembly may further comprise a first three-way valve having a first connection and a second connection and a third connection, wherein the first and second connections are connected to the collector and the flow of the second heat source and the third connection is connected to the distributor.
  • the heat pump arrangement can further comprise a second three-way valve with a first connection and a second connection and a third connection, wherein the first and second connections are connected to the distributor and the return of the second heat source and the third connection is connected to the collector.
  • the first heat source can also be equipped with two three-way valves, as described above.
  • the three-way valves have the effect that the flow of the heat transfer fluid flowing from the supply to the return during normal operation can be reversed, so that heat can be supplied to the heat source via the return, for example to regenerate a geothermal probe or to defrost an air heat exchanger.
  • the distributor can be formed by a pipe, with the flow of the first heat pump and the return of the first heat source being arranged at a first end of the pipe and the flow of the second heat pump and the return of the second heat source being arranged at a second End of the tube are arranged.
  • the collector can also be formed by a pipe, with the return of the first heat pump being arranged at a first end of the pipe and the return of the second heat pump being arranged at a second end of the pipe.
  • this relates to a method for operating a heat pump arrangement with at least a first heat pump, at least a second heat pump, at least a first heat source and at least a second heat source.
  • the method according to this aspect of the invention is characterized in that the heat pump arrangement has at least three operating states.
  • heat can be taken from a heat source and supplied to the other heat source.
  • Regenerating a heat source can include de-icing an air heat exchanger or introducing heat into a geothermal probe.
  • heat can be taken from a single heat source, which is provided as industrial heat via a single heat pump, for example for heating domestic water, for heating buildings or for industrial purposes or for operating a district heating network.
  • the heat pump arrangement allows each heat source to be individually connected to each heat pump, so that there is the greatest possible flexibility in selecting the heat pump and the heat source.
  • heat can be taken from the first heat source, which is provided as useful heat via the first heat pump, and heat can be taken from the second heat source, which is provided as useful heat via the second heat pump.
  • This parallel operation is particularly suitable for high load requirements, for example for simultaneous building heating and domestic water heating in winter. If both heat sources are of different types, for example an air heat exchanger and a geothermal probe, the limited Annual work of a geothermal probe can be saved for times when the air heat exchanger only offers inadequate performance due to low outside temperatures. If outside temperatures are very high, heat from the air heat exchanger can be fed into the geothermal probe in order to regenerate it.
  • the air heat exchanger tends to ice up, it can be de-iced with heat from the geothermal probe.
  • a high heat output can be provided by the heat pump arrangement with at the same time a low risk of overloading a possibly partial load-sized, limited, higher-quality heat source.
  • the heat can be transported between the heat source and the heat pump with a liquid heat transfer fluid, which is conveyed between the heat sources and the heat pumps using an assigned pump.
  • the pumps can be easily influenced via a control or regulating device, so that the flow of the heat transfer fluid can be adapted to the different operating states.
  • the first and second pumps assigned to the heat pumps can be operated with a constant delivery rate and the third and fourth pumps assigned to the heat sources can be controlled or regulated. This allows the control strategy to be simplified without losing flexibility.
  • the supply and return lines of the heat sources and the heat pumps can be connected to a collector and a distributor, with a connecting pipe being arranged between the distributor and the collector and the pumps being controlled or regulated so that the flow flow through the connecting pipe is below a predetermined limit value. In In some embodiments of the invention the flow is zero or below the measurement limit.
  • control may be accomplished through a translation table.
  • the temperatures of the heat sources and/or the heat requirement of the building equipped with the heat pump arrangement and/or the temperatures of the heat sinks can be used as input variables and the respective pump speed or Delivery quantity can be read out and set as an initial variable from the conversion table.
  • control takes place in such a way that the connecting pipe has the average temperature between the collector and distributor. This can be seen as an indication that there is no significant flow of heat transfer fluid through the connecting pipe.
  • control can be carried out in such a way that a flow meter in the connecting pipe detects a flow below a predeterminable limit value.
  • this limit value can be a minimum value or be null.
  • the method according to the invention can have a fourth operating state in which heat is taken from both heat sources and is provided as useful heat via a single heat pump.
  • Figure 1 shows a heat pump arrangement according to a first embodiment of the invention.
  • Figure 2 shows a heat pump arrangement according to a second embodiment of the invention.
  • Figure 3 shows a heat pump arrangement according to a third embodiment of the invention.
  • the heat pump arrangement 9 has a first heat pump 1.
  • the first heat pump 1 contains an evaporator 101 and a condenser 102.
  • the evaporator 101 is provided with a flow 11 and a return 12, via which a heat transfer fluid can be supplied to the evaporator 101.
  • the heat from the heat transfer fluid causes the evaporation of a working fluid in the evaporator 101, with heat being removed from the heat transfer fluid so that it cools down.
  • the working fluid is compressed with a compressor 104 and fed to the condenser 102.
  • the working fluid is condensed in the condenser 102 with the release of heat.
  • the heat released in this way can be used as domestic heat for heating buildings, for industrial processes or for heating domestic water.
  • the liquefied working medium is fed back to the evaporator 101 via a throttle valve 103, so that the process described above runs cyclically.
  • the heat pump arrangement contains a second heat pump 2 with an evaporator 201, a condenser 202, a compressor 204 and a throttle valve 203.
  • the functionality of the second heat pump 2 essentially corresponds to the functionality of the first heat pump 1.
  • the second heat pump 2 also has a flow 21 and a return 22, via which a heat transfer fluid and thus heat can be supplied.
  • the heat pump arrangement according to the invention has a first heat source 3.
  • the heat source 3 also has a flow 31 and a return 32.
  • the Heat source 3 can be, for example, a geothermal probe, a geothermal collector or even a groundwater well.
  • a cooled heat transfer fluid is supplied to the first heat source 3 via the flow 31, which absorbs heat in the heat source 3 and leaves the first heat source 3 again as heated heat transfer fluid via the return line 32.
  • the heat pump arrangement has a second heat source 4.
  • the second heat source 4 also has a flow 41 and a return 42.
  • a cooled heat transfer fluid can be supplied via the flow 41, which absorbs heat and is removed from the heat source 4 at a higher temperature level via the return 42.
  • the second heat source 4 may contain an air heat exchanger or a solar collector.
  • more than two heat sources can also be present.
  • the first heat source 3 and the second heat source 4 shown represent only the minimum number. Due to their different types, the first and second heat sources 3 and 4 can operate at different temperature levels. about their return 32 or 42 deliver a heat transfer fluid with different temperatures.
  • the heat transfer fluid circulating in the heat pump arrangement can be liquid or gaseous.
  • a liquid heat transfer fluid can be, for example, a water/glycol mixture or a brine in order to enable working temperatures below the freezing point of water.
  • the heat transfer fluid can be a thermal oil.
  • water can be used as a heat transfer fluid when temperatures below freezing are not expected.
  • the heat pump arrangement according to the invention also contains a distributor 6 and a collector 5.
  • the heat pump arrangement further contains an optional first pump 15, which is set up to convey a heat transfer fluid from the distributor 6 into the first heat pump 1.
  • an optional second pump 25 may be present, which is set up to convey a heat transfer fluid from the distributor 6 into the second heat pump 2.
  • an optional third pump 35 may be present, which is set up to convey a heat transfer fluid from the collector 5 into the first heat source 3.
  • an optional fourth pump 45 may be present, which is set up to provide a heat to promote carrier fluid from the collector 5 into the second heat source 4.
  • the flow in the connecting pipe 7 can also be determined by one or more temperature sensors.
  • three temperature sensors 71, 72 and 73 are shown along the longitudinal extent of the connecting pipe 7.
  • the heat pump arrangement may further include an optional first three-way valve 47 with a first port and a second port and a third port.
  • the first and second connections are connected to the collector 5 and the flow 41 of the second heat source 4.
  • the third connection can be connected to the flow 42, so that it is indirectly connected to the distributor 6.
  • the third connection is connected to the distributor 6.
  • the heat pump arrangement may further include an optional second three-way valve 48 with a first port and a second port and a third port.
  • the first and second connections are connected to the distributor 6 and the return 42 of the second heat source 4.
  • the third connection is connected to the collector 5.
  • the third connection may be connected to the return 41 so that it is indirectly connected to the collector 5.
  • the three-way valves have the effect that the flow of the heat transfer fluid that flows from the flow to the return during normal operation can be reversed, so that heat can be supplied to the heat source via the return, for example to regenerate a geothermal probe or to de-ice an air heat exchanger .
  • the first operating state can be selected when regeneration of a heat source with the heat of the other heat source is effective and none of the first and second heat pumps are active.
  • heat from a geothermal probe 3 can be used to defrost or defrost an air heat exchanger used as a second heat source 4. to de-ice.
  • heat from an air heat exchanger which can arise, for example, on hot summer days, can be used to regenerate the geothermal probe.
  • the control of the first operating state can, for example, be carried out predictively based on a weather forecast.
  • the first heat source 3 can supply either the first heat pump 1 or the second heat pump 2. If, for example, the second heat pump 2 is to be operated, the cooled heat transfer fluid can be conveyed from the collector 5 via the third pump 35 into the flow 31 of the first heat source 3. There, the heat transfer fluid absorbs heat and leaves the first heat source 3 via the return 32 into the distributor 6. From there, the heat transfer fluid is conveyed via the second pump 25 into the flow 21 of the second heat pump. In the second heat pump 2, heat is extracted from the heat transfer fluid. The heat transfer fluid cooled in this way flows via the return 22 into the collector 5. In the same way as As described above, the first heat pump 1 can also be operated with the first heat source 3. Alternatively, the first heat source 3 can also be replaced by the second heat source 4.
  • the second operating mode described above is selected when only one heat pump is active.
  • the source can be selected which is advantageous at the respective operating time. For example, efficiency can be optimized by maximizing the source temperature. Further selection criteria include, for example, a sustainable load on a geothermal probe while avoiding overload. Which heat source is advantageous with regard to these goals can be determined, for example, by an outside temperature-related bivalent temperature. Alternatively or additionally, the comparison of the measured or predicted source temperatures can be used to make the decision. In some embodiments of the invention, a predictive selection can also be made taking into account the expected future outside temperatures.
  • a third operating state of the heat pump arrangement heat is taken from the first heat source, which is provided as useful heat via the first heat pump. Furthermore, heat is taken from the second heat source, which is provided as domestic heat via the second heat pump.
  • the third operating state therefore involves parallel operation of both heat sources and both heat pumps.
  • cooled heat transfer fluid is removed from the collector 5 by means of the third pump 35 and fed to the first heat source 3 via its flow 31.
  • the heated heat transfer fluid leaves the first heat source 3 via its return line 32 and is fed to the distributor 6 , as described above.
  • the first pump 15 takes the heat from the distributor carrier fluid and supplies this to the first heat pump 1 via the flow 11.
  • the heat transfer fluid cooled in the heat pump 1 leaves the first heat pump 1 via the return line 12 into the collector 5.
  • the fourth pump 45 removes heat transfer fluid from the collector 5 and supplies it to the second heat source 4 via the flow 41.
  • the heat transfer fluid heated in this way leaves the second heat source 4 via its return line 42 into the distributor 6.
  • the second pump 25 removes the heat transfer fluid from the distributor 6 and supplies it to the second heat pump 2 via its flow 21.
  • the heat transfer fluid cooled in this way leaves the second heat pump 2 via its return line 22 and is passed into the collector 5.
  • the first and second pumps 15 and 25 can have a constant delivery rate or Speed are operated and the third and fourth pumps 35 and 45 assigned to the heat sources 3 and 4 are controlled or. can be regulated so that the flow in the connecting pipe 7 comes to a standstill. This reliably prevents mixing of the heat transfer fluid that is at different temperature levels.
  • the pumps can be controlled using an implementation table depending on the source temperatures or the manipulated variable of the pump of the assigned heat pump. Alternatively, the pumps can be controlled using a known electronic controller.
  • a heat pump can be used with both heat sources.
  • the third and fourth pumps 35 and 45 remove the heat transfer fluid from the collector 5 and supply it to the first and second heat sources 3 and 4, as described above.
  • the heat transfer fluid heated in the respective heat source flows into the distributor 6 via the respective return lines 32 and 42. There the heat transfer fluid is mixed and the temperature is adjusted at the same time.
  • the first pump 15 or the second pump 25 removes the heat transfer fluid and supplies it to a heat pump, for example the second heat pump 2.
  • the cooled heat transfer fluid flows back into the collector 5 via the return line of the heat pump.
  • the fourth operating state can be used advantageously, for example, when a heat source, for example an air heat exchanger or a solar collector, provides an outlet temperature at its return that exceeds the permissible inlet temperature of a heat pump.
  • a heat source for example an air heat exchanger or a solar collector
  • the inlet temperature can be reduced.
  • a geothermal probe can be passively regenerated at the same time due to the still elevated temperature in the collector 5.
  • the admixture can be limited to the necessary level by appropriately controlling the third pump 35 and the fourth pump 45 in order to maximize the efficiency of the heat pumps.
  • an air heat exchanger can be de-iced using an electrical heating register 405.
  • the first and second valves 47 and 48 are switched so that the fourth pump 45 can circulate the heat transfer fluid between the heating register 405 and the second heat source 4 without the heat transfer fluid being exchanged between the collector 5 and the distributor 6.
  • the fifth operating state can be used in particular if de-icing is not possible due to the first operating state described above.
  • a combination of operating states 1 and 5 can be made possible, i.e. H . the defrosting of an air heat exchanger using heat from the ground and the heating register 405.
  • the second heat source 4 can be supplied with heat from the electrical heating register 405, while at the same time one or both heat sources pumps are in operation, as described above with reference to the second, third or fourth operating state.
  • FIG. 2 A second embodiment of the invention is described with reference to FIG. 2.
  • the same components of the invention are provided with the same reference numbers, so that the following description is limited to the essential differences.
  • the collector 5 and the distributor 6 are replaced by three connecting lines 701, 702 and 703 and six shut-off valves 81, 82, 83, 84, 85 and 86.
  • shut-off valves 81, 82, 83, 84, 85 and 86 By controlling the shut-off valves, all of the operating states described above can be realized.
  • the flow 31 of the first heat source 3 is connected to the return 12 of the first heat pump 1 by means of a line 51.
  • the flow 11 of the first heat pump 1 is connected to the return 32 of the first heat source 3 by means of a line 61.
  • the third pump 35 is located in line 61.
  • a third shut-off valve 83 is arranged in line 51.
  • the flow 21 of the second heat pump 2 is connected to the return 42 of the second heat source 4 via a line 62.
  • the return line 22 of the second heat pump is connected via a line 52 to the flow line 41 of the second heat source.
  • the fourth pump 45 is located in line 52 and can be bridged with a parallel bypass line.
  • the fifth shut-off valve 85 is located in the bypass line.
  • the fourth shut-off valve 84 and the optional heating register 405 are located in line 62.
  • the bypass line can also be arranged above the pump 35. Such a bypass line can preferably be present above the smaller pump, which is assigned to the heat source with the lower pressure loss.
  • the pumps 35 and 45 can also be assigned to the first and second heat pumps, as described above in connection with the first embodiment. It is only essential that a flow of a heat transfer medium can be generated between at least one source 3, 4 and at least one heat pump 1, 2.
  • the lines 51 and 62 are connected by a first connecting line 701, in which a sixth shut-off valve 86 is arranged.
  • the lines 61 and 52 are connected to a second connecting line 702, which is connected to two shut-off valves 81 and 82.
  • the second connecting line 702 also has a fluid connection to the line 62 at a point between the two shut-off valves 81 and 82.
  • lines 51 and 52 are connected by a third connecting line 703.
  • the first shut-off valve 81 and the fifth shut-off valve 85 are open and the third pump 35 is operated.
  • the heat transfer fluid thus flows from the return 32 of the first heat source 3 via the connecting line
  • the heat transfer fluid flows from the flow 41 of the second heat source through the bypass of the fourth pump 45 and the connecting line
  • either heat from the first heat source 3 can be supplied to the first heat pump 1 via the lines 61 and 51.
  • heat from the second heat source 4 can be supplied to the second heat pump 2 via the lines 62 and 52.
  • heat from the first heat source 3 can be supplied to the second heat pump 2. This is what happens Fluid path from the return 32 of the first heat source via the first connecting line 702 into the line 62, the second shut-off valve 82 is closed. The return 22 leads via the third connecting line 703 to the flow 31 of the first heat source 3.
  • the second heat source 4 can also be connected to the first heat pump 1.
  • shut-off valves 85, 81, 82 and 86 are closed and the third and fourth shut-off valves 83 and 84 are opened. This enables parallel operation, in which the first heat pump is connected to the first heat source and the second heat pump is connected to the second heat source.
  • the first heat source is connected to the second heat pump, as described above.
  • the shut-off valve 84 is opened so that the second heat source 4 is also connected to the second heat pump 2 and the mixed operation described above is made possible.
  • an air heat exchanger which can be used, for example, as a second heat source 4
  • an air heat exchanger can be de-iced using an optional electrical heating register 405.
  • the shut-off valves 81 and 84 can be closed and the shut-off valve 82 can be opened so that the fourth pump 45 can circulate the heat transfer fluid between the heating register 405 and the heat source 4.
  • a third embodiment of the invention is described with reference to FIG. 3.
  • the same components are given the same reference numbers, so that the following description is limited to the essential differences.
  • the third embodiment of the heat pump arrangement can, in some embodiments, be operated with the method according to the invention.
  • FIG. 3 shows, there are three shut-off valves 81 in the collector 5,
  • the second shut-off valve 82 according to the second embodiment described above is realized by a three-way valve 82 with a first port and a second port and a third port.
  • the first and second connections are connected to the distributor 6 and the return 42 of the second heat source 4.
  • the third connection is connected to the collector 5.
  • the third connection may be connected to the return 41 so that it is indirectly connected to the collector 5.
  • the first and fifth shut-off valves 81 and 85 are open and the three-way valve 82 is switched so that the first and second connections are connected to each other.
  • the third and fourth shut-off valves 83 and 84 are closed and the third pump 35 is operated.
  • the heat transfer fluid thus flows from the return 32 of the first heat source 3 via the connecting line 61, the collector 5 and the connecting line 62 to the return 42 of the second heat source 4. From the flow 41 of the second heat source, the heat transfer fluid flows through the fifth valve 85 via the bypass line of the fourth pump 45 and the connecting line 52, the collector 5 and the connecting line 51 to the flow 31 of the first heat source 3.
  • a heat source can be connected to a heat pump, i.e. H .
  • Either heat is supplied from the first heat source 3 via the lines 61 and 51 to the first heat pump 1 or alternatively heat can be supplied from the second heat source 4 via the lines 62 and 52 of the second heat pump 2 are supplied.
  • the fluid path runs from the return line 32 of the first heat source via the connecting line 61 into the collector 5 and from there to the flow line 11 of the first heat pump 1.
  • the return 12 leads through the open third shut-off valve 83 through the collector 5 and via the connecting line 51 to the flow 31 of the first heat source 3.
  • the first shut-off valve 81 is closed.
  • the second heat source 4 can also be connected to the second heat pump 2 by opening the fourth shut-off valve 84.
  • the optional three-way valve 82 is connected so that the first and second ports are connected to each other.
  • heat from the first heat source 3 can be supplied to the second heat pump 2.
  • the fluid path runs from the return line 32 of the first heat source via the connecting line 61 into the collector 5 and from there to the flow line 21 of the second heat pump 2.
  • the return 22 leads through the open fourth and first shut-off valves 84 and 81 through the collector 5 and via the connecting line 51 to the flow 31 of the first heat source 3.
  • the third shut-off valve 83 is closed.
  • the second heat source 4 can also be connected to the first heat pump 1 by opening the first and third shut-off valves 81 and 83 and closing the fourth shut-off valve 84.
  • the first shut-off valve 81 is closed and the third and fourth shut-off valves 83 and 84 are opened. This enables parallel operation, in which the first heat pump is connected to the first heat source and the second heat pump is connected to the second heat source.
  • the first heat source 3 is connected to the second heat pump 2 by opening the first and fourth shut-off valves 81 and 84.
  • Closing the third shut-off valve 83 prevents flow through the first heat pump 1.
  • the optional three-way valve 82 is connected so that the first and second ports are connected to each other. Both pumps 35 and 45 are then operated, so that the second heat pump 2 is supplied with heat from both heat sources 3 and 4 on the one hand and, on the other hand, heat is exchanged between the two heat sources 3 and 4, as described above in connection with the first embodiment.
  • This mixed operation can also be implemented with the first heat pump 1 by switching the third and fourth shut-off valves 83 and 84, whereby flow through the second heat pump is avoided.
  • an air heat exchanger which can be used, for example, as a second heat source 4
  • the three-way valve 82 can be switched so that the first and third connections are connected to each other, i.e. H .
  • the heat transfer fluid flows from the return 42 directly to the flow 41 of the second heat source 4.
  • the shut-off valve 85 is closed and the fourth pump 45 delivers the heat transfer fluid between the heating register 405 and the heat source 4.
  • the third embodiment allows a combination of the fifth and second operating states with both heat pumps 1 and 2.
  • defrosting can take place with flow through the evaporator 201 of the second heat pump 2.
  • the second operating state can run simultaneously with the first heat pump 1.
  • the invention is not limited to the embodiments shown. The above description is therefore not to be viewed as limiting, but rather as illustrative.
  • the following claims are to be understood as meaning that a stated feature is present in at least one embodiment of the invention. This does not exclude the presence of other features. If the claims and the above description define “first” and “second” embodiments, this designation serves to distinguish two similar embodiments without establishing a ranking.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Central Heating Systems (AREA)

Abstract

L'invention concerne un ensemble pompe à chaleur (9) comprenant au moins une première pompe à chaleur (1) comportant une conduite d'aller (11) et une conduite de retour (12), au moins une deuxième pompe à chaleur (2) comportant une conduite d'aller (21) et une conduite de retour (22), au moins une première source de chaleur (3) comportant une conduite d'aller (31) et une conduite de retour (32) et au moins une deuxième source de chaleur (4) comportant une conduite d'aller (41) et une conduite de retour (42), l'ensemble pompe à chaleur (9) comprenant en outre un collecteur (5) et un distributeur (6), la conduite d'aller (11, 21) de la première et de la deuxième pompe à chaleur (1, 2) et la conduite de retour (32, 42) de la première et de la deuxième source de chaleur (3, 4) étant reliées au distributeur (6) et la conduite de retour (12, 22) de la première et de la deuxième pompe à chaleur (1, 2) et la conduite d'aller (31, 41) de la première et de la deuxième source de chaleur (3, 4) étant reliées au collecteur (5) et un tuyau de liaison (7) étant disposé entre le distributeur (6) et le collecteur (5). Cette invention concerne en outre un bâtiment équipé de cet ensemble pompe à chaleur ainsi qu'un procédé pour faire fonctionner ce dernier.
EP23773223.5A 2022-09-19 2023-09-18 Ensemble pompe à chaleur, procédé pour le faire fonctionner et bâtiment en étant équipé Pending EP4591011A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022209850.1A DE102022209850A1 (de) 2022-09-19 2022-09-19 Wärmepumpenanordnung, Verfahren zu deren Betrieb und damit ausgestattetes Gebäude
PCT/EP2023/075649 WO2024061828A2 (fr) 2022-09-19 2023-09-18 Ensemble pompe à chaleur, procédé pour le faire fonctionner et bâtiment en étant équipé

Publications (1)

Publication Number Publication Date
EP4591011A2 true EP4591011A2 (fr) 2025-07-30

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EP23773223.5A Pending EP4591011A2 (fr) 2022-09-19 2023-09-18 Ensemble pompe à chaleur, procédé pour le faire fonctionner et bâtiment en étant équipé

Country Status (3)

Country Link
EP (1) EP4591011A2 (fr)
DE (1) DE102022209850A1 (fr)
WO (1) WO2024061828A2 (fr)

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69617966T2 (de) 1995-08-29 2002-08-01 MONARD (RESEARCH & DEVELOPMENT) LTD., CORK Hydraulische weiche für zentralheizungsanlage
AT406081B (de) 1997-03-14 2000-02-25 Zortea Rembert Heizanlage
MX2011013530A (es) * 2009-06-16 2012-05-23 Dec Design Mechanical Consultants Ltd Sistema distrital de compartimiento de energia.
CN101988775B (zh) * 2010-11-16 2012-08-15 山东建筑大学 太阳能-空气-地能多源双机热泵供热空调复合系统
DE202011106855U1 (de) 2011-10-15 2011-11-29 Institut Für Solarenergieforschung Gmbh Wärmeversorgungssystem mit dezentralen Wärmepumpen und gebäudeintegriertem Wärmequellennetz für Umweltwärme, insbesondere Erdwärme, Umgebungsluft, Abwärme oder/und Solarwärme
PL3076111T3 (pl) * 2015-03-30 2021-07-19 Viessmann Refrigeration Solutions Gmbh Układ płynów i sposób sterowania układem płynów
DE202016000563U1 (de) * 2016-01-28 2017-05-02 Erwin Dietz Exergieoptimierungseinheit
EP4148343A4 (fr) * 2018-07-09 2024-03-06 Toshiba Carrier Corporation Système de source de chaleur, machine de source de chaleur et dispositif de commande

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WO2024061828A3 (fr) 2024-05-16
WO2024061828A2 (fr) 2024-03-28
DE102022209850A1 (de) 2024-03-21

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