EP2026019A2 - Installation d'équilibrage de la température à base de pompe thermique - Google Patents

Installation d'équilibrage de la température à base de pompe thermique Download PDF

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Publication number
EP2026019A2
EP2026019A2 EP07023280A EP07023280A EP2026019A2 EP 2026019 A2 EP2026019 A2 EP 2026019A2 EP 07023280 A EP07023280 A EP 07023280A EP 07023280 A EP07023280 A EP 07023280A EP 2026019 A2 EP2026019 A2 EP 2026019A2
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EP
European Patent Office
Prior art keywords
heat
heat exchanger
compressor
circuit
valve
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.)
Withdrawn
Application number
EP07023280A
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German (de)
English (en)
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EP2026019A3 (fr
Inventor
Markus Kroll
Andreas Vetter
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Kroll Markus
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Individual
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Filing date
Publication date
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Publication of EP2026019A2 publication Critical patent/EP2026019A2/fr
Publication of EP2026019A3 publication Critical patent/EP2026019A3/fr
Withdrawn legal-status Critical Current

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    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D11/00—Central heating systems using heat accumulated in storage masses
    • F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps
    • F24D11/0214—Central heating systems using heat accumulated in storage masses using heat pumps water heating system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/08—Hot-water central heating systems in combination with systems for domestic hot-water supply

Definitions

  • the innovation relates to a tempering device based on heat pump, with a cooling medium circuit in which in series a compressor, a heat exchanger for certain condenser in the form of a first heat exchanger, an expansion valve, a certain heat from a fluid stream evaporator and optionally in the Series connected second heat exchanger are arranged, and with a heat transport medium circuit, which is generally a water circulation system and in which the one or more heat exchangers are involved and there is in heat exchange relationship with the refrigerant circuit.
  • a tempering is off DE 202006 010412 U1 known.
  • the innovation should enable an improved utilization of the tangible energies. According to the innovation, several steps serve this purpose, representing different aspects of the innovation.
  • the first heat exchanger for the purpose of dissipating heat in the refrigerant circuit between the output of the compressor and a switched on before the input of the second heat exchanger, this in the cooling or defrosting of Compressor output separating circuit reversing valve is used so that it is included in both directions in the refrigerant circuit, the connecting lines of the refrigerant circuit or the heat transport medium circuit are passed to the second heat exchanger via switching valves, which for a flow direction reversal of the refrigerant or, what is easier to implement, the heat transfer medium in the second heat exchanger can be switched.
  • the first and the second heat exchanger in the heat transport medium circuit are connected in series and are the two connections of the second heat exchanger to this circuit subsequent switching valves between a straight and a cross-switching position switchable switching valves.
  • the renewal concept can be realized with moderate equipment costs.
  • a second aspect relates to a tempering device which is to allow a heating and a cooling operation and in which for this aspect the second heat exchanger is useful, but not urgently necessary, and the - first - heat exchanger for the purpose of dissipating heat into the refrigerant circuit behind the outlet the compressor is inserted so that it is included in both circuit directions in the refrigerant circuit.
  • the heat transport medium circuit consists of at least two parallel pitch circles, one of which is passed through a serving as a heat exchanger against a service water stratified storage, which in turn is connectable via two connection points with switching valves with a buffer heat storage, which in turn with heating or cooling heat exchangers is connected, and the other is feasible via switching valves through the buffer memory.
  • the stratified storage can then be bypassed and the energy extracted by the cooling of the room air utilized, namely used for hot water.
  • a preferred device realization of this concept is such that the switching valves of the connection points of the buffer heat accumulator are synchronously controlled three-way valves, which connect to the buffer heat storage either the stratified storage or the two media circuits coupling heat exchanger.
  • the switching valves in the connection lines of the heat transport medium circuit to the second heat exchanger are two controlled Three-way valves are and another third controlled three-way valve is turned on in one of the connecting lines of the heat transport medium circuit to the first heat exchanger, and the switching valves can take the following switching positions: the first switching valve connects the first port of the second heat exchanger with one of the three-way valves of the buffer heat accumulator or with first The second switching valve connects the second port of the second heat exchanger to the other three-way valve of the buffer heat accumulator or to a first port of the third three-way valve, and the third three-way valve connects one port of the first heat exchanger, the other port to second ports of the first heat exchanger Stratified storage is passed, with the second terminal of the second switching valve or with the first terminals of the stratified storage.
  • the desired method measures can be easily effected by
  • the refrigerant circuit of the temperature control parallel to the first heat exchanger serving as a hot water module third heat storage is connected, and between the compressor on the one hand and the first and the third heat exchanger on the other a switched between the inputs of these heat exchangers controlled switching valve is used, wherein preferably the third heat storage in the heat transport medium circuit (W) is connected via a pump with connection points of a water heater.
  • W heat transport medium circuit
  • the tempering device with the refrigerating medium circuit in which the condenser, the expansion valve and the evaporator, which is intended for heat absorption and arranged with the fan are arranged in series connection of the compressors, not only one but two for passing the air arranged evaporator present, which are by switching valves alternately in the refrigeration medium circuit einbeziehbar, so perform a pendulum operation, one of the two evaporators each one of the air heat extracting evaporator is included in the cycle, while the other as heat discharging heat exchanger without evaporation function is connected to a source with warmed refrigerant, and these two connection configurations are alternately adjustable by the changeover valves.
  • the sensitivity to very cold outside air is thereby reduced by the fact that the two evaporators in the air flow individually or collectively a known ( DE 202006 010412 U1 ) upstream of the additional air-refrigerant-medium heat exchanger, which is switched on for the purpose of heat dissipation in the cold medium flow between the outlet of the condenser and the inlet of the evaporator and is located locally in the path of the air flow generated by the fan in front of the evaporator.
  • the tempering device utilizes further additional energy sources, namely in particular air streams of forced ventilation.
  • the heat-absorbing heat exchanger part is inserted in the flow channel of a heatable material containing a flowable material flow such as in particular a exhaust air flow and possibly also a supply air.
  • the further heat exchanger (s) is / are turned on with respect to the refrigerating medium circuit in a branch branching from the line leading from the compressor outlet to the circulation reversing valve and entering the line leading from the circulation reversing valve to the compressor inlet, preferably the additional heat exchanger (s) (n) in the cold medium circulation branch each not an expansion valve, but a injection of the refrigerant causing capillary tube is connected upstream.
  • the tempering device comprises an intermediate container upstream of the compressor, which serves as an expansion tank and liquid separator for the refrigerant medium and through which the input line of the compressor is guided, as well as an oil separator switched into the output line of the compressor and one from an oil collecting point in the compressor Oil separator installation branching oil return line to the compressor, which opens according to the innovation in an intermediate container, so that line clogging, which could result from lumping of possibly cooled by heat extraction separated oil in the steam lines, are avoided.
  • heat pump tempering with which can be heated and cooled, basically consists of a cycle K of a heat transport medium, which is also referred to as a refrigerant or hereinafter referred to as cryogen, with regard to its critical Pressure and its critical temperature in the work area of the plant and liquefied by pressure under heat release and elsewhere in the circuit is evaporated by pressure release while absorbing heat.
  • a heat transport medium which is also referred to as a refrigerant or hereinafter referred to as cryogen
  • Such cold media may be, for example, Frigene or halogenated fluorohydrocarbons, and ammonia is also known as a cold medium.
  • the tempering device shown further comprises a heat transport medium circuit W, which uses water here as a heat transport medium.
  • the circuit W connects to the heat discharge point of the circuit K and gives the heat absorbed partly to radiators in the house, such as an underfloor heating, and partly in a stratified storage to the hot water of the house.
  • tempering should therefore serve as a climate device for space heating or optional room cooling and also for hot water heating; it comprises an inner part I containing the heat-emitting parts, which is located in the interior, and an outer part A comprising the heat-absorbing parts, which is located outside the house.
  • the circuit K is located partly in the outer and partly in the inner part, the circuit W in the inner part.
  • Parts I and A are separated by a thin dot-dash line.
  • the expanded, vaporized and due to its vapor form a raised enthalpy having refrigerant is sucked back to the compressor.
  • the fan is shown here on the unit's airflow inlet, but in many cases it is mounted as a suction fan on the airflow outlet.
  • heat transport medium cycle W is heated in the heating mode water as a heat transport medium in the heat exchangers 2 and 3 and partly a layer memory 11 and partly fed to a buffer memory 12.
  • Schematically represented are: a domestic hot water consumer 13, for which the cold water fed from a fresh water connection 14 in the stratified storage 11 is heated, and radiators 15, which can be used for heat dissipation and also for heat absorption, ie for cooling the room.
  • the located in the inner part I part of the refrigerant circuit K has the in DE 202006 010412 U1 described construction, which is therefore not explained here in detail.
  • the medium leaves the compressor 1 via a pressure line 21, in the course of which there is an oil separator 22 which separates machine oil mixed in the refrigerant into the refrigerating medium, which would be a problematic component in the circuit, and returns it to the compressor via an oil return line 23 by adding it to the gaseous input medium of the compressor.
  • the pressure line 21 then opens into the first plate heat exchanger 2, which emits a portion of the given by the compression and liquefaction of the refrigerant heat as useful heat to the water, and continues to a circulation reversing valve 24 which is controlled as a solenoid valve and four-way switching allowed.
  • a valve output line 25 coming from the outer part A and leading to the outer part A line 26 and an intermediate links to the compressor 1 returning suction line 27.
  • a line 28 connects, which in its further course as the second refrigerant medium line, in addition to the line 26, the parts I and A together.
  • To the manifold 33 includes as an output line 26, which finally establishes the connection to the compressor 1 in the heating mode again.
  • the preheat 31 is connected as shown in the drawing with the expansion valve 5, which is followed by a Venturi, the output lines each open at an injection nozzle in the main register 32.
  • a temperature sensor 36 measures the temperature in the line 26 and sends a corresponding signal or drive voltage to the drive motor of the expansion valve 5.
  • the preheat 31 is thus still traversed by liquid hot refrigerant at high pressure, while in the main register 32 initially liquid and warm, but already under low pressure medium enters, which then evaporates under cooling and the Register circulating air withdraws heat.
  • the illustrated construction of the units 4, 4 contains even more lines and elements that stand out for themselves and their function from said DE 202006 010412 U1 are known. In cold outside air, the main register 32 tends to freeze so that it must be defrosted at intervals. This is done according to the prior art by a short cycle reversal, with heat release at the main register 32.
  • the doubling of the unit 4, 4 creates here, as will be explained, in the context of the innovation an improved possibility.
  • the compressor 1 is a pure gas compressor, and when it also sucks liquid particles on the input side, there are shocks and disturbances up to plant-damaging fluid pressure.
  • the compressor is a scroll compressor.
  • a liquid separator 41 is included so far in the compressor 1 directed toward the suction line 27, at the output almost only vaporous medium is sucked.
  • the line 27 terminates after leaving the separator 41 in an intermediate container 42, which in turn comprises two containers, namely a first storage tank 43, which serves as a surge tank and heat exchanger, and a second storage tank 44, from which a suction line to the compressor 1 leads.
  • a further line return relates to the heat exchanger 3. Between its input to the line 25 and its output to the line 28 is a return line 46 for still gaseous medium, and in this line a check valve is inserted so that only one return line, but not a bypass the heat exchanger 3 is possible.
  • This return is referred to as H constitugasum Actuallyung.
  • a bypass line 47 is still drawn, in which a solenoid valve is included, which can be opened and closed by a controller.
  • a second switching valve 50 is turned on, but always assumes the same switching position in regular operation.
  • Fig. 1 plotted are still a check valve 51, which only plays a role if only a single heat collector unit 4 is present. It is used for the fixed injection into the heat exchanger 3 during the defrosting of the evaporator 6 of this unit 4. In this phase, the heat exchanger 3 acts as an evaporator. - And an electronic injection valve 53, which plays a role in the cooling operation, for higher cooling capacity, in turn, when the heat exchanger 3 acts as an evaporator.
  • Fig. 2 shows the diagram of the refrigerant circuit K an extended tempering, namely with additional heat sources.
  • the tempering is installed in a house in which a forced ventilation with exhaust air and supply air is installed.
  • An additional heat exchanger 55 in the form of an evaporator is in the exhaust air duct and an optional additional heat exchanger 56 in the form of an evaporator is arranged in the supply air duct of the home ventilation installation.
  • the heat exchangers 55 and 56 are each not connected via an expansion valve, but via a capillary tube 57 or 58 and a switching valve and connected in parallel. They take the hot and to be evaporated refrigerant medium of the pressure line 21 at the entrance of the circulation reversing valve 24.
  • circuit K In the circuit K according to Fig. 2 are still more elements included, whose function is known per se and therefore need not be described here in detail. It is a Verdampfungsdruckregler 62 and fed via a capillary return plate heat exchanger 63, the output refrigerant medium flow of the secondary steam flow line 61 is fed, called a "minimizer" subcooler 64, which is useful for higher flow temperatures from about 65 ° C. and safety switches on the compressor inputs, namely a low pressure switch 65 and a high pressure switch 66. With respect to these circuit elements and their connections, reference is made to the drawings for relief of the description.
  • Fig. 2 shown connection of the oil separator 22.
  • Fig. 1 It is shown that the oil separator 22 feeds the separated oil back via the oil return line 23 directly into the input line of the compressor 1.
  • An alternative known connection way is that the oil is inoculated into the main vapor stream flowing to the liquid separator 41, with the consequent danger of clogging there by lumping.
  • the oil return line 23 opens in the intermediate container 42, specifically in its storage tank 44, without opening into another line. The oil to be returned is thus added to the main steam flow not in the confines of a pipeline, but in the storage tank, where it does not come to blockages.
  • FIGS. 3 and 4 are intended to illustrate the possible device arrangement, in particular of the elements of the refrigerating medium cycle K or of the heat transport medium cycle W, by means of simplified embodiments.
  • Fig. 3 two air channels are shown, namely an air channel 75 for the main heat removal of the system and an air duct 76 for the exhaust air of the living room ventilation.
  • block 77 is the By removing heat heat, so it flows, moved by the fan 7, more or less warm air and on the other hand cooled air from, as illustrated by arrows.
  • the elements of the heat transport medium circuit W are shown in a block 78, namely the return plate heat exchanger 63, the heat exchangers 2 and 3 and the subcooler 64.
  • the buffer store 12 is in the arrangement of FIG Fig. 3 unavailable.
  • Fig. 4 shows essential parts of the refrigerant circuit K and the heat transport medium circuit W, again without the optional separate buffer memory 12 and also without the optional Vormérmregister 31.
  • the heating return, in a return line 80, passes to the heat exchanger 55 and the heat exchanger block 77 and from there to acting as a buffer layer storage 11.
  • About three-way valves 84 and 85, the areas 82 and 83 of the stratified storage 11 can be fed separately from the heat exchangers.
  • the refrigerant circuit K is shown here only as a block 86, in which the heat exchanger block 77 and the exhaust duct heat exchanger 55 are included.
  • a modern design of the heat transport medium circuit W is in detail the Fig. 1 removable, then to the first and the second plate heat storage 2 and 3.
  • the upper portion 82 of the stratified memory has an input terminal 90 at the bottom thereof and an output terminal 91 at the top thereof, and the bottom portion 83 likewise has a lower input terminal 92 and an upper output terminal 93.
  • the input terminals 90 and 92 are connected to the valve 85, and the output ports 91 and 93 are connected to the valve 84.
  • the valves 84 and 85 are switchable controlled between their connected to the terminals 90, 91, 92 and 93 outputs.
  • the input of the valve 84 is connected via a pump 94 to the heat transport medium output of the heat exchanger 2, whose input is connected via a controlled changeover valve 95 to the input of the valve 85, which also connected via a controlled changeover valve 96 to the input of the heat exchanger 3 is;
  • the valves 95 and 96 can each be switched to passage from the heat exchanger to the valve 85, or to a branch, and the valve 97 can be connected to a branch or via a pump 100 to a controlled change-over valve 101 are switched.
  • the branch of the valve 96 leads to a controlled switching valve 102, and the branches of the valves 95 and 97 are connected to each other.
  • the valves 101 and 102 are each connected between heater outputs of the lower portion 83 of the stratified storage 11 and associated inputs of the buffer memory 12 and may connect these inputs either to the region 83 or to branches connected to the pump 100 and to the branch of the valve 92, respectively are connected.
  • the radiators 15 are connected to the buffer memory 12 via a pump 103, a conventional backmixing branch 104 completes the installation.
  • the circuit described is used for energy recovery for hot water preparation in the cooling mode and the improved heat transfer in the heat exchanger 3 by countercurrent operation in all operating phases.
  • FIGS. 1 to 4 can be operated in methods which will be explained with reference to the following figures.
  • FIGS. 5 and 6 show simplified diagrams of the refrigerating medium circuit K, the medium flows being illustrated in the two units operating in alternating oscillating operation.
  • the environment of the compressor 1 is not shown in detail, but to think in a block 110.
  • the respective lines through which the refrigerant flows are thick and the non-flown thin lines are drawn.
  • the two working states are changed by switching the circulation reversing valve 24, which takes place, for example, every 15 minutes.
  • the switching valve 50 is not switched for the described pendulum operation, but remains in the same switching position.
  • the line could also be pulled through, the switching enabled by this valve 50 plays a role in other operations not described here.
  • the evaporator of the unit 4 defrosted by coming from the compressor 1 liquid, warm refrigerant medium, which is then evaporated in the evaporator of the unit 4 with heat absorption, the air flowing through is cooled and the evaporator gradually iced.
  • FIGS. 7, 8 and 9 again show the lines in which the Nutzströmung takes place, in this case the hot water flow, drawn thick with a solid line, while the cold water flow is shown in thick dashed lines.
  • Fig. 7 shows the winter heating operation
  • Fig. 8 the water heating
  • Fig. 9 the summer cooling operation.
  • the coming out of the heat exchanger 3 there cooled water occurs at the upper end in the buffer memory 12 and at the bottom again off, and from there, the "radiator" 15 is supplied with cold water.
  • the refrigerant circuit K can for a system with cooling function compared to the circuit of Fig. 1 the number of valves and thus the complexity of the circuit can be reduced if there is still another, third heat exchanger between the circuits K and W.
  • the Fig. 10 shows a corresponding attachment. Opposite the Fig. 1 some changes and drawing simplifications are recognizable, for the understanding of the characteristic to be described in the context of the innovation however the features not explicitly described here are not necessary.
  • the outer part is symbolized as block 110, and in the line 28 is still referred to as a block 110 liquid separation.
  • a third heat exchanger 2 ' which is connected in parallel to the heat exchanger 2 substantially.
  • a controllable switch 112 by the switching position of either the heat exchanger 2 or the heat exchanger 2 'with the compressor is connected.
  • the lines for the heat exchanger 2 extend over a non-return valve to the buffer memory, for the heat exchanger 2 'directly to the input of the circulation reversing valve 24.
  • the outputs of the heat exchanger 2' for the heat transfer medium ie in the example described for the hot water that the service water to be heated, are connected via a pump 113 to the terminals 90 and 91 of the stratified storage tank or other boiler.
  • the third heat exchanger 2 serves as a hot water module.
  • heating mode in which the changeover valves in the in Fig. 10 shown position, it is not active, the heating hot water for the heating of the service water is supplied from the heat exchanger 2 via the valves 84 and 85.
  • the two switching valves 24 and 112 are switched, and it enters the flow pattern shown in Fig.n 9 and 11 a.
  • the heat withdrawn for cooling in the conditioned space is thus conducted past the stratified storage 11 and is finally transferred to the stratified storage or other boiler.
  • the heat pump-based tempering device described with a refrigeration medium circuit and a water circuit for the purpose of heating, where appropriate, cooling and water heating constructive by 1. the possibility of a flow direction reversal in a heat exchanger between the refrigerant circuit and the water cycle for the purpose of a countercurrent Heat exchange in all operating phases, 2. by a division of the water cycle on a stratified storage tank and a buffer for heat recovery in the cooling operation, 3. in heat absorption from the air by an alternating pendulum operation of the heat-absorbing, from time to time enteisenden heat exchanger in the refrigerant circuit, 4. By heat absorption from the exhaust air of a forced indoor ventilation, and 5. by a clog-proof return of the pressure line of the heat pump compressor with ejected machine oil in the compression it can be operated in working procedures that provide optimized utilization of available energy in safe operation.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
EP07023280A 2007-08-17 2007-11-30 Installation d'équilibrage de la température à base de pompe thermique Withdrawn EP2026019A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE202007011546U DE202007011546U1 (de) 2007-08-17 2007-08-17 Temperiereinrichtung auf Wärmepumpenbasis

Publications (2)

Publication Number Publication Date
EP2026019A2 true EP2026019A2 (fr) 2009-02-18
EP2026019A3 EP2026019A3 (fr) 2010-08-25

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EP07023280A Withdrawn EP2026019A3 (fr) 2007-08-17 2007-11-30 Installation d'équilibrage de la température à base de pompe thermique

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EP (1) EP2026019A3 (fr)
DE (1) DE202007011546U1 (fr)
WO (1) WO2009024282A2 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2500676A1 (fr) * 2011-03-14 2012-09-19 STIEBEL ELTRON GmbH & Co. KG Pompe à chaleur
EP2860469A1 (fr) * 2013-10-11 2015-04-15 Nederlandse Organisatie voor toegepast -natuurwetenschappelijk onderzoek TNO Chauffe-eau
DE102016113630A1 (de) * 2016-07-25 2018-01-25 Carnotherm Wärmelogistik GmbH & Co. KG Wärmepumpenheizung und Verfahren zum Betreiben einer derartigen Wärmepumpenheizung
DE102019001642A1 (de) * 2019-03-08 2020-09-10 Stiebel Eltron Gmbh & Co. Kg Heizungs-und/oder Warmwasserbereitungssystem

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DE102011050731A1 (de) * 2011-05-30 2012-12-06 Kermi Gmbh Wärmespeicher
DE102012011519A1 (de) * 2012-06-08 2013-12-12 Yack SAS Klimaanlage
DE102012024577A1 (de) * 2012-12-17 2014-06-18 Robert Bosch Gmbh Wärmepumpenanordnung und Verfahren zum Betrieb einer Wärmepumpenanordnung
JP5985405B2 (ja) 2013-01-28 2016-09-06 株式会社日立産機システム 油冷式ガス圧縮機における排熱回収システム
US10578339B2 (en) 2013-01-28 2020-03-03 Hitachi Industrial Equipment Systems Co., Ltd. Waste-heat recovery system in oil-cooled gas compressor
DE102013001827A1 (de) * 2013-02-04 2014-08-07 Frenger Systemen BV Heiz- und Kühltechnik GmbH Energietransfersystem
DE102016224661A1 (de) * 2016-12-12 2018-06-14 Robert Bosch Gmbh Heizsystem und Verfahren zum Betrieb eines Heizsystems

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US2135285A (en) * 1938-01-15 1938-11-01 Gen Electric Heat pump
DE19740398A1 (de) * 1997-09-09 1999-03-11 Vng Verbundnetz Gas Ag Kraft-Wärme-gekoppelte Einrichtung zur Energieversorgung
DE202006010412U1 (de) * 2006-07-05 2006-09-14 Kroll, Markus Temperiereinrichtung auf Wärmepumpenbasis

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US5937669A (en) * 1998-06-16 1999-08-17 Kodensha Co., Ltd. Heat pump type air conditioner
DE10062764A1 (de) * 2000-12-15 2002-06-20 Buderus Heiztechnik Gmbh Wärmepumpe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2135285A (en) * 1938-01-15 1938-11-01 Gen Electric Heat pump
DE19740398A1 (de) * 1997-09-09 1999-03-11 Vng Verbundnetz Gas Ag Kraft-Wärme-gekoppelte Einrichtung zur Energieversorgung
DE202006010412U1 (de) * 2006-07-05 2006-09-14 Kroll, Markus Temperiereinrichtung auf Wärmepumpenbasis

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2500676A1 (fr) * 2011-03-14 2012-09-19 STIEBEL ELTRON GmbH & Co. KG Pompe à chaleur
EP2860469A1 (fr) * 2013-10-11 2015-04-15 Nederlandse Organisatie voor toegepast -natuurwetenschappelijk onderzoek TNO Chauffe-eau
WO2015053630A1 (fr) * 2013-10-11 2015-04-16 Nederlandse Organisatie Voor Toegepast-Natuurwetenschappelijk Onderzoek Tno Chauffe-eau
DE102016113630A1 (de) * 2016-07-25 2018-01-25 Carnotherm Wärmelogistik GmbH & Co. KG Wärmepumpenheizung und Verfahren zum Betreiben einer derartigen Wärmepumpenheizung
DE102016113630B4 (de) 2016-07-25 2022-04-28 Köhler Industrie Holding GmbH & Co. KG Wärmepumpenheizung
DE102019001642A1 (de) * 2019-03-08 2020-09-10 Stiebel Eltron Gmbh & Co. Kg Heizungs-und/oder Warmwasserbereitungssystem

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Publication number Publication date
EP2026019A3 (fr) 2010-08-25
WO2009024282A3 (fr) 2009-06-18
WO2009024282A2 (fr) 2009-02-26
DE202007011546U1 (de) 2009-01-02

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