EP0069756A1 - Agencement de pompes a chaleur. - Google Patents

Agencement de pompes a chaleur.

Info

Publication number
EP0069756A1
EP0069756A1 EP82900346A EP82900346A EP0069756A1 EP 0069756 A1 EP0069756 A1 EP 0069756A1 EP 82900346 A EP82900346 A EP 82900346A EP 82900346 A EP82900346 A EP 82900346A EP 0069756 A1 EP0069756 A1 EP 0069756A1
Authority
EP
European Patent Office
Prior art keywords
heat pump
heat
arrangement according
compressor
pump arrangement
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.)
Granted
Application number
EP82900346A
Other languages
German (de)
English (en)
Other versions
EP0069756B1 (fr
Inventor
Andreas Dr-Ing Hampe
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.)
Individual
Original Assignee
Individual
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=25790761&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0069756(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Individual filed Critical Individual
Priority to AT82900346T priority Critical patent/ATE14626T1/de
Publication of EP0069756A1 publication Critical patent/EP0069756A1/fr
Application granted granted Critical
Publication of EP0069756B1 publication Critical patent/EP0069756B1/fr
Expired 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • 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
    • F25B2400/061—Several compression cycles arranged in parallel the capacity of the first system being different from the second
    • 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • F25B2400/0751—Details of compressors or related parts with parallel compressors the compressors having different capacities
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • F25B49/022—Compressor control arrangements
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component

Definitions

  • the invention relates to a heat pump arrangement in which the subcooling enthalpy is used by means of a second heat pump and the heat obtained and raised to a higher temperature level can also be dissipated as useful heat in addition to that of the first heat pump.
  • the liquid working fluid in heat pumps is cooled before expanding and the heat energy generated is thus made usable.
  • the evaporation temperature of the auxiliary heat pump is essentially a function of the storage temperature
  • the object of the invention is to increase the improvement in effectiveness achieved by supercooling in a heat pump arrangement of the type specified at the outset, ie in particular to achieve a stabilization of the output with a variation in the condensation temperature and / or an improvement in the coefficient of performance.
  • This object is achieved in that a second heat pump is inserted into the circuit of the working fluid of a first heat pump in such a way that it directly cools down the liquid working fluid.
  • the liquefied working fluid (refrigerant) that emerges from the condenser and flows to the expansion valve has a temperature that is higher than the return temperature that can be achieved for heat use due to the necessary thermal contact resistance due to the heat exchanger properties of the condenser (when used for hot water heating is the temperature of the water delivered by the heat distribution system to the heat pump).
  • the liquid working medium is cooled before expansion, its enthalpy decreases, so that less liquid needs to evaporate during expansion and thus the proportion of the energy to be supplied by the heat source is increased.
  • the use of the enthalpy to be obtained from the liquid subcooling is particularly problematic because the temperature level is lower than that during the condensation.
  • the use of this enthalpy, for example for heating water, is made possible by the use of a second heat pump, which accordingly consists of an evaporator, compressor, condenser and expansion valve.
  • the evaporator of the second heat pump is inserted directly into the working fluid circuit of the first heat pump.
  • the evaporation temperature of the second heat pump is thus a function of the condensation temperature of the first heat pump, so that higher condensation temperatures lead to higher evaporation temperatures and thus to the intended improvement in the coefficient of performance of the entire heat pump arrangement. Due to the existence of only a single heat exchange process, the heat "quality" is almost retained.
  • the first and second heat pumps are designed very differently - even in the case of a shared heat utilization system.
  • the ratio of the nominal power consumption of the first heat pump and the second heat pump is approximately
  • both heat pumps can be operated together over the entire operating time and an optimal increase in the coefficient of performance and positive change in the performance behavior is achieved.
  • a smaller numerical value of the ratio leads to a reduced improvement in the coefficient of performance with a more constant heating output with increasing condensation temperature during an increase in the ratio has the opposite effect.
  • the first and second heat pumps in the case of shared heat-use systems preferably have approximately the same switch-on times, so that the improvement achieved can be optimally used.
  • the components of the heat pump arrangement are designed overall so that the 'evaporation temperature in the evaporator of the additional heat pump is (significantly) above the temperature in the evaporator of the first (basic) heat pump. This results in a noticeably higher coefficient of performance for the additional heat pump (based on approximately identical condensation temperatures) than for the basic heat pump. The coefficient of performance resulting for the entire heat pump arrangement is considerably improved.
  • the enthalpy can be extracted from the heat source and used for heating, the higher the condensation temperature, i.e. the additional heat pump largely compensates for the system-related decrease in output of the basic heat pump towards higher condensation temperatures and thus has a stabilizing effect visibly the available performance - based on the overall arrangement.
  • This stabilizing property is of particular importance because the decrease in output due to higher condensation temperatures in heat pumps used for the supply of hot water heaters goes hand in hand with the higher hot water supply temperatures required at lower outside temperatures.
  • both heat pumps can also be optimally used to supply separate consumers. If, for example, a relatively small amount of heat with the highest possible temperature is required for heating domestic water, it is advantageous if only 25 to 33% of its enthalpy is withdrawn from the liquid working medium of the first heat pump by the second heat pump.
  • the condensers of the two heat pumps are connected in series.
  • the high condensation temperatures that can be achieved thereby enable an effective utilization of the improvement in performance of a heat pump arrangement achieved by the invention by particularly effective increase in performance, particularly when there is a high demand for power.
  • the second heat pump is preferably operated with a non-azeotropic mixture of refrigerants, because the liquid working medium of the first heat pump, from which the useful heat for the second heat pump is extracted, experiences a much greater change in temperature during cooling than the carrier of the useful heat of the first heat pump.
  • the evaporator of the second heat pump assumes a locally different, ie decreasing, temperature distribution in the flow direction of the working medium of the first pump.
  • the different evaporation temperatures of the constituents of the non-azeotropic refrigerant mixture and the resulting local distribution of the evaporation areas of the individual constituents within the evaporator result in improved heat transfer and a more uniform distribution of the heat transport over the evaporator surface.
  • the parallel flow method ensures that the second heat pump is defective even if the expansion valve fails the working medium emerging from the evaporator of this heat pump has essentially the same temperature as the working medium emerging from the heat exchanger belonging to the evaporator of the first heat pump.
  • the ratio of the power consumption of the compressors of the two heat pumps is chosen to be particularly favorable if the second heat pump can remain in permanent operation together with the first one under the operating conditions that are to be considered normal, because the maximum effect achieved with respect to the operating time of the heat pump arrangement is effective is coming.
  • An exception to this is a short switch-on delay of the compressor of one of the two heat pumps - preferably the second heat pump in order to limit the starting flow of the arrangement.
  • the single figure shows a schematic representation of a heat pump arrangement according to the invention.
  • the heat pump arrangement shown in the figure initially contains the known working medium circuit of a compression heat pump components in a conventional arrangement.
  • the working fluid evaporates at a temperature T o and extracts the heat of vaporization from the medium flowing through the evaporator 1 in a separate circuit.
  • the heat of vaporization Q E is extracted from a brine flowing through the pipes 2 and 3 in the direction of the arrow, which is circulated by means of a pump 4.
  • the brine for its part, flows through heat exchangers introduced into the ground, for example — not shown — and is thereby heated. Accordingly, heat absorption from the ambient air etc. is also possible.
  • a compressor 5 draws in the vaporous working medium at a pressure p o and compresses it to the pressure p.
  • the condenser 6 which also forms a heat exchanger, the compressed, gaseous working medium liquefies at a temperature T and gives off the heat Q AI as useful heat to a heating circuit which contains a feed line 7 and a discharge line 8 and which contains a further circulation pump 9.
  • a thermostatically controlled expansion valve 10 the liquid working medium flows from the condenser 6 back to the evaporator 1, where the circuit closes.
  • the medium to be used in the working circuit is selected according to the expected temperatures and pressures.
  • the known refrigerants (mixtures) are available.
  • Compressor 12 which can be of a small design because of the relatively high evaporator temperatures, a condenser 13 serving as a heat exchanger and an expansion valve 14 complete the working medium circuit of the second heat pump.
  • the useful heat Q A2 is discharged into the lines 15 and 16, which are separated from the useful heat lines 7 and 8 of the first heat pump, in a circuit provided with a circulation pump 17. This is the system for domestic water heating, the heating system of which is supplied by the first heat pump.
  • the condenser 13 can be included in a hot water tank. Lines 15 and 16 form the process water supply and return.
  • the arrangement of the evaporator 11 of the second heat pump in the vicinity of the condenser 6 of the first heat pump and the combination of the condenser 13 of the second heat pump with the condenser 6 of the first heat pump enable a particularly compact design, since the components of the second heat pump take up relatively little space, so that they can be installed in a housing with the condenser of the second heat pump, possibly with its compressor, without requiring a substantial additional space.
  • the largest component of such a heat pump arrangement, the evaporator of the first heat pump, which is the base load, can be arranged spatially independently of the other components, but is preferably accommodated within the same housing.
  • the heat exchangers forming the condensers 5 and 13 of the two heat pumps can, depending on the requirements - according to the considerations made at the beginning - either be combined or arranged separately in order to supply useful heat for different consumers, the heat pump supplying the base load advantageously being used in the home energy sector for the heating supply is used, while the second heat pump is preferably used for domestic water heating.
  • the heat exchangers 6 and 13 can be operated both in parallel and in series according to the requirements, with the combination into a single structural unit also being advantageous here.
  • the arrangement is in the flow direction of the medium that transports the useful heat in such a way that the Useful heat is first dissipated from the condenser of the first heat pump and then from the condenser of the second heat pump, since a maximum heat flow is ensured in this way due to the temperature conditions that arise.
  • a control part 18 which opens a solenoid valve 19 together with the switching on of the compressor 12 and during the operation of the compressor keeps open.
  • a backflow preventer 20 also ensures that no refrigerant liquefied in the condenser 13 flows back into the compressor 12 during interruptions in operation. In this way, the additional heat pump can be switched on and off during operation.
  • Such a backflow preventer 20 including solenoid valve 19 is unnecessary if the compressor 5 of the second heat pump is designed as a rotary piston compressor, such a rotary piston compressor further being distinguished on the one hand by the fact that it survives wet starts without damage and on the other hand there is an inherent protection against overloading in that if the evaporation temperature is too high, the power consumption decreases.
  • the control part 18 in the figure is also designed so that it is switched on at the same time both Ver denser the start-up of the compressor 12 of the auxiliary heat pump is delayed slightly (i.e. by one or more seconds), so that the sudden load on the power supply network is reduced when the arrangement is started up.
  • the delay effect can be achieved by known electromechanical or electronic delay switching means.
  • the presence of two compressors can thus easily meet the demand of many electricity supply companies for limiting the surge load increase when switching on heat pump systems.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

Dans le circuit de circulation du fluide de travail d'une premiere pompe a chaleur (1, 5, 6, 8, 10) est inseree une deuxieme pompe a chaleur (11 a 14) de sorte qu'elle produit directement un refroidissement du fluide. Avec cet agencement, on utilise, a l'aide de la deuxieme pompe a chaleur, l'enthalpie de surrefroidissement et la chaleur ainsi obtenue, portee a un niveau de temperature plus eleve, peut etre dissipee comme chaleur utile en plus de celle fournie par la premiere pompe a chaleur.
EP82900346A 1981-01-19 1982-01-19 Agencement de pompes a chaleur Expired EP0069756B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82900346T ATE14626T1 (de) 1981-01-19 1982-01-19 Waermepumpenanordnung.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3102247 1981-01-19
DE3102247 1981-01-19
DE19813106152 DE3106152A1 (de) 1981-01-19 1981-02-16 "waermepumpenanordnung"
DE3106152 1981-02-16

Publications (2)

Publication Number Publication Date
EP0069756A1 true EP0069756A1 (fr) 1983-01-19
EP0069756B1 EP0069756B1 (fr) 1985-07-31

Family

ID=25790761

Family Applications (2)

Application Number Title Priority Date Filing Date
EP82730005A Pending EP0056780A3 (fr) 1981-01-19 1982-01-19 Disposition de pompes à chaleur
EP82900346A Expired EP0069756B1 (fr) 1981-01-19 1982-01-19 Agencement de pompes a chaleur

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP82730005A Pending EP0056780A3 (fr) 1981-01-19 1982-01-19 Disposition de pompes à chaleur

Country Status (4)

Country Link
EP (2) EP0056780A3 (fr)
DE (2) DE3106152A1 (fr)
DK (1) DK410582A (fr)
WO (1) WO1982002588A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2154459A1 (fr) * 2006-04-14 2010-02-17 Mitsubishi Denki Kabushiki Kaisha Échangeur de chaleur et appareil de conditionnement d'air de réfrigération
EP2511627A1 (fr) 2011-04-11 2012-10-17 AJ-Tech Pompe à chaleur bi-étagée à hautes performances

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19935550A1 (de) * 1999-07-30 2001-02-08 B K T Bonnet Kaeltetechnik Gmb Kälteanlage
DE10103150B4 (de) * 2001-01-24 2015-12-10 Stiebel Eltron Gmbh & Co. Kg Lüftungsanlage
SE527882C2 (sv) 2004-11-26 2006-07-04 Foersta Naervaermeverket Ab Värmeanläggning och uppvärmningsförfarande
WO2006099378A1 (fr) * 2005-03-14 2006-09-21 York International Corporation Systeme cvc equipe d'un sous-refroidisseur mecanique
FR2934890B1 (fr) * 2008-08-06 2010-09-17 Cb Froid Installation de pompe a chaleur pour le chauffage d'un fluide.
EP2211125A1 (fr) * 2009-01-27 2010-07-28 Zanotti S.p.A. Installation et procédé de production d'eau chaude et froide devant alimenter un ou plusieurs utilisateurs thermiques
DE102010056370A1 (de) * 2010-05-02 2012-06-06 KLK Klima Lüftung Kälte GmbH Vorrichtung zur Steigerung der Effizienz einer Wärmepumpe bei der Brauchwassererzeugung
JP5054180B2 (ja) 2010-11-04 2012-10-24 サンデン株式会社 ヒートポンプ式暖房装置
ITTO20111132A1 (it) * 2011-12-12 2013-06-13 Innovation Factory Scarl Unita' a pompa di calore ad alte prestazioni
SE537589C2 (sv) 2013-05-14 2015-07-07 Energy Machines S A Värmeanläggning
CN106524539B (zh) * 2016-12-22 2018-08-10 广东高而美制冷设备有限公司 利用冷热水自然对流进行过冷的太阳能空气能换热系统

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SE394741B (sv) * 1974-04-18 1977-07-04 Projectus Ind Produkter Ab Vermepumpsystem
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DE2520226A1 (de) * 1975-05-07 1976-11-25 Gerhard Heeren Mehrstufige waermepumpe
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DE2907982A1 (de) * 1979-03-01 1980-09-11 Lawrence E Lush Vorrichtung zur leistungsregelung von kuehlgeraetekompressoren
DE7908625U1 (de) * 1979-03-27 1979-07-19 Lindner, Helmut, 4600 Dortmund Modulwaermepumpe zur erwaermung von heiz- und brauchwasser aus umweltwaerme
DE2919824A1 (de) * 1979-05-16 1980-11-20 Siemens Ag Waermepumpe
DE2922119A1 (de) * 1979-05-31 1980-12-11 Kmn Beratung Beratungsbuero Fu Kombination von kaeltemaschinen und waermepumpen zur kaelte- und waermeerzeugung unter ausnutzung der naturwaerme
US4227380A (en) * 1979-11-09 1980-10-14 Frick Company Single casing, multiple duty valve

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8202588A1 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2154459A1 (fr) * 2006-04-14 2010-02-17 Mitsubishi Denki Kabushiki Kaisha Échangeur de chaleur et appareil de conditionnement d'air de réfrigération
US8272233B2 (en) 2006-04-14 2012-09-25 Mitsubishi Electric Corporation Heat exchanger and refrigerating air conditioner
EP2511627A1 (fr) 2011-04-11 2012-10-17 AJ-Tech Pompe à chaleur bi-étagée à hautes performances

Also Published As

Publication number Publication date
EP0056780A2 (fr) 1982-07-28
DK410582A (da) 1982-09-14
DE3264958D1 (en) 1985-09-05
EP0056780A3 (fr) 1982-08-25
DE3106152A1 (de) 1982-08-26
WO1982002588A1 (fr) 1982-08-05
EP0069756B1 (fr) 1985-07-31

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