EP1620684B1 - Procede de regulation d'un cycle de carnot et installation appropriee pour sa mise en oeuvre - Google Patents

Procede de regulation d'un cycle de carnot et installation appropriee pour sa mise en oeuvre Download PDF

Info

Publication number
EP1620684B1
EP1620684B1 EP03729752A EP03729752A EP1620684B1 EP 1620684 B1 EP1620684 B1 EP 1620684B1 EP 03729752 A EP03729752 A EP 03729752A EP 03729752 A EP03729752 A EP 03729752A EP 1620684 B1 EP1620684 B1 EP 1620684B1
Authority
EP
European Patent Office
Prior art keywords
evaporator
expansion valve
working medium
supplementary
compressor
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.)
Expired - Lifetime
Application number
EP03729752A
Other languages
German (de)
English (en)
Other versions
EP1620684A1 (fr
Inventor
Felix Kalberer
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
Application filed by Individual filed Critical Individual
Priority claimed from PCT/CH2003/000361 external-priority patent/WO2003106900A1/fr
Publication of EP1620684A1 publication Critical patent/EP1620684A1/fr
Application granted granted Critical
Publication of EP1620684B1 publication Critical patent/EP1620684B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • 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
    • F25B2600/00—Control issues
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/197—Pressures of the evaporator
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
    • 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

Definitions

  • the invention relates to a method for controlling a Carnot cycle according to the preamble of claim 1 and to a system for carrying out the method according to the preamble of claim 8.
  • Carnot cycles are used to generate higher temperature heat from lower temperature heat and vice versa.
  • the equipment required for this purpose are known as heat pumps and refrigerators.
  • Well-known sources of energy include: refrigerated and freezer rooms, outdoor air, geothermal probes, groundwater, etc.
  • a method for controlling a Carnot cycle for a heat pump and a chiller are for example from DE 34 42 169 A known.
  • the exiting from the evaporator gaseous refrigerant (working fluid) flows through an inner heat exchanger in which the gaseous refrigerant overheats and the condensate is undercooled.
  • the evaporator and the condenser and especially the inner heat exchanger are designed in such a way that the overheating exclusively and the subcooling occur almost exclusively in the inner heat exchanger. The overheating is kept so great that the temperature of the refrigerant reaches a predetermined maximum value after compression.
  • the opening cross-section of the expansion valve is regulated as a function of the temperature of the refrigerant after the compressor and / or the state of the refrigerant at the evaporator outlet. It is disadvantageous that with this device the desired supercooling causes massive overheating of the suction gas in the inner heat exchanger, whereby the compressor lubricating oil tends to coke at too high temperatures and depending on the compressor design, the winding cooling of the drive motor more fully guaranteed. An optimal performance increase is not possible.
  • the object of the invention is to further improve a method for controlling a Carnot cycle and a system for its implementation.
  • the level of the temperature and the pressure of the working fluid can be increased during evaporation compared to the solution according to the prior art, without having to accept a large overheating of the suction gas in purchasing.
  • the overheating can be kept to a minimum, whereby stable conditions of the Carnot cycle can be maintained.
  • the noticeable Level - rise of the temperature and pressure of the steam on the one hand and the cooling of the working fluid before it enters the evaporator on the other hand allow a significant increase in performance of the Carnot cycle process, as more working fluid evaporates and the compressor has to overcome less pressure differences between evaporation and condensation.
  • the compressor requires less power although more suction gas is conveyed.
  • the power increase can be 10 to 30%.
  • any cooling of the condensed working fluid brings about an improvement in the performance of the system.
  • the condensed working fluid in the auxiliary evaporator is cooled to approximately the evaporation temperature.
  • control unit is additionally regulated on the basis of the temperature and / or the pressure of the working medium between the evaporator and the auxiliary evaporator. Also advantageous is a development according to claim 7, according to which the control unit is additionally regulated on the basis of the temperature of the working medium between the compressor and the condenser.
  • control features can be achieved in a system for carrying out the method, in particular a heat pump by design features.
  • a proportional evaporation of the working fluid in the multi-pass additional evaporator is achieved in which the additional evaporator has a correspondingly large heat exchanger surface.
  • Preferred is the embodiment according to claim 9, according to which the additional evaporator 10 to 30%, preferably 15 to 25%, in particular 20% of the heat exchanger surface of the evaporator.
  • the simplest control of the system is given by claim 10, characterized in that the expansion valve is formed thermostatically and by means of a arranged between the auxiliary evaporator and the compressor temperature sensor on the one hand and arranged before or after the additional evaporator pressure line on the other hand.
  • An expedient embodiment of the system is described in claim 11, wherein parallel to the expansion valve, a second expansion valve is arranged, which is controllable by a pressure line and a temperature sensor, which are arranged between the evaporator and the auxiliary evaporator, wherein the first expansion valve of a pressure line and a temperature sensor controllable is, which are arranged between the auxiliary evaporator and the compressor.
  • a second expansion valve is arranged, whose output is connected to a line between the evaporator and the auxiliary evaporator and which is controlled by a pressure line and a temperature sensor which between the Additional evaporator and the compressor are arranged, wherein the first expansion valve of a pressure line and a temperature sensor is controllable, which are arranged between the evaporator and the auxiliary evaporator.
  • the heat pumps illustrated in FIGS. 1, 4, 5 and 6 each contain a working medium circuit 10, in which an evaporator 12, an auxiliary evaporator 14, a compressor 16, a condenser 18 and an expansion valve 20 via lines 10a, 10b, 10c, 10d, 10e and 10f are interconnected.
  • the lines 10f, 10a, 10b form the suction gas side of the cycle with low pressure and the lines 10c, 10d, 10e form the hot gas side, which is under high pressure.
  • the primary sides of the evaporator 12, the auxiliary evaporator 14 and the condenser 18 are each denoted by P and the secondary sides by S, which are used as an addition to the respective reference numeral.
  • the supply line 22 and the discharge line 24 of a heat source are connected.
  • a heat source as a heat carrier, a fluid, such as water, or a gas, such as air, have.
  • a fluid such as water
  • a gas such as air
  • heat sources there are a variety of heat sources in question, such as. the exhaust air of a building or the water of a geothermal probe and the like.
  • the secondary side 12S of the evaporator 12 is connected via the line 10a to the secondary side 14S of the additional evaporator 14, which in turn is connected to the compressor 16 via the line 10b.
  • the line 10c leads to the primary side 18P of the capacitor 18, whose secondary side 18S is connected via the supply line 26 and the discharge line 28 to a heat consumer, not shown, for example, a heating system.
  • the primary side 18P of the condenser 18 is connected via the line 10a to the primary side 14P of the auxiliary evaporator 14. From there, the line 10e leads to the expansion valve 20, which in turn is connected via the line 10f to the secondary side 12S of the evaporator 12.
  • the expansion valve 20 is formed as a thermostatic expansion valve and connected via a line 30 with a temperature sensor 32 which is arranged after the additional evaporator 14 in the line 10b to the compressor 16.
  • a pressure line 34th is also connected to the expansion valve 20 and serves to control a diaphragm of the expansion valve. Since the pressure before and after the auxiliary evaporator 14 is approximately equal, the pressure line 34 can also be connected to the line 10a before the auxiliary evaporator 14, as indicated by the dashed line 34a.
  • the additional evaporator 14 is designed as a multi-pass, for example, multi-channel auxiliary evaporator and dimensioned so that it accomplishes 10 to 30%, preferably 15 to 25% of the total evaporation of the working fluid.
  • the evaporator and the additional evaporator are expediently configured the same as multi-pass evaporators, wherein the additional evaporator 14 according to the evaporation to be created 10 to 30%, preferably 15 to 25% of the heat exchanger surface of the evaporator 12 has.
  • the refrigerant immediately absorbs heat from the source.
  • the expansion valve 12 is controlled and opened via the pressure line 34, whereby more working fluid enters the evaporator 12 and the temperature of the vaporized working fluid is lowered until the set value on the suction gas side of the lines 10 a, 10 b is reached to the compressor 16.
  • the overheating of the suction gas can be maintained at a minimum value of 6 to 7 K.
  • the key data of the heat pump of Figures 1 to 3 are, for example: work equipment R 407c Area of the evaporator 12 5 m 2 Surface of the additional evaporator 14 1 m 2 Performance of the evaporator 12 16.3 kW Performance of the additional evaporator 14 2.8 kW Temperature of the spring water T1 10 ° C T2 6 ° C Temperature of the working fluid T3 2 ° C T4 3 ° C T5 7 ° C T6 65 ° C T7 31 ° C T8 12 ° C Temperature of the heat consumer T9 30 ° C T10 37 ° C
  • a second expansion valve 20a is parallel to it, which is connected via a line 36 with a temperature sensor 38 in the line 10a between the evaporator 12 and the auxiliary evaporator 14.
  • a pressure line 40 connects the line 10a to the expansion valve 20a.
  • This additional expansion valve 20a is used for additional control of the heat pump based on the data of the evaporator 12, wherein then the supply of the working fluid is controlled to the evaporator 12 at the same time.
  • a further expansion valve 20b connected in parallel, the output via the line 42 is not connected to the evaporator 12, but with the connecting line 10a between the evaporator 12 and the auxiliary evaporator 14.
  • This Expansion valve 20b is controlled via the line 30a from the temperature sensor 32 to the auxiliary evaporator 14 and the pressure line 34a, which is also connected to the auxiliary evaporator 14. Excessive overheating of the vaporized working fluid in the conduit 10b causes the expansion valve 20b to open and direct working fluid into the connecting conduit 10a to the auxiliary evaporator 14 to lower the superheat temperature.
  • the first expansion valve 20 controls the working fluid inlet to the secondary side 12S of the evaporator 12 via the line 10f.
  • To control the expansion valve 20 is connected via a line 44 with a temperature sensor 46 in the line 10 a from the evaporator 12 to the auxiliary evaporator 14.
  • a pressure line 48 establishes the connection from the line 10 a to the expansion valve 20, so that the expansion valve 20 responds to the operating state in the line 10 a, ie immediately after the evaporator 12.
  • FIG. 6 shows a heat pump with an electronic control unit 50, which is preferably computer-controlled.
  • This control unit controls the expansion valve 20c via the line 52.
  • the data required for control receives the control unit 50 via a temperature sensor 54 in the line 10b after the additional evaporator 14 via the line 56.
  • After the compressor 16 is another temperature sensor 58 via the line 60th connected to the control unit 50.
  • a further temperature sensor 62 is arranged, which is connected via the line 64 to the control unit 50.
  • a further temperature sensor 66 is finally arranged and connected via the line 68 to the control unit 50.
  • a temperature sensor 70 is connected, which is connected via the line 72 to the control unit 50.
  • the temperature and pressure conditions in the embodiments according to Figures 4 to 6 correspond to those of the embodiment of Figures 1 to 3.
  • the electronic control according to the embodiment of Figure 6 a more subtle control is possible, which allows a reduction of overheating to 4 K.
  • the electronic control also allows an increase in overheating, for example, from 4 K to 15 K when the consumer hotter water, for example 60 ° C from a source of 10 ° C is desired and find the higher hot gas temperatures useful in a storage stratified charge use , in which the water temperature from the condenser is 8 K higher than the condensation temperature.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)

Claims (15)

  1. Procédé de régulation d'un cycle de Carnot d'une installation, ayant un circuit de fluide de travail comprenant au moins : un compresseur (16), un condenseur (18), une soupape de détente (20, 20a, 20b, 20c) et un évaporateur (12) ainsi qu'un échangeur thermique (14) interne traversé par le fluide de travail condensé sortant du condenseur (18) et par le fluide de travail sortant de l'évaporateur (12), et dans lequel le fluide de travail sous forme gazeuse est surchauffé et le fluide de travail condensé est sur-refroidi, sachant que la soupape de détente (20, 20a, 20b, 20c) permet de réguler la surchauffe du fluide de travail,
    caractérisé en ce qu'
    on effectue 10 à 30 % de l'évaporation complète du fluide de travail dans l'échangeur thermique interne conçu sous forme d'évaporateur supplémentaire (14) à plusieurs passes.
  2. Procédé selon la revendication 1,
    caractérisé en ce qu'
    on effectue 15 à 25 % de l'évaporation complète du fluide de travail dans l'évaporateur supplémentaire (14).
  3. Procédé selon la revendication 1 ou 2,
    caractérisé en ce qu'
    on refroidit le fluide de travail condensé dans l'évaporateur supplémentaire (14) approximativement jusqu'à sa température d'évaporation.
  4. Procédé selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce qu'
    on utilise une soupape de détente (20, 20a, 20b) thermostatique et régule celle-ci à l'aide de la pression du fluide de travail en amont ou en aval de l'évaporateur supplémentaire (14) et de la température du fluide de travail entre l'évaporateur supplémentaire (14) et le compresseur (16).
  5. Procédé selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce qu'
    on utilise une soupape de détente (20c) régulée par une unité de régulation (50), sachant qu'au moins un capteur de pression (74, 74a) en amont ou en aval de l'évaporateur supplémentaire (14) et de la température du fluide de travail entre l'évaporateur supplémentaire (14) et le compresseur (16) permet de réguler l'unité de régulation.
  6. Procédé selon la revendication 5,
    caractérisé en ce qu'
    on régule l'unité de régulation (50) également à l'aide de la température et/ou de la pression du fluide de travail entre l'évaporateur (12) et l'évaporateur supplémentaire (14).
  7. Procédé selon la revendication 5 ou 6,
    caractérisé en ce qu'
    on régule l'unité de régulation également à l'aide de la température et/ou de la pression du fluide de travail entre le compresseur (16) et le condenseur (18).
  8. Installation pour la mise en oeuvre du procédé selon l'une quelconque des revendications 1 à 7, avec un circuit de fluide de travail comprenant au moins : un compresseur (16), un condenseur (18), une soupape de détente (20, 20a, 20b, 20c) et un évaporateur (12) ainsi qu'un échangeur thermique (14) interne traversé par le fluide de travail condensé sortant du condenseur (18) et par le fluide de travail sortant de l'évaporateur (12), et dans lequel le fluide de travail sous forme gazeuse est surchauffé et le fluide de travail condensé est refroidi, sachant que la soupape de détente (20, 20a, 20b, 20c) permet de réguler la surchauffe du fluide de travail,
    caractérisée en ce que
    l'échangeur thermique (14) interne est conçu comme un évaporateur supplémentaire (14) à plusieurs passes et l'évaporateur supplémentaire (14) présente 10 à 30 % de la surface d'échange thermique de l'évaporateur (12).
  9. Installation selon la revendication 8,
    caractérisée en ce que
    l'évaporateur supplémentaire (14) présente 15 à 25 % de la surface d'échange thermique de l'évaporateur (12).
  10. Installation selon la revendication 8 ou 9,
    caractérisée en ce que
    la soupape de détente (20, 20a, 20b) est thermostatique et peut être régulée au moyen d'un capteur de température (32) disposé entre l'évaporateur supplémentaire (14) et le compresseur (16) et par une conduite de pression (34, 34a) raccordée en amont ou en aval de l'évaporateur supplémentaire (14).
  11. Installation selon l'une quelconque des revendications 8 à 10,
    caractérisée en ce que
    une deuxième soupape de détente (20a) en parallèle à la soupape de détente (20) peut être régulée par une conduite de pression (40) et un capteur de température (38) disposés entre l'évaporateur (12) et l'évaporateur supplémentaire (14), et la première soupape de détente (20) peut être régulée par une conduite de pression (34) et par un capteur de température (32) disposés entre l'évaporateur supplémentaire (14) et le compresseur (16) (figure 4).
  12. Installation selon l'une quelconque des revendications 8 à 10,
    caractérisée en ce qu'
    en plus de la soupape de détente (20), une deuxième soupape de détente (20b) a sa sortie reliée au moyen d'une conduite (42) entre l'évaporateur (12) et l'évaporateur supplémentaire (14) et peut être régulée par une conduite de pression (34a) et un capteur de température (32) disposés entre l'évaporateur supplémentaire (14) et le compresseur (16), sachant que la première soupape de détente (20) peut être régulée par une conduite de pression (48) et un capteur de température (46) disposés entre l'évaporateur (12) et l'évaporateur supplémentaire (14) (figure 5).
  13. Installation selon la revendication 8 ou 9,
    caractérisée en ce que
    la soupape de détente (20c) peut être régulée au moyen d'une unité de régulation électronique (50) à laquelle sont raccordés au moins un capteur de température (54) disposé entre l'évaporateur supplémentaire (14) et le compresseur (16) ainsi qu'un capteur de pression (74, 74a) disposé en aval et/ ou en amont de l'évaporateur supplémentaire (14).
  14. Installation selon la revendication 13,
    caractérisée en ce que
    au moins l'un des capteurs de pression et/ou de température (58, 70) suivants est raccordé sur l'unité de régulation (50) :
    a) entre le compresseur (16) et le condenseur (18) ;
    b) entre l'évaporateur (12) et l'évaporateur supplémentaire (14).
  15. Installation selon l'une quelconque des revendications 8 à 14,
    caractérisée en ce qu'
    elle est conçue sous forme d'une pompe à chaleur.
EP03729752A 2003-05-06 2003-06-06 Procede de regulation d'un cycle de carnot et installation appropriee pour sa mise en oeuvre Expired - Lifetime EP1620684B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH7942003 2003-05-06
PCT/CH2003/000361 WO2003106900A1 (fr) 2002-06-01 2003-06-06 Procede de regulation d'un cycle de carnot et installation appropriee pour sa mise en oeuvre

Publications (2)

Publication Number Publication Date
EP1620684A1 EP1620684A1 (fr) 2006-02-01
EP1620684B1 true EP1620684B1 (fr) 2007-10-10

Family

ID=38472856

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03729752A Expired - Lifetime EP1620684B1 (fr) 2003-05-06 2003-06-06 Procede de regulation d'un cycle de carnot et installation appropriee pour sa mise en oeuvre

Country Status (3)

Country Link
EP (1) EP1620684B1 (fr)
AT (1) ATE375487T1 (fr)
DE (1) DE50308377D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103097835A (zh) * 2010-06-30 2013-05-08 丹福斯有限公司 使用过冷值操作蒸汽压缩系统的方法

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202006010412U1 (de) * 2006-07-05 2006-09-14 Kroll, Markus Temperiereinrichtung auf Wärmepumpenbasis
US9453665B1 (en) 2016-05-13 2016-09-27 Cormac, LLC Heat powered refrigeration system
EP4170262A1 (fr) * 2021-10-20 2023-04-26 Thermo King Corporation Pompe à chaleur, procédés de fonctionnement et de simulation
DE102022109795A1 (de) * 2022-04-22 2023-10-26 Ratiotherm GmbH & Co. KG Gebäudeheizung und/oder -kühlung mit einer Wärmepumpe

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103097835A (zh) * 2010-06-30 2013-05-08 丹福斯有限公司 使用过冷值操作蒸汽压缩系统的方法
CN103097835B (zh) * 2010-06-30 2016-01-20 丹福斯有限公司 使用过冷值操作蒸汽压缩系统的方法

Also Published As

Publication number Publication date
DE50308377D1 (de) 2007-11-22
ATE375487T1 (de) 2007-10-15
EP1620684A1 (fr) 2006-02-01

Similar Documents

Publication Publication Date Title
DE2545606C2 (de) Verfahren zum Betrieb eines Kühlsystems sowie Kühlsystem zur Durchführung des Verfahrens
DE3215141C2 (fr)
DE60314559T2 (de) Verfahren zum Erhöhen der Leistungsfähigkeit einer Dampfverdichtungsanordnung mittels Verdampferheizung
DE102009056027B4 (de) Fahrzeug, insbesondere Elektrofahrzeug
DE3500252C2 (de) Wärmepumpe zum Heizen oder Kühlen
DE102014014923B4 (de) Wärmepumpen-System für ein Fahrzeug
DE60128244T2 (de) Verfahren und anordnung zum abtauen einer dampfverdichtungsanlage
EP0945290B1 (fr) Procédé et dispositif de chauffage et de refroidissement pour un espace utile d'un véhicule automobile
DE102014113526A1 (de) Klimatisierungssystem für ein Kraftfahrzeug
DE19955339A1 (de) Heißwasserversorgungssystem
DE3805987A1 (de) Kaelteerzeugungskreis mit kaeltespeicherungsmaterial
DE19935731A1 (de) Verfahren zum Betreiben einer unter- und transkritisch betriebenen Fahrzeugkälteanlage
DE3229779C2 (fr)
DE60033261T2 (de) Klimaanlage
EP1620684B1 (fr) Procede de regulation d'un cycle de carnot et installation appropriee pour sa mise en oeuvre
DE602004012905T2 (de) Energie sparende klimaprüfkammer und betriebsverfahren
EP3791114A1 (fr) Système de chauffage et/ou de production d'eau chaude sanitaire
DE3106152A1 (de) "waermepumpenanordnung"
DE10108768C2 (de) Absorptionskälteanlage mit Niedertemperaturnutzung
WO2003106900A1 (fr) Procede de regulation d'un cycle de carnot et installation appropriee pour sa mise en oeuvre
DE102008043823B4 (de) Wärmepumpenanlage
WO2014131606A1 (fr) Machine frigorifique et procédé de fonctionnement d'une machine frigorifique
EP0866291B1 (fr) Pompe de chaleur à compression ou machine de refroidissement à compression et sa méthode de régulation
DE69507944T2 (de) Eine zwischenflüssigkeit verwendende wärmetausch-vorrichtung und -verfahren zum wärmeaustausch zwischen austreiber und absorber und verwendung davon in einer absorptionswärmepumpe
DE19908043A1 (de) Elektrisch angetriebenes Kompressionskältesystem eines Kraftfahrzeuges

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20051114

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 50308377

Country of ref document: DE

Date of ref document: 20071122

Kind code of ref document: P

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: SCHMAUDER & PARTNER AG PATENTANWALTSBUERO

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20080117

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080121

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080110

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080110

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080310

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

ET Fr: translation filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

26N No opposition filed

Effective date: 20080711

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

BERE Be: lapsed

Owner name: KALBERER, FELIX

Effective date: 20080630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080111

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

REG Reference to a national code

Ref country code: CH

Ref legal event code: PCAR

Free format text: SCHMAUDER & PARTNER AG PATENT- UND MARKENANWAELTE VSP;ZWAENGIWEG 7;8038 ZUERICH (CH)

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080606

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20090618

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080606

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080411

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071010

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20100712

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20100723

Year of fee payment: 8

Ref country code: FR

Payment date: 20100805

Year of fee payment: 8

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20100606

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100606

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20120229

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50308377

Country of ref document: DE

Effective date: 20120103

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120103

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110630

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110630

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110630