EP0604417B1 - Regulation de pression en partie haute pression d'un cycle de carnot renverse transcritique - Google Patents

Regulation de pression en partie haute pression d'un cycle de carnot renverse transcritique Download PDF

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Publication number
EP0604417B1
EP0604417B1 EP91916351A EP91916351A EP0604417B1 EP 0604417 B1 EP0604417 B1 EP 0604417B1 EP 91916351 A EP91916351 A EP 91916351A EP 91916351 A EP91916351 A EP 91916351A EP 0604417 B1 EP0604417 B1 EP 0604417B1
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EP
European Patent Office
Prior art keywords
pressure
throttling valve
gas cooler
refrigerant
circuit
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
EP91916351A
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German (de)
English (en)
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EP0604417A1 (fr
Inventor
Gustav Lorentzen
Jostein Pettersen
Roar Rektorli Bang
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.)
Sinvent AS
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Sinvent AS
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Publication date
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Publication of EP0604417A1 publication Critical patent/EP0604417A1/fr
Application granted granted Critical
Publication of EP0604417B1 publication Critical patent/EP0604417B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • 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
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/063—Feed forward 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
    • 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
    • F25B2400/16—Receivers
    • 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
    • F25B2600/17—Control issues by controlling the pressure of the condenser

Definitions

  • the present invention relates to vapor compression cycle devices such as refrigerating, air-conditioning and heat pump systems, operating under transcritical conditions, and more particularly to a method of high-side pressure regulation maintaining optimum operation with respect to energy consumption.
  • PTC application WO 990/07683 discloses a transcritical vapor compression cycle device and a method for regulating its capacity based on modulation of the supercritical high-side pressure.
  • the system consists of a compressor, a gas cooler (condenser), an internal heat exchanger, an evaporator and a receiver. Capacity control is achieved by varying the liquid inventory of the low pressure refrigerant receiver situated intermediate the evaporator and the compressor, where a throttling valve between the high pressure outlet of the internal heat exchanger and evaporator inlet is applied as steering means.
  • the present invention starts from the teaching of the above mentioned WO 90/07683. It is an object of the present invention to provide for a respective method and device, respectively, which is simple and which is adapted to avoid waste of energy.
  • the modulating of the supercritical high-side pressure is performed by controlling the degree of opening of the throttling valve.
  • the control means of the device according to the invention may operatively be connected to the throttling valve and may be adapted to control the degree of opening of the throttling valve.
  • the above method may include that detection of the operating condition is conducted by measurement of the refrigerant temperature adjacent an outlet of the gas cooler.
  • the detecting means comprises means for measuring a parameter representative of the refrigerant temperature adjacent said outlet of the gas cooler.
  • the throttling valve may be a back-pressure controlling unit with variable set-point electronically controlled by a microprocessor.
  • the throttling valve is a back-pressure controlling unit with variable set-point comprising a temperature sensor bulb situated at or near the gas cooler refrigerant outlet or at another location having a temperature representing the operating condition of the circuit, and a membrane arrangement regulating the set-point of the back-pressure controlling unit in a desired relation to the bulb temperature.
  • carbon dioxide is applied as a refrigerant.
  • a well known peculiarity of transcritical cycles (operating with the refrigerant compressed to a supercritical pressure in the high-side) is that the coefficient of performance COP, defined as the ratio between the refrigerating capacity and applied compressor shaft power, can be raised by increasing the high-side pressure, while the gas cooler (condenser) outlet refrigerant temperature is maintained mainly constant. This can be illustrated by means of a conventional pressure enthalpy diagram.
  • the COP increases with increasing high-side pressure only up to a certain level and then begins to decline as the extra refrigerating effect no longer fully compensates for the extra work of compression.
  • a diagram showing the cooling capacity (Q o ), compressor shaft power (P) and their ratio (COP) as a function of high-side pressure can be provided.
  • Fig. 1 illustrates such a diagram generated for refrigerant CO2 at a constant evaporating and gas cooler (condenser) outlet temperature, based on theoretical cycle calculations.
  • the COP reaches a maximum as indicated.
  • the detected refrigerant temperature at the gas cooler (condenser) outlet or some other temperature or parameter corresponding to this will be the only significant steering parameter required as input for control of the throttling valve.
  • a back-pressure controller as throttling valve may give certain advantages in that internal compensation for varying refrigerant mass flow and density is obtained.
  • a throttling valve with back-pressure control will keep the inlet pressure, i.e. high-side pressure, at the set point regardless of refrigerant mass flow and inlet refrigerant temperature.
  • the set-point of the back-pressure controller is then regulated by means of an actuator operating in accordance with the predetermined control scheme indicated above.
  • Fig. 3 illustrates a preferred embodiment of the transcritical refrigerating circuit comprising a compressor 10 connected in series to a gas cooler (condenser) 11, an internal counterflow heat exchanger 12 and a throttling valve 13.
  • An evaporator 14 and a low pressure liquid receiver 16 are connected intermediate the throttling valve and the compressor.
  • a temperature sensor at the gas cooler (condenser) refrigerant outlet 5 provides information on the operating conditions of the circuit to the control system 7 e.g. a microprocessor.
  • the throttling valve 13 is equipped with an actuator 9 and the valve position is automatically modulated in accordance with the predetermined set-point pressure characteristics by the control system.
  • the circuit is now provided with a throttling valve 13 based on a simple mechanical back-pressure controller eliminating use of the microprocessor and electronic control of the valve shown in Example 1.
  • the regulator is equipped with a temperature sensor bulb 5 situated at or near the gas cooler (condenser) refrigerant outlet.
  • the pressure resulting from the sensor bulb temperature mechanically adjusts the set-point of the back-pressure controller according to the gas cooler (condenser) outlet refrigerant temperature.
  • the gas cooler condenser
  • the circuit is based on one of the throttling valve control concepts described in Examples 1 or 2, but instead of locating the temperature sensor or sensor bulb at the gas cooler (condenser) refrigerant outlet, the sensor or sensor bulb measures the inlet temperature of the cooling agent to which heat is rejected.
  • the sensor or sensor bulb measures the inlet temperature of the cooling agent to which heat is rejected.
  • the signal from a temperature sensor or bulb may be replaced by a signal representing the desired cooling or heating capacity of the system. Due to the correspondence between ambient temperature and load, this signal may serve as a basis for regulating throttling valve set-point pressure.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Auxiliary Devices For And Details Of Packaging Control (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Crystals, And After-Treatments Of Crystals (AREA)
  • Lasers (AREA)
  • Processing Of Solid Wastes (AREA)
  • Eye Examination Apparatus (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
  • Reduction Or Emphasis Of Bandwidth Of Signals (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Air Conditioning Control Device (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Claims (9)

  1. Procédé de commande d'un appareil à cycle de compression de vapeur transcritique travaillant à une pression supercritique du côté des valeurs élevées et comprenant un compresseur (10), un organe (11) de refroidissement de gaz, un échangeur de chaleur interne (12), une soupape d'étranglement (13), un évaporateur (14) et un récepteur (16) de fluide de refroidissement à basse pression raccordés en série sous forme d'un circuit,
    caractérisé par
    des étapes de détection de l'une au moins des conditions réelles de fonctionnement du circuit, et de modulation de la pression supercritique du côté des valeurs élevées en fonction d'un ensemble prédéterminé de valeurs qui déterminent la consommation minimale d'énergie de l'appareil dans les conditions détectées de fonctionnement pour une capacité nécessaire déterminée.
  2. Procédé de fabrication selon la revendication 1, caractérisé en ce que la modulation de la pression supercritique du côté des valeurs élevées est réalisée par réglage du degré d'ouverture de la soupape d'étranglement (13).
  3. Procédé selon la revendication 1 ou 2, caractérisé en ce que la détection de la condition de fonctionnement est réalisée par mesure de la température du fluide de refroidissement près d'une sortie (5) de l'organe (11) de refroidissement de gaz.
  4. Appareil à cycle de compression de vapeur travaillant à une pression supercritique du côté des valeurs élevées et comprenant un compresseur (10), un organe (11) de refroidissement de gaz, un échangeur de chaleur interne (12), une soupape d'étranglement (13), un évaporateur (14) et un récepteur (16) de fluide de refroidissement à basse pression raccordés en série sous forme d'un circuit,
    caractérisé par
    un dispositif de détection d'une condition de fonctionnement au moins du circuit, et un dispositif de commande (9), raccordé pendant le fonctionnement au dispositif de détection et destiné à moduler la pression supercritique du côté des valeurs élevées en fonction d'un ensemble prédéterminé de valeurs de pression élevées qui déterminent la consommation minimale d'énergie de l'appareil pour la condition détectée de fonctionnement à une capacité nécessaire déterminée.
  5. Appareil selon la revendication 4, caractérisé en ce que le dispositif (9) de commande est connecté, pendant le fonctionnement, à la soupape d'étranglement (13) et est destiné à régler le degré d'ouverture de la soupape d'étranglement (13).
  6. Appareil selon la revendication 4 ou 5, caractérisé en ce que le dispositif de détection comporte un dispositif de mesure d'un paramètre représentatif de la température du fluide de refroidissement près d'une sortie (5) de l'organe (11) de refroidissement de gaz.
  7. Appareil selon l'une quelconque des revendications 4 à 6, caractérisé en ce que la soupape d'étranglement (13) est une unité de réglage de contre-pression ayant un point de consigne variable électroniquement, réglée par un microprocesseur (7).
  8. Appareil selon l'une quelconque des revendications 4 à 6, caractérisé en ce que la soupape d'étranglement (13) est une unité de réglage de contre-pression ayant un point de consigne variable, comprenant un bulbe de capteur de température situé à la sortie (5) de fluide de refroidissement de l'organe de refroidissement de gaz ou près de cette sortie ou à un autre emplacement ayant une température qui représente la condition de fonctionnement du circuit, et un ensemble à membrane qui régule le point de consigne de l'unité de réglage de contre-pression avec une relation voulue par rapport à la température du bulbe.
  9. Appareil selon l'une quelconque des revendications 4 à 8, caractérisé en ce que l'anhydride carbonique est utilisé comme fluide de refroidissement.
EP91916351A 1991-09-16 1991-09-16 Regulation de pression en partie haute pression d'un cycle de carnot renverse transcritique Expired - Lifetime EP0604417B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/NO1991/000119 WO1993006423A1 (fr) 1991-09-16 1991-09-16 Procede de regulation de pression en partie haute dans un dispositif a cycle de carnot renverse transcritique

Publications (2)

Publication Number Publication Date
EP0604417A1 EP0604417A1 (fr) 1994-07-06
EP0604417B1 true EP0604417B1 (fr) 1996-04-17

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EP91916351A Expired - Lifetime EP0604417B1 (fr) 1991-09-16 1991-09-16 Regulation de pression en partie haute pression d'un cycle de carnot renverse transcritique

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EP (1) EP0604417B1 (fr)
JP (1) JP2931668B2 (fr)
KR (1) KR100245958B1 (fr)
AT (1) ATE137009T1 (fr)
AU (1) AU669473B2 (fr)
BR (1) BR9107318A (fr)
CA (1) CA2119015C (fr)
DE (1) DE69118924T2 (fr)
DK (1) DK0604417T3 (fr)
ES (1) ES2088502T3 (fr)
NO (1) NO180603C (fr)
RU (1) RU2088865C1 (fr)
WO (1) WO1993006423A1 (fr)

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EP0952344A2 (fr) 1998-04-16 1999-10-27 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Soupape de contrÔle de débit d'un compresseur à capacité variable pour réfrigérant
US6105380A (en) * 1998-04-16 2000-08-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Refrigerating system and method of operating the same
US6182456B1 (en) 1998-04-20 2001-02-06 Denso Corporation Supercritical refrigerating cycle system
US6523365B2 (en) * 2000-12-29 2003-02-25 Visteon Global Technologies, Inc. Accumulator with internal heat exchanger
US6923011B2 (en) 2003-09-02 2005-08-02 Tecumseh Products Company Multi-stage vapor compression system with intermediate pressure vessel
DE102005044029B3 (de) * 2005-09-14 2007-03-22 Stiebel Eltron Gmbh & Co. Kg Wärmepumpe

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JP4207340B2 (ja) * 1999-03-15 2009-01-14 株式会社デンソー 冷凍サイクル
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DE10337136A1 (de) * 2003-08-11 2005-03-24 Behr Gmbh & Co. Kg Klimaanlage und Verfahren zur Regelung der Heizleistung derselben
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JP4179231B2 (ja) 2004-06-09 2008-11-12 株式会社デンソー 圧力制御弁と蒸気圧縮式冷凍サイクル
JP4613526B2 (ja) * 2004-06-23 2011-01-19 株式会社デンソー 超臨界式ヒートポンプサイクル装置
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JP2007139342A (ja) * 2005-11-21 2007-06-07 Mitsubishi Heavy Ind Ltd 空気調和機の圧力制御弁および空気調和機
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MX2011007293A (es) 2009-01-27 2011-09-01 Emerson Climate Technologies Sistema descargador y metodo para un compresor.
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JP2013124802A (ja) * 2011-12-14 2013-06-24 Panasonic Corp 冷凍サイクル装置
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CN112432376B (zh) * 2020-11-24 2021-09-03 同济大学 二氧化碳冷藏冷冻系统及智能切换-混合控制方法

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0952344A2 (fr) 1998-04-16 1999-10-27 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Soupape de contrÔle de débit d'un compresseur à capacité variable pour réfrigérant
US6105380A (en) * 1998-04-16 2000-08-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Refrigerating system and method of operating the same
US6260369B1 (en) 1998-04-16 2001-07-17 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Flow control valve for a variable displacement refrigerant compressor
US6182456B1 (en) 1998-04-20 2001-02-06 Denso Corporation Supercritical refrigerating cycle system
DE19917048B4 (de) * 1998-04-20 2005-11-03 Kabushiki Kaisha Toyota Jidoshokki, Kariya Superkritisches Kältekreislaufsystem
US6523365B2 (en) * 2000-12-29 2003-02-25 Visteon Global Technologies, Inc. Accumulator with internal heat exchanger
US6923011B2 (en) 2003-09-02 2005-08-02 Tecumseh Products Company Multi-stage vapor compression system with intermediate pressure vessel
DE102005044029B3 (de) * 2005-09-14 2007-03-22 Stiebel Eltron Gmbh & Co. Kg Wärmepumpe

Also Published As

Publication number Publication date
DK0604417T3 (da) 1996-08-26
NO940936L (no) 1994-03-16
RU2088865C1 (ru) 1997-08-27
ES2088502T3 (es) 1996-08-16
BR9107318A (pt) 1995-11-07
DE69118924T2 (de) 1996-11-21
DE69118924D1 (de) 1996-05-23
NO940936D0 (no) 1994-03-16
NO180603B (no) 1997-02-03
WO1993006423A1 (fr) 1993-04-01
NO180603C (no) 1997-05-14
AU669473B2 (en) 1996-06-13
EP0604417A1 (fr) 1994-07-06
RU94030805A (ru) 1997-04-20
AU8530191A (en) 1993-04-27
JPH06510111A (ja) 1994-11-10
CA2119015C (fr) 2002-07-09
KR100245958B1 (en) 2000-04-01
CA2119015A1 (fr) 1993-04-01
JP2931668B2 (ja) 1999-08-09
ATE137009T1 (de) 1996-05-15

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