EP1570215B1 - Systeme de commande de processus d'evaporation utilise dans la technique frigorifique - Google Patents
Systeme de commande de processus d'evaporation utilise dans la technique frigorifique Download PDFInfo
- Publication number
- EP1570215B1 EP1570215B1 EP02782599A EP02782599A EP1570215B1 EP 1570215 B1 EP1570215 B1 EP 1570215B1 EP 02782599 A EP02782599 A EP 02782599A EP 02782599 A EP02782599 A EP 02782599A EP 1570215 B1 EP1570215 B1 EP 1570215B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- condenser
- evaporator
- temperature
- refrigerant
- iwt
- 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
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Classifications
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
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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
- 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
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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
- 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
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
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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
- 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
- F25B2700/2103—Temperatures near a heat exchanger
-
- 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
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge 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
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21155—Temperatures of a compressor or the drive means therefor of the oil
-
- 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
- F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet 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
- F25B2700/2117—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
- 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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
Definitions
- the evaporator In order to optimally operate an evaporator in refrigeration, the evaporator is so far supplied with wet steam that a control valve (expansion valve) (3) to a minimum stable signal, usually after the evaporator outlet pressure (12) and the associated evaporator outlet temperature (13) of the refrigerant regulated is (drawing Fig. 1, 2 and 3).
- the difference of the evaporator pressure, converted into the associated evaporation temperature and the evaporation temperature actually measured as the temperature, serves as a measured variable for the control valve.
- Stable control behavior with the smallest possible temperature difference, is sought. The smallest possible temperature difference results in a higher evaporator output. If the difference is too small or the signal is unstable, there will be liquid hammer or power reduction on the compressor (1). If the difference is too large, the evaporator performance is reduced (4).
- IWT internal heat exchangers
- FIGS. 4, 5, 6 Some of the evaporators are already equipped with internal heat exchangers (IWT) (5) (FIGS. 4, 5, 6). However, these are designed as "thermally short" apparatus and not involved in the evaporator control by inlet steam content. The refrigerant liquid is not cooled down much and the suction vapors are not overheated. Overheating of the suction steam is limited to approx. 5-10K. Today's conventional injectors are not designed for maximum overheating, and the adjustable superheat is a maximum of about 20-25K.
- the aim of the invention is to achieve the following in refrigerating / freezing plants, refrigerating machines for cooling and heating operation, refrigeration systems, refrigeration sets, heat pumps, air conditioning systems and all other systems with the use of refrigerant for evaporation:
- the refrigeration system consisting essentially of compressor (1), condenser (2), injection valve (3) and evaporator (4) with an additional internal heat exchanger (5) hereinafter referred to as IWT provided (Fig. 7, 8 , 9, 10, 11).
- This IWT (5) is installed between evaporator (4) and compressor (1) on the one hand and between condenser (2) and injection valve (3) on the other hand (drawing Fig. 8, 9, 10).
- the actual evaporation (first stage) (4) takes place partially or completely in the evaporator (4).
- liquid refrigerant is admitted at the evaporator outlet.
- the regulation registered here for the first time assumes for the first time the measured variables of the liquid temperature of the refrigerant before the injection valve (3) and the evaporator pressure (FIGS. 7, 8, 9, 10, 11, points 9, 10, 11, 12).
- the evaporator pressure is removed at the inlet of the evaporator (12) (beginning of evaporation) ( Figures 7, 8, 9, 10, 11, point 12).
- the outlet pressure or any value derived from both pressure readings can also be used as the measured value (FIGS. 7, 23).
- the evaporation process is started as close as possible to the left limit curve of the 1g p, h diagram.
- the beginning of the evaporation process is defined by the liquid temperature before the injection valve (11, 9) and the evaporation pressure (12, 10) (FIGS. 7, 8, 9, 10, 11, points 11, 12, 9, 10).
- the definition of the controlled variable can be made from the evaporation pressure and a fixed (temperature) difference (adjustable) or from a stored curve calculation per refrigerant.
- the injection valve (3) lowers the temperature of the refrigerant liquid (11) before the injection valve (3) by opening the valve (3) and increases the refrigerant liquid temperature by closing the valve (3), thus trying the desired setpoint at a corresponding evaporation pressure ( 12).
- the degree of flooding or overheating (19, 13) of the evaporator or evaporators (4) thus determines the subcooling temperature of the liquid refrigerant (11) at a corresponding evaporation pressure (12) and the suction steam temperature (13) at the compressor inlet (14).
- the measured value for this safety and optimization function is the suction steam temperature at the outlet IWT (5) (13), the suction steam temperature at the inlet compressor (1) (14), the hot gas temperature (outlet compressor) (15), Oil temperature of the compressor (1) (16) or another corresponding temperature is used (Fig. 8, 9, 10, 11 points 13, 14, 15, 16).
- optimally maximum subcooling (11) of the refrigerant liquid and optimally maximum suction steam superheating (14), depending on the corresponding compressor, are sought (FIGS. 7, 9, 10, 11, points 11, 14).
- the refrigeration system consists of one or more evaporators (4), one or more IWTs (5), one or more compressors (1) or one or more injection valves (3), and whether these are grouped together or not. It also does not matter whether or not one or more evaporators (4) are grouped together with only one or more IWTs (5) (FIGS. 10-18, points 9, 10, 13, 14, 15, 16). , Any combination between injectors (3), evaporators (4), IWT's (5) and compressors (1) is therefore possible.
- the injectors (3) are mechanical, thermal, electronic or otherwise, and whether they are timed, continuous or otherwise. Relevant is the process and control loop with the listed dependencies between evaporation start 11, 12), evaporation end (13, 19) depending on the refrigerant liquid inlet temperature (21) in the IWT (5), the Saugdampfaustrittstemperatur (13) from the IWT (5) Condition of the refrigerant (wet steam (19) or superheated suction steam (13)) when leaving the evaporator (19) resp.
- the advantage of this evaporator control consists of the fact that the evaporator (4) is optimally flooded and utilized (drawing FIGS. 7, 9, 10, 11 points 17, 19) that the pressure drop on the refrigerant side via the evaporator (4) is smaller in that thereby the evaporation temperature (23) is increased, thereby smaller evaporators (4) can be used, thereby reducing the refrigerant mass flow for a required cooling capacity, thereby causing the compressors (1) to become smaller (cooling), thereby resulting in less energy for cooling is required that thereby the degrees of delivery and lubrication and thus the life of the compressor (1) is increased.
- the control is set so that the maximum power always comes to the evaporator (4) ( Figure 7, 8, 9 points 17) and not to the IWT (5) (18) (largest possible enthalpy distance at point 17).
- New to our invention is that the refrigerant enters as a liquid / gas mixture with a high gas content in a second evaporation stage (5, 18, 20) (dry evaporator), in which a residual evaporation followed by high superheating of the refrigerant (13) and a simultaneous Supercooling of the liquid refrigerant takes place on the second side of the IWT (5) (11).
- a second evaporation stage (5, 18, 20) (dry evaporator)
- a residual evaporation followed by high superheating of the refrigerant (13) and a simultaneous Supercooling of the liquid refrigerant takes place on the second side of the IWT (5) (11).
- New to our invention is that the suction steam superheating (13) is chosen as large as possible.
- a refrigeration system consisting essentially of one or more:
- a refrigeration system additionally comprises one or more of the aforementioned components and additionally desupers (24), one or more waste heat utilization exchangers, further subcoolers (25), sight glasses (7), dryers (6), filters, valves (8), safety apparatuses , Absperrapparaturen, collectors, oil pumps, distribution systems, electrical and control parts, refrigeration aids, etc. on.
- the measured value for Saugdampfbegrenzung on the suction line to the refrigerant compressor (1) is removed.
- the measured values of the refrigerant liquid temperature (11) and the evaporator inlet pressure (12) are used.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
- Sorption Type Refrigeration Machines (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Peptides Or Proteins (AREA)
- Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
Claims (9)
- Procédé de régulation d'évaporateurs (4, 12) dans des installations frigorifiques, selon lequel le fluide réfrigérant est sous-refroidi dans un condenseur (2, 25) et selon lequel un échangeur thermique interne (IWT) est utilisé entre l'évaporateur (4) et un compresseur (16) d'une part, et entre un condenseur (2, 25) et une vanne d'injection (3) d'autre part, caractérisé en ce que l'on utilise comme première grandeur réglée la pression d'évaporation (12) à l'entrée de l'évaporateur (4, 12) et comme deuxième grandeur réglée la température de sous-refroidissement du fluide réfrigérant (11) avant la vanne d'injection (3) et l'on détermine et régule ainsi le début de l'évaporation (12).
- Procédé selon la revendication 1, caractérisé en ce que la température de vapeur aspirée (13/14) à l'entrée dans le compresseur (1) est utilisée comme valeur mesurée supplémentaire pour optimiser cette régulation et garantir la protection du compresseur (1).
- Procédé selon la revendication 1 ou 2, caractérisé en ce que d'autres valeurs mesurées comme la température du gaz chaud (15) à la sortie du compresseur (1), la température de l'huile de compresseur (16), la pression d'aspiration au compresseur (23) et/ou la haute pression (22) avant la vanne d'injection (3) ou après le compresseur (1) sont utilisées pour optimiser la régulation ou pour protéger le compresseur (1).
- Procédé selon l'une des revendications 1 à 3, caractérisé en ce que l'on régule à proximité de la courbe limite gauche du diagramme 1g(p,h) pour le fluide réfrigérant (12).
- Procédé selon l'une des revendications 1 à 4, caractérisé en ce que ce type de régulation permet de noyer l'évaporateur (4) et de déterminer le degré de noyage et en même temps de contrôler et réguler la température de vapeur aspirée du fluide réfrigérant et la température du fluide réfrigérant liquide (13/11).
- Procédé selon l'une des revendications 1 à 5, caractérisé en ce que la valeur mesurée de la température de vapeur aspirée (13/14) avant le compresseur (1) ou la température du gaz chaud (15) à la sortie du compresseur (1) ou la température de l'huile de compresseur (16) a priorité sur la commande d'évaporation (11, 12) et maintient constante la température de vapeur aspirée (14) à une valeur optimale et/ou maximale en fonction du compresseur.
- Procédé selon l'une des revendications 1 à 6, caractérisé en ce que l'optimum du processus par exploitation maximale de l'enthalpie dans l'évaporateur (4) entre courbe limite gauche et droite du diagramme lg (p,h) pour le fluide réfrigérant et selon le niveau de température de l'IWT (5, 21) avec part de surchauffe dans l'évaporateur (4), profite toujours à l'évaporateur (4) et pas à l'IWT (5).
- Procédé selon l'une des revendications 1 à 7, caractérisé en ce qu'un évaporateur (4) est relié à un IWT (5) ou plusieurs évaporateurs (4) à un IWT (5) ou plusieurs évaporateurs (4) à plusieurs IWT (5) pour former un système frigorifique.
- Procédé selon la revendication 8, caractérisé en ce que selon la combinaison d'évaporateurs (4), d'IWT (5), de vannes d'injection (3) et de compresseurs (1), les vannes d'injection (3) et le système sont régulés avec un nombre réduit de valeurs mesurées (9, 10, 11, 12, 13, 14, 15, 16, 22, 23).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/CH2002/000685 WO2004053406A1 (fr) | 2002-12-11 | 2002-12-11 | Systeme de commande de processus d'evaporation utilise dans la technique frigorifique |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1570215A1 EP1570215A1 (fr) | 2005-09-07 |
EP1570215B1 true EP1570215B1 (fr) | 2007-12-05 |
Family
ID=32477088
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02782599A Expired - Lifetime EP1570215B1 (fr) | 2002-12-11 | 2002-12-11 | Systeme de commande de processus d'evaporation utilise dans la technique frigorifique |
Country Status (7)
Country | Link |
---|---|
US (1) | US7665321B2 (fr) |
EP (1) | EP1570215B1 (fr) |
AT (1) | ATE380321T1 (fr) |
AU (1) | AU2002347179A1 (fr) |
DE (1) | DE50211329D1 (fr) |
ES (1) | ES2298405T3 (fr) |
WO (1) | WO2004053406A1 (fr) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6505475B1 (en) | 1999-08-20 | 2003-01-14 | Hudson Technologies Inc. | Method and apparatus for measuring and improving efficiency in refrigeration systems |
WO2005073645A1 (fr) * | 2004-01-28 | 2005-08-11 | Bms-Energietechnik Ag | Evaporation a haut rendement dans des dispositifs frigorifiques et procede correspondant d'obtention de conditions stables avec des differences de temperature minimales et/ou requises des produits a refroidir par rapport a la temperature d'evaporation |
US7494536B2 (en) * | 2005-01-04 | 2009-02-24 | Carrier Corporation | Method for detecting a fault in an HVAC system |
ATE514044T1 (de) * | 2005-02-18 | 2011-07-15 | Carrier Corp | Steuerung einer kühlschaltung mit einem internen wärmetauscher |
DE202006000385U1 (de) * | 2006-01-11 | 2006-03-02 | Hans Güntner GmbH | Kälteanlage |
US9383127B2 (en) * | 2010-10-22 | 2016-07-05 | Tai-Her Yang | Temperature regulation system with active jetting type refrigerant supply and regulation |
DE102020115265A1 (de) | 2020-06-09 | 2021-12-09 | Stiebel Eltron Gmbh & Co. Kg | Verfahren zum Betrieb einer Kompressionskälteanlage und Kompressionskälteanlage |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS63163739A (ja) * | 1986-12-26 | 1988-07-07 | 株式会社不二工機製作所 | 冷凍システムの制御方法 |
US4878355A (en) * | 1989-02-27 | 1989-11-07 | Honeywell Inc. | Method and apparatus for improving cooling of a compressor element in an air conditioning system |
DE4430468C2 (de) * | 1994-08-27 | 1998-05-28 | Danfoss As | Regeleinrichtung einer Kühlvorrichtung |
DE19506143C2 (de) * | 1995-02-22 | 1998-01-15 | Danfoss As | Verfahren zur Regelung der Überhitzungstemperatur des Kältemittels in einer Verdampfereinrichtung einer Kälte- oder Wärmepumpanlage und Vorrichtung zur Durchführung des Verfahrens |
US6105386A (en) * | 1997-11-06 | 2000-08-22 | Denso Corporation | Supercritical refrigerating apparatus |
DE19832480A1 (de) * | 1998-07-20 | 2000-01-27 | Behr Gmbh & Co | Mit CO¶2¶ betreibbare Klimaanlage für ein Fahrzeug |
JP2000179960A (ja) * | 1998-12-18 | 2000-06-30 | Sanden Corp | 蒸気圧縮式冷凍サイクル |
US6505476B1 (en) * | 1999-10-28 | 2003-01-14 | Denso Corporation | Refrigerant cycle system with super-critical refrigerant pressure |
JP4517529B2 (ja) * | 2000-07-21 | 2010-08-04 | 株式会社日本自動車部品総合研究所 | ヒートポンプサイクル、加熱装置、車両用暖房装置、暖房装置および蒸気圧縮式冷凍サイクル |
FR2815397B1 (fr) * | 2000-10-12 | 2004-06-25 | Valeo Climatisation | Dispositif de climatisation de vehicule utilisant un cycle supercritique |
JP2002130849A (ja) * | 2000-10-30 | 2002-05-09 | Calsonic Kansei Corp | 冷房サイクルおよびその制御方法 |
JP2002267279A (ja) * | 2001-03-06 | 2002-09-18 | Zexel Valeo Climate Control Corp | 冷凍サイクル制御装置 |
US6530236B2 (en) * | 2001-04-20 | 2003-03-11 | York International Corporation | Method and apparatus for controlling the removal of heat from the condenser in a refrigeration system |
US7076964B2 (en) * | 2001-10-03 | 2006-07-18 | Denso Corporation | Super-critical refrigerant cycle system and water heater using the same |
US6817193B2 (en) * | 2001-11-23 | 2004-11-16 | Daimlerchrysler Ag | Method for operating a refrigerant circuit, method for operating a motor vehicle driving engine, and refrigerant circuit |
-
2002
- 2002-12-11 ES ES02782599T patent/ES2298405T3/es not_active Expired - Lifetime
- 2002-12-11 EP EP02782599A patent/EP1570215B1/fr not_active Expired - Lifetime
- 2002-12-11 WO PCT/CH2002/000685 patent/WO2004053406A1/fr active IP Right Grant
- 2002-12-11 US US10/538,700 patent/US7665321B2/en not_active Expired - Fee Related
- 2002-12-11 AT AT02782599T patent/ATE380321T1/de active
- 2002-12-11 AU AU2002347179A patent/AU2002347179A1/en not_active Abandoned
- 2002-12-11 DE DE50211329T patent/DE50211329D1/de not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
US20060242974A1 (en) | 2006-11-02 |
AU2002347179A1 (en) | 2004-06-30 |
EP1570215A1 (fr) | 2005-09-07 |
WO2004053406A1 (fr) | 2004-06-24 |
US7665321B2 (en) | 2010-02-23 |
ATE380321T1 (de) | 2007-12-15 |
DE50211329D1 (de) | 2008-01-17 |
ES2298405T3 (es) | 2008-05-16 |
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