WO2000050826A1 - Systeme de refroidissement a compression a entrainement electrique d'un vehicule - Google Patents

Systeme de refroidissement a compression a entrainement electrique d'un vehicule Download PDF

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Publication number
WO2000050826A1
WO2000050826A1 PCT/EP2000/001238 EP0001238W WO0050826A1 WO 2000050826 A1 WO2000050826 A1 WO 2000050826A1 EP 0001238 W EP0001238 W EP 0001238W WO 0050826 A1 WO0050826 A1 WO 0050826A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
compressor
control device
refrigeration system
compression refrigeration
Prior art date
Application number
PCT/EP2000/001238
Other languages
German (de)
English (en)
Inventor
Detlef Kettner
Hans-Martin Knaus
Original Assignee
Mannesmann Vdo Ag
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 Mannesmann Vdo Ag filed Critical Mannesmann Vdo Ag
Publication of WO2000050826A1 publication Critical patent/WO2000050826A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3223—Cooling devices using compression characterised by the arrangement or type 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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor

Definitions

  • the invention relates to a compression refrigeration system of a motor vehicle air conditioning system with a compressor driven by an electric motor with a motor control device, a condenser, an expansion device and an evaporator, these being connected by means of refrigerant lines in such a way that a circulating circulation of a refrigerant from the compressor via the condenser, the expansion device and the Evaporator is returned to the compressor.
  • the invention further relates to a method for operating a corresponding compression refrigeration system.
  • Compression refrigeration systems in today's automotive air conditioning systems are driven directly by the vehicle's internal combustion engine via a belt drive.
  • the speed of the compressor driven by the belt drive is directly related to the speed of the internal combustion engine.
  • the speed of the internal combustion engine varies greatly under the various operating conditions of the vehicle. For example, a high speed will prevail on fast freeway driving, while low speeds will dominate on city trips or especially in traffic jams. This means that the lowest speed level is available, especially when driving slowly, when the required cooling capacity of the air conditioning system is usually the greatest.
  • these systems have compressors with a variable displacement. These are, for example, so-called swash plate compressors.
  • the object of the invention is therefore to provide an electrically driven compression refrigeration system in which these disadvantages are avoided be and that at the same time has a high efficiency and thus a low use of primary energy.
  • the object is achieved in a generic compression refrigeration system in that the engine and / or the engine control device are arranged in such a way that the dissipation of the heat loss of the engine and / or the engine control device takes place essentially via the refrigerant of the compression refrigeration system.
  • the refrigerant has a temperature of only a few degrees Celsius. Both the temperature of the engine and the engine control device can therefore be reduced by the measure according to the invention to a temperature level at which the losses of the engine and the engine control device are significantly lower than at the high temperatures which are usually present in the engine compartment.
  • the low temperature level for example, significantly reduces the winding resistance of the motor windings.
  • the absorption of the waste heat from the engine and / or the engine control device is taken into account.
  • a thermostatic expansion valve or an electronically controlled expansion valve can be provided to adjust the overheating at the compressor inlet. By regulating the passage of the valve and thus the refrigerant mass flow, the superheating of the refrigerant at the compressor inlet is adjusted.
  • the reference overheating for the control of the expansion device is taken off directly at the compressor inlet. As a result, the influence of the waste heat from the engine and / or the engine control device is automatically taken into account.
  • the electric motor is housed together with the compressor in a common housing.
  • This arrangement has the advantage that leaks on a rotating shaft, which can occur when the electric motor is arranged outside the compressor housing, are avoided from the start.
  • a particularly effective cooling of the electric motor is achieved when the refrigerant flows directly around the electric motor.
  • the electric motor 5 has a hollow shaft through which the refrigerant is conveyed from the refrigerant line to the compressor 6. In this known embodiment, the electric motor 5 is thus cooled by the refrigerant at most to a small extent.
  • the engine control device In order to achieve efficient cooling of the engine control device, it is arranged in close thermal contact with the refrigerant, preferably in the area between the outlet of the expansion element and the inlet of the compressor, that is to say in the area of low refrigerant temperatures.
  • the refrigerant flows directly around the engine control device.
  • the method according to the invention for operating a compression refrigeration system of a vehicle is based on a refrigeration system which has a compressor driven by an electric motor with a motor control device, a condenser, a controllable expansion element and an evaporator and a refrigerant circuit with a refrigerant. Due to the well-known mode of operation of such a compression refrigeration system, it has areas with a low and a higher temperature level.
  • the electric motor or the motor control device is cooled by the refrigerant in the region of the low temperature level. It is also provided that the refrigerant passage of the expansion element is controlled so that the refrigerant has an almost constant overheating at the inlet of the compressor.
  • This procedure enables energy-efficient operation of the compression refrigeration system.
  • the electric motor and / or the motor control device operate in an area with a reduced temperature level, so that reduced losses occur with these elements.
  • an almost constant overheating of the refrigerant is set at the inlet of the compressor. By doing this the temperature or superheat increase in the refrigerant is taken into account by the waste heat from the electric motor and / or the motor control device.
  • the overheating at the compressor inlet will be set so that so-called liquid hammer in the compressor can be excluded.
  • Liquids in the compressor are caused by refrigerant that has not evaporated completely. Any liquid content in the gaseous refrigerant is not compressible. Due to the highly dynamic compression process and the inertia of the exhaust valves, liquid can strike in the compression chamber. This effect can lead to the compressor failing.
  • the overheating of the refrigerant at the compressor inlet is selected so that there is a slight overheating of, for example, about 5 to 15 K.
  • a high value for the overheating is permitted per se, but has a negative effect on the efficiency of the overall system.
  • Figure 1 is a compression refrigeration system with an electrically driven
  • Figure 2 is a compression refrigeration system with an electrically driven
  • Figure 3 is a compression refrigeration system with an electrically driven
  • Compressor with means for setting the refrigerant overheating at the compressor inlet
  • FIG. 4 shows the cycle process taking place in the compression refrigeration system in the Mollier-h, Ig p diagram
  • Figure 5 is a schematic representation of a heating and air conditioning system of a motor vehicle.
  • a compression refrigeration system according to the invention is shown schematically. It has a compressor 6 driven by an electric motor 5.
  • the compressor 6 can in particular be a spiral compressor known per se. With the help of a scroll compressor, a continuous low-pulsation delivery of a refrigerant, not shown, is achieved.
  • the refrigeration system also has a condenser 7, an expansion element 8 and an evaporator 9.
  • the compressor 6, the condenser 7, the expansion element 8 and the evaporator 9 are connected in the manner shown by means of refrigerant lines 10, so that a continuous circulation of a refrigerant from the compressor 6 via the condenser 7, the expansion element 8 and the evaporator 9 back to the compressor 6 is achieved .
  • the refrigerant is compressed in the compressor 6 and then fed to the condenser 7.
  • heat is given off to an external medium, so that the refrigerant is liquefied.
  • the expansion element 8 there is a relaxation of the refrigerant and thus a decrease in the pressure.
  • the area between the compressor 6 via the condenser 7 to the expansion element 8 therefore forms the high-pressure side of the refrigeration system.
  • the cold that is relaxed by the expansion element 8 Teffen enters the evaporator 9 and there passes through heat absorption from an external medium into the gaseous state.
  • the gaseous refrigerant is finally sucked in by the compressor 6 and the entire process starts again.
  • the area from the expansion element 8 via the evaporator 9 to the inlet of the compressor 6 forms the low-pressure side of the refrigeration system. At the same time, this is also the area with a low temperature level compared to the temperature level on the high pressure side.
  • the electric motor 5 and the compressor 6 are in a common housing 11, and the refrigerant flows around the electric motor 5. Very good cooling of the electric motor 5 by the refrigerant thus takes place.
  • the engine control device 12 is also arranged in close thermal contact with the refrigerant.
  • the representation in the schematic representation of FIG. 1 is intended to indicate that the motor control device 12 is in the refrigeration cycle, ie the coolant flows around the motor control device 12. In this way, an optimal dissipation of the waste heat of the engine control device is achieved.
  • Various alternative installation positions 12a of the engine control device within the refrigerant circuit are shown in dashed lines in FIG.
  • the motor control device can be accommodated together with the electric motor 5 and the compressor 6 in a common housing 11.
  • Alternative locations are between the expansion element 8 and the evaporator 9, in the evaporator and between the evaporator 9 and the electric motor 5 or the compressor 6.
  • the motor control device 12 By arranging the motor control device 12 on the low pressure side and thus also on the low temperature side of the refrigerant circuit. Particularly efficient cooling of the engine control device 12 is continuously achieved. In this area the refrigerant temperature is only a few degrees Celsius. Due to the significantly lower temperature level of the motor control device 12 compared to other embodiments, only significantly lower losses occur in the latter. The reason for this is the lower heat loss of the components used in the engine control device at a lower temperature level. The same effect also occurs in the electric motor 5 cooled by the coolant to a lower temperature level. In particular, its winding losses are significantly lower than when operating at a high temperature level in the engine compartment of the motor vehicle.
  • FIG. 1 A further embodiment of the invention is shown in FIG.
  • the electric motor 5 is located together with the compressor 6 in a common housing 11.
  • the coolant preferably flows around the electric motor and cools it.
  • the engine control device 12 is now not directly included in the refrigerant circuit, but the engine control device 12 is in close thermal contact with the refrigerant without being flowed around by it.
  • the engine control device 12 can be attached directly to the housing 11, the interior of the housing being filled with refrigerant. If the housing 11 consists of a metallic material, there is very good heat transfer from the engine control device 12 to the refrigerant within the housing. This embodiment also ensures that the engine control device 12 is essentially cooled by the refrigerant.
  • the refrigerant is subjected to an additional amount of heat on the low-pressure side.
  • the overheating of the refrigerant at the inlet of the compressor 6 can thus be at a higher level than in known refrigeration systems. If this does not appear to be desirable from an energetic point of view, additional inventive measures described below can remedy the situation.
  • FIG. 4 shows a Mollier diagram with the specific enthalpy h and the logarithm of the pressure p.
  • the refrigerant is liquid in area A and gaseous in area C.
  • the refrigerant is present as so-called wet vapor, ie in gaseous form with liquid droplets.
  • the cycle in the refrigeration system is shown in the diagram in FIG. According to the standardized designation, 1 denotes the compressor inlet, 2 the compressor outlet, 3 the expansion organ inlet and 4 the evaporator inlet or the expansion organ outlet. As already mentioned at the beginning, the overheating at the compressor inlet and thus the spec.
  • FIG. 3 again shows the refrigeration system with compressor 6, condenser 7, expansion element 8 and evaporator 9.
  • a liquid separator 14 is provided between evaporator 9 and compressor 6.
  • the compressor 6 is located together with the electric motor 5 in a common housing 11.
  • the refrigerant flows directly around the electric motor 5.
  • the engine control device 12 is arranged on the housing 11 and is also cooled in this way by the refrigerant. By the waste heat of the electric motor 5 and the motor control device 12, the spec. Enthalpy of the refrigerant increased on the way from the evaporator 9 to the inlet of the compressor 6.
  • FIG. 5 schematically shows a ventilation and air conditioning device of a motor vehicle in which the compression refrigeration system described is used.
  • the air conditioning system For air supply to the interior of the motor vehicle, the air conditioning system has an air duct 15 which guides the air from the air inflow opening 16 by means of a fan 17 via the cooling device 18 and the heating device 19 to the outflow openings 20, 21, 22 into the interior.
  • the climate control takes place via the climate controller 23, which controls the blower 17, the cooling device 18 and the heating device 19.
  • the input signals for the climate controller are also the setting variables which are selected via the operating elements of the operating unit 24.
  • the cooling device 18 now includes the compression refrigeration system described above.
  • the evaporator 9 of the compression refrigeration system is arranged in the air flow of the air duct 15.
  • the refrigerant thus absorbs heat from the air drawn in in the air duct 15 and cools it down before it is supplied to the vehicle interior. As a result, the desired cooling effect of the vehicle interior is achieved.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne un système de refroidissement à compression d'une installation d'air climatisé d'un véhicule comprenant un compresseur (6) entraîné par un moteur électrique (5) doté d'un dispositif de commande (12), un condensateur (7), un organe d'expansion (8) et un évaporateur ainsi que des éléments de liaison destinés à la circulation d'un réfrigérant conçus de telle façon que la chaleur dissipée du moteur (5) et/ou du dispositif de commande (12) du moteur soit sensiblement cédée au réfrigérant. Le réfrigérant peut notamment couler autour du moteur et/ou de son dispositif de commande (12). On obtient ainsi un refroidissement particulièrement efficace des composants, ce qui permet simultanément de réduire leur chaleur dissipée. Pour obtenir un rendement élevé de l'ensemble de l'installation, il est également prévu de maintenir à un niveau quasi constant la surchauffe du réfrigérant à l'entrée du compresseur par un organe d'expansion (8) réglé.
PCT/EP2000/001238 1999-02-24 2000-02-16 Systeme de refroidissement a compression a entrainement electrique d'un vehicule WO2000050826A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19908043A DE19908043C2 (de) 1999-02-24 1999-02-24 Elektrisch angetriebenes Kompressionskältesystem eines Kraftfahrzeuges
DE19908043.7 1999-02-24

Publications (1)

Publication Number Publication Date
WO2000050826A1 true WO2000050826A1 (fr) 2000-08-31

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PCT/EP2000/001238 WO2000050826A1 (fr) 1999-02-24 2000-02-16 Systeme de refroidissement a compression a entrainement electrique d'un vehicule

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DE (1) DE19908043C2 (fr)
WO (1) WO2000050826A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
LU90890B1 (en) 2002-02-15 2003-08-18 Delphi Tech Inc Cooling of electronics in an electrically driven refrigeration system
US11198345B2 (en) * 2015-11-27 2021-12-14 Inps Environmental Products Inc. Method and apparatus for cooling and heating in a vehicle

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10027617A1 (de) * 2000-06-02 2001-12-06 Mannesmann Vdo Ag Einrichtung zum Antrieb eines Klimakompressors
DE10128307B4 (de) * 2001-06-12 2004-03-18 Siemens Ag Klimaanlage
WO2007139537A1 (fr) * 2006-05-26 2007-12-06 Carrier Corporation commande de surchauffe POUR systÈmes CVCAR
DE102013004252A1 (de) 2013-03-12 2014-10-02 Kurt Orthmann Klimaanlage, die Wärme zusätzlich zur Kompression verwendet und dadurch Antriebsenergie für den Kompressor einspart
DE102013208369A1 (de) * 2013-05-07 2014-11-13 Siemens Aktiengesellschaft Vorrichtung mit einer elektronischen Komponente und einer Kältemaschine zum Kühlen der elektronischen Komponente sowie Verfahren zum Kühlen einer elektronischen Komponente

Citations (8)

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Publication number Priority date Publication date Assignee Title
US4720981A (en) * 1986-12-23 1988-01-26 American Standard Inc. Cooling of air conditioning control electronics
DE3731360A1 (de) 1986-09-22 1988-03-31 Gen Electric Verfahren und einrichtung zum regeln einer elektrisch angetriebenen kfz-klimaanlage
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
EP0385766A2 (fr) * 1989-03-03 1990-09-05 Sanden Corporation Dispositif de commande pour une installation d'air conditionné d'automobile
US5350039A (en) * 1993-02-25 1994-09-27 Nartron Corporation Low capacity centrifugal refrigeration compressor
DE9416795U1 (de) * 1994-10-19 1995-01-26 Ilka Mafa Kältetechnik GmbH, 06184 Döllnitz Ammoniak-Kompressionskälteanlage
WO1997002729A1 (fr) * 1995-07-06 1997-01-23 Danfoss A/S Compresseur a electronique de commande
US5927089A (en) * 1995-11-13 1999-07-27 O'donnell; Dennis W. Air conditioner for a motor vehicle

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JPH0754207B2 (ja) * 1986-11-25 1995-06-07 日本電装株式会社 冷凍サイクル装置
DE4212162C2 (de) * 1992-04-10 1994-02-17 Ilka Maschinenfabrik Halle Gmb Einrichtung zur Kühlung des Elektromotors eines halbhermetischen Kältemittelverdichters
DE19706663B4 (de) * 1997-02-20 2007-01-11 Behr Gmbh & Co. Kg Verfahren zur Regelung einer Klimaanlage in einem Kraftfahrzeug
DE19726943C2 (de) * 1997-06-25 2000-03-23 Bitzer Kuehlmaschinenbau Gmbh Kältemittelkompressor

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3731360A1 (de) 1986-09-22 1988-03-31 Gen Electric Verfahren und einrichtung zum regeln einer elektrisch angetriebenen kfz-klimaanlage
US4720981A (en) * 1986-12-23 1988-01-26 American Standard Inc. Cooling of air conditioning control electronics
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
EP0385766A2 (fr) * 1989-03-03 1990-09-05 Sanden Corporation Dispositif de commande pour une installation d'air conditionné d'automobile
US5350039A (en) * 1993-02-25 1994-09-27 Nartron Corporation Low capacity centrifugal refrigeration compressor
DE9416795U1 (de) * 1994-10-19 1995-01-26 Ilka Mafa Kältetechnik GmbH, 06184 Döllnitz Ammoniak-Kompressionskälteanlage
WO1997002729A1 (fr) * 1995-07-06 1997-01-23 Danfoss A/S Compresseur a electronique de commande
US5927089A (en) * 1995-11-13 1999-07-27 O'donnell; Dennis W. Air conditioner for a motor vehicle

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
LU90890B1 (en) 2002-02-15 2003-08-18 Delphi Tech Inc Cooling of electronics in an electrically driven refrigeration system
EP1336518A2 (fr) 2002-02-15 2003-08-20 Delphi Technologies, Inc. Réfrigération d'unités électroniques dans un système frigorifique électrique
EP1336518A3 (fr) * 2002-02-15 2003-10-22 Delphi Technologies, Inc. Réfrigération d'unités électroniques dans un système frigorifique électrique
US6708521B2 (en) 2002-02-15 2004-03-23 Delphi Technologies, Inc. Cooling of electronics in an electrically driven refrigerant system
US11198345B2 (en) * 2015-11-27 2021-12-14 Inps Environmental Products Inc. Method and apparatus for cooling and heating in a vehicle

Also Published As

Publication number Publication date
DE19908043A1 (de) 2000-09-07
DE19908043C2 (de) 2001-08-30

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