EP2989397A1 - Procédé et dispositif de refroidissement d'un moteur - Google Patents

Procédé et dispositif de refroidissement d'un moteur

Info

Publication number
EP2989397A1
EP2989397A1 EP14714996.7A EP14714996A EP2989397A1 EP 2989397 A1 EP2989397 A1 EP 2989397A1 EP 14714996 A EP14714996 A EP 14714996A EP 2989397 A1 EP2989397 A1 EP 2989397A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
compression stage
stage
compression
cooling
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP14714996.7A
Other languages
German (de)
English (en)
Other versions
EP2989397B1 (fr
Inventor
Max Meise
Simon Klink
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2989397A1 publication Critical patent/EP2989397A1/fr
Application granted granted Critical
Publication of EP2989397B1 publication Critical patent/EP2989397B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/025—Motor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/23—Separators
    • 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
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator

Definitions

  • the invention relates to a method for cooling a motor according to the preamble of patent claim 1 and to an apparatus for carrying out the method.
  • Such a refrigerant circuit with a two-stage compressor is used for example in connection with heat pumps.
  • the two compression stages of the compressor are driven by a motor, which is mechanically connected to it.
  • the refrigerant gas is compressed from a low level to a medium level.
  • the pressure level is then further increased until the refrigerant has a high pressure level.
  • a heat release from the refrigerant can take place via a condenser downstream of the second compression stage, which is subsequently expanded and can again absorb heat in an evaporator in order to be supplied in gaseous form to the first compression stage of the compressor.
  • heating or cooling for example of a room
  • heating or cooling for example of a room
  • the refrigerant serves to cool the engine, which can thus be operated at an optimum operating temperature.
  • refrigerant circuits usually the motor of the compressor is cooled either by the compressor sucked or by the already compressed, gaseous refrigerant.
  • the engine waste heat is supplied to the gaseous refrigerant either directly before or directly after compression.
  • Refrigerant circuits with two-stage compressors comprising a first compression stage and a second compression stage, it is known to cool the engine with the intermediate pressure level refrigerant. This happens then either by the suction gas before the second or second compression stage or by the compressed gas of the first or first compression stage.
  • the invention is based on the object to overcome the disadvantages of the prior art and in particular to provide a method and apparatus for cooling an engine, wherein the waste heat of the engine in the refrigerant circuit can be attributed without having a negative impact on the efficiency of the overall system.
  • the production cost and the regulatory burden should be as low as possible and be done with as few components.
  • the engine is cooled with a two-phase refrigerant main flow, which is the middle one.
  • the second compression stage from the middle pressure level to a high pressure level and relaxed after the second compression stage with heat release to the average pressure level Pressure level has.
  • the two-phase main refrigerant flow contains both gaseous and liquid refrigerants. Since the main refrigerant flow, ie usually the entire refrigerant flow, is used for engine cooling, no additional expansion valves are required. Accordingly, no regulation in this regard is required.
  • the waste heat removed by the engine has no negative influence on the efficiency, as it has no negative influence on the respective pressure side or on the respective suction side of the compression stages.
  • the process is applied between two of the compression stages.
  • the process can be used between two refrigerant compressors. It can also be more than one engine be cooled, where appropriate, each motor can be assigned its own refrigerant circuit.
  • the main refrigerant flow is separated into a liquid refrigerant part and a gaseous refrigerant part, wherein the gaseous refrigerant part of the second compression stage and the liquid refrigerant part of the first compression stage of the two-stage compressor are supplied.
  • the motor thus follows a separation of the two-phase refrigerant main flow in the two phases, wherein the gaseous fraction is further compressed in the second compression stage.
  • This can be done in the second compression stage directly a very efficient compression of the gaseous refrigerant to a high pressure at high temperature.
  • a medium-pressure vessel, or serve which is a collecting container, in which the refrigerant is separated into a gaseous portion and into a liquid portion.
  • the refrigerant is vaporized before the first compression stage with heat absorption and condensed after heat dissipation after the second compression stage.
  • the liquid refrigerant part takes place with subsequent evaporation in an evaporator in which heat can be absorbed, for example, from the environment.
  • the hitherto liquid refrigerant part also passes into the gaseous phase and is supplied in gaseous form to the first compression stage of the two-stage compressor where it is compressed and heated.
  • a condenser may be provided, in which a condensation of the previously gaseous refrigerant part takes place and heat is thereby released, for example, to the environment. From there, the refrigerant is continued under high pressure and partially liquefied and finally expanded to the mean pressure level.
  • the refrigerant portion after the first compression stage with that of the second compression stage after Heat dissipation coming refrigerant part before use for cooling the engine merged. This results in a combination of the two refrigerant parts, so that the entire refrigerant flow is available for cooling the engine.
  • the refrigerant part is fed directly after the first compression stage of the second compression stage, wherein the after cooling of the engine gaseous middle part of the second compression stage is supplied and merged with the coming of the first compression stage refrigerant part, wherein the refrigerant - Main flow forming, coming from the second compression stage after heat coming refrigerant is used to cool the engine.
  • the invention provides that it has an engine and a refrigerant circuit in which a two-stage compressor with a first compression stage and a second compression stage is arranged , which is drivable by the engine, wherein an engine cooling is integrated into the refrigerant circuit, that it is flowed through by a main refrigerant flow, wherein downstream of the engine cooling, a phase separation element is arranged downstream of a suction gas conduit for a gaseous refrigerant part with the second compression stage and is connected via a first line for a liquid refrigerant part with the first compression stage of the two-stage Kältem ittel compressor.
  • the entire refrigerant which is at a medium pressure level, can be used for engine cooling, and the waste heat can be returned to the refrigerant circuit.
  • a negative influence on the efficiency does not take place with it, since with the help of the phase separation element following the absorption of the heat from the engine or following the engine cooling, a separation into a gaseous and a liquid refrigerant part takes place, with only the gaseous refrigerant part of the second compression stage is supplied and thus further compressed. This can therefore be operated with high efficiency.
  • an evaporator and optionally a throttle element and possibly further components are arranged in the first line before the first compression stage. This can be done a relaxation and evaporation of the hitherto liquid refrigerant part, so that this is the first compression stage can be supplied in gaseous form. In the evaporator heat absorption takes place from an environment which is cooled thereby.
  • the other components include, for example, filters or the like.
  • a capacitor and optionally a throttle element and optionally further components are arranged in a second line of the refrigerant circuit after the second compression stage.
  • heat may be released to the environment from the gaseous refrigerant portion after the second stage of compression, whereby this refrigerant portion is at least partially liquefied.
  • throttle element which may be formed, for example, as a simple throttle or as an expansion valve, then followed by a relaxation of this refrigerant part, so that it can be used at an average pressure level liquid and / or gaseous for engine cooling.
  • the other components may be formed, for example, as cooling elements for power electronics or the like.
  • a mixing device is arranged in the refrigerant circuit before the engine cooling, which is connected to a pressure gas line coming from the first compression stage and the second line.
  • the mixing device so that coming from the first compression stage meet Refrigerant part and coming from the second compression stage refrigerant part together and can be performed from there together for engine cooling.
  • the entire refrigerant flow is used for engine cooling.
  • the second line is connected to the engine cooling, wherein a compressed gas line coming from the first compression stage opens into the suction gas line leading to the second compression stage.
  • the gaseous refrigerant part after the phase separation element can be merged with the running of the first to the second compression stage refrigerant portion before the second compression stage. Even with this simplified design, the entire refrigerant flow is led to engine cooling and used there to absorb waste heat. The coming from the first compression stage refrigerant part is not combined directly before the engine cooling with the coming of the second compression stage refrigerant part, but only passes through the second compression stage.
  • a refrigerant line between the engine cooling and phase separation element further components may be arranged. These are, for example, throttle elements and / or additional cooling elements which serve, for example, for cooling elements of power electronics.
  • the refrigerant compressor has more than two stages of compression, wherein the method according to any one of claims 1 to 5 is applied between two of the compression stages. This can also be a very strong cooling can be achieved.
  • the device has two refrigerant compressors, wherein the method is used according to one of claims 1 to 5 between the refrigerant compressors or between compression stages of the refrigerant compressors, wherein optionally more than one engine cooling takes place.
  • the device is thus very universally applicable.
  • Fig. 1 shows a refrigerant circuit with a two-stage compressor of a first embodiment
  • FIG. 2 shows a refrigerant circuit with a two-stage compressor of a second embodiment.
  • FIG. 1 schematically shows a refrigerant circuit 1 of a heat pump, which has a two-stage compressor 2 with a first compression stage 3 and a second compression stage 4.
  • the two-stage compressor 2 is operated with a motor 5, wherein a mechanical connection between the motor 5 and the compression stages 3, 4 of the two-stage compressor 2 is not shown for reasons of clarity.
  • the pressure level of a refrigerant is raised from a first pressure level to an intermediate pressure level and then to a high pressure level.
  • the refrigerant used here is a liquid which is liquid under excess pressure and which becomes gaseous after pressure is released and heat absorbed.
  • the refrigerant is supplied, for example, in gaseous form and at low pressure to the first compression stage 3 of the compressor 2 where it is brought to a medium pressure level while being heated at the same time.
  • a gaseous refrigerant component then passes in the refrigerant circuit according to FIG. 1 to a mixing device 7 and is combined there with a refrigerant part coming from the second compression stage 4.
  • This refrigerant part had been supplied to the second compression stage of the compressor 2 in gaseous form and at a medium pressure level and was brought to a high pressure level in the second compression stage 4 with simultaneous heating.
  • the gaseous refrigerant part is then fed to a condenser 9 via a second line 8 following the second compression stage 4. There is a heat transfer from the refrigerant part to an environment or heat sink 10.
  • the thus condensed heat medium part which may have both liquid and gaseous phases, is then with the help of a throttle element 11, which is for example designed as an expansion valve, relaxed to the mean pressure level at which this refrigerant part arrives at the mixing device 7 and is merged with the coming of the first compression stage 3 refrigerant part.
  • a throttle element 11 which is for example designed as an expansion valve
  • the combined refrigerant parts ie the main refrigerant flow, which comprises the entire volume flow, passes from the mixing device 7 to an engine cooling of the engine 5 and absorbs heat from the engine 5 there. Subsequently, the main refrigerant flow in a phase separation element 12 is separated into the gaseous refrigerant part and the liquid refrigerant part. The gaseous refrigerant part is then in turn fed to the second compression stage 4.
  • the liquid refrigerant part is by means of a throttle element 13, which in turn may be designed as an expansion valve, relaxed and supplied at low pressure and low temperature to an evaporator 14, in which the liquid refrigerant part is converted into a gaseous phase.
  • the evaporator 14 takes from the environment or from a heat source 15 heat, which is absorbed by the refrigerant part.
  • the throttle element 13 and the evaporator 14 are arranged in a first line 16, which connects the phase separation element 12 with the first compression stage 3 of the two-stage compressor 2.
  • an increase in the pressure of the refrigerant part vaporized in the evaporator 14 then takes place, so that it can again be supplied to the mixing device 7 at an average pressure level and at an elevated temperature.
  • FIG. 2 shows an alternative preferred embodiment, in which corresponding elements are provided with the same reference numerals.
  • the refrigerant part after the first compression stage 3 is not supplied to a motor cooling upstream mixing device, but directly the second compression stage 4.
  • gaseous refrigerant part of second compression stage 4 is supplied, the refrigerant main stream is brought in the second compression stage 4 to the high pressure level and thereby heated.
  • After heat release and condensation in the condenser 9 and subsequent expansion via the throttle element 11 then passes the refrigerant main flow having gaseous and liquid components, for cooling the motor 5 and can absorb heat there.
  • the liquid refrigerant part separated from the main refrigerant flow by the phase separation element 12 is conducted via the first line 16 and initially expanded to a low pressure level with the aid of the throttle element 13. Subsequently, an evaporation takes place in the evaporator 14, so that it is finally supplied in gaseous form to the first compression stage 3 of the compressor 3 and is brought there with simultaneous heating to a mean pressure level, in order then to reach the second compression stage 4.
  • cooling of the motor which is required to drive the two-stage compressor, takes place with the aid of the main refrigerant flow, ie through the entire refrigerant.
  • An additional bypass connection to divert a portion of the refrigerant to cool the engine is not required. Accordingly, a simplified structure results in particular by reducing the number of required expansion valves and thus simpler control.
  • the waste heat of the engine is thereby returned to the refrigerant circuit, without deteriorating the efficiency of the overall system due to the phase separation taking place after absorption of the waste heat.
  • the inventive procedure can be adapted to a refrigeration cycle with a single-stage compressor, wherein an intermediate injection and an internal heat exchanger or an intermediate injection and a phase separation can be used in a phase separation element application. Due to the design of the refrigerant circuit, a reversal of the refrigerant circuit for defrosting and / or for the cooling operation can take place, wherein the phase separation element, however, are always flowed through in the same direction

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne un procédé et un dispositif de refroidissement d'un moteur. Le moteur entraîne au moins un compresseur (2), possédant au minimum deux étages, d'un circuit de fluide réfrigérant (1), lequel comprend au moins un premier étage de compression (3) et un deuxième étage de compression (4). Un fluide réfrigérant circulant dans le circuit de fluide réfrigérant (1) est amené dans le premier étage de compression (3) d'un faible niveau de pression à un niveau de pression moyen et, dans le deuxième étage de compression (4), du niveau de pression moyen à un niveau de pression élevé pour ensuite, après le deuxième niveau de compression (4), être détendu au niveau de pression moyen en délivrant de la chaleur.
EP14714996.7A 2013-04-23 2014-04-02 Procédé et dispositif de refroidissement d'un moteur Active EP2989397B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013207344.5A DE102013207344A1 (de) 2013-04-23 2013-04-23 Verfahren und Vorrichtung zum Kühlen eines Motors
PCT/EP2014/056567 WO2014173641A1 (fr) 2013-04-23 2014-04-02 Procédé et dispositif de refroidissement d'un moteur

Publications (2)

Publication Number Publication Date
EP2989397A1 true EP2989397A1 (fr) 2016-03-02
EP2989397B1 EP2989397B1 (fr) 2020-06-10

Family

ID=50434195

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14714996.7A Active EP2989397B1 (fr) 2013-04-23 2014-04-02 Procédé et dispositif de refroidissement d'un moteur

Country Status (5)

Country Link
US (1) US20160273812A1 (fr)
EP (1) EP2989397B1 (fr)
CN (1) CN105143790B (fr)
DE (1) DE102013207344A1 (fr)
WO (1) WO2014173641A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10391835B2 (en) * 2015-05-15 2019-08-27 Ford Global Technologies, Llc System and method for de-icing a heat pump
CN111164352B (zh) * 2017-10-04 2022-07-12 比泽尔制冷设备有限公司 冷却剂压缩机设备

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2746269A (en) * 1955-03-17 1956-05-22 Trane Co Plural stage refrigerating apparatus
US3232074A (en) * 1963-11-04 1966-02-01 American Radiator & Standard Cooling means for dynamoelectric machines
FR2620205A1 (fr) * 1987-09-04 1989-03-10 Zimmern Bernard Compresseur hermetique pour refrigeration avec moteur refroidi par gaz d'economiseur
WO1997039292A1 (fr) * 1996-04-18 1997-10-23 Zakrytoe Aktsionernoe Obschestvo Nauchno-Proizvodstvennoe Obiedinenie 'vik' INSTALLATION DE REFROIDISSEMENT D'UNE PUISSANCE DE 5 ET 8 kW ET SYSTEME DE COMPRESSEUR CENTRIFUGE POUR CETTE INSTALLATION
CA2253195A1 (fr) * 1996-04-18 1997-10-23 Zakrytoe Aktsionernoe Obschestvo Nauchno-Proisvodstvennoe Obiedinenie "V Ic" Installation de refroidissement d'une puissance de 5 et 8 kw et systeme de compresseur centrifuge pour cette installation
KR100288315B1 (ko) * 1999-03-15 2001-04-16 김평길 2단 원심압축기
US7600390B2 (en) * 2004-10-21 2009-10-13 Tecumseh Products Company Method and apparatus for control of carbon dioxide gas cooler pressure by use of a two-stage compressor
CN201488382U (zh) * 2009-09-11 2010-05-26 河南千年冷冻设备有限公司 一种双级制冷系统

Also Published As

Publication number Publication date
EP2989397B1 (fr) 2020-06-10
CN105143790A (zh) 2015-12-09
DE102013207344A1 (de) 2014-10-23
US20160273812A1 (en) 2016-09-22
CN105143790B (zh) 2018-02-23
WO2014173641A1 (fr) 2014-10-30

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