EP2932169A1 - Unité compresseur et véhicule utilitaire équipé d'une machine de refroidissement comportant une telle unité compresseur - Google Patents

Unité compresseur et véhicule utilitaire équipé d'une machine de refroidissement comportant une telle unité compresseur

Info

Publication number
EP2932169A1
EP2932169A1 EP13811863.3A EP13811863A EP2932169A1 EP 2932169 A1 EP2932169 A1 EP 2932169A1 EP 13811863 A EP13811863 A EP 13811863A EP 2932169 A1 EP2932169 A1 EP 2932169A1
Authority
EP
European Patent Office
Prior art keywords
compressor
refrigerant
compressor unit
motor housing
drive motor
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.)
Withdrawn
Application number
EP13811863.3A
Other languages
German (de)
English (en)
Inventor
Norbert Flacke
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.)
Schmitz Cargobull AG
Original Assignee
Schmitz Cargobull 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 Schmitz Cargobull AG filed Critical Schmitz Cargobull AG
Publication of EP2932169A1 publication Critical patent/EP2932169A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1081—Casings, housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • 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
    • F25B49/022—Compressor 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/023—Compressor control controlling swash plate angles
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/023—Compressor arrangements of motor-compressor units with compressor of reciprocating-piston type
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • Compressor unit and commercial vehicle with a cooling unit comprising such a compressor unit
  • the invention relates to a compressor unit for
  • Compressing refrigerant and a commercial vehicle with a refrigeration machine comprising such a compressor unit.
  • a medium to be cooled is passed through a heat exchanger through which a refrigerant flows simultaneously in spatial separation, but in heat-conducting contact with the cooling medium.
  • Refrigerant expands in an endothermic reaction in the heat exchanger (evaporator), thereby removing heat from the medium to be cooled.
  • the emerging from the evaporator heat exchanger refrigerant is from the
  • Refrigerants are used today in many areas of daily life. For example, the air conditioning of passenger areas in vehicles or residential or commercial premises, as well as cooling in the supermarket, industrial and marine sectors, or even in the field of what is known as "transport refrigeration".
  • Transport refrigeration is needed when transporting temperature-sensitive goods from the producer to the processor, trader or end consumer. For this
  • Transport tasks are widely used commercial vehicles with thermally insulated structures, each equipped with a chiller to keep the stored in the construction space enclosed cargo during transport at a predetermined temperature.
  • EP 1 046 543 B1 A transport refrigerating machine suitable for this purpose is known from EP 1 046 543 B1. This exemplified for a variety of refrigerators designed machine is designed so that it can be mounted as a separate unit to the respective commercial vehicle. A special feature over other known, based on similar concepts Transportkühl respondeden is that in the EP 1 046 543 B1
  • the compressor is driven by an electric drive motor.
  • the electrical energy to drive the engine is from a likewise in the
  • Chiller built-in combustion engine generator combination provided, which can be operated in each case in a stationary, performance-optimized operating point.
  • Compressor and drive motor form in the known refrigerating machine, a compressor unit, which is complete by means of a drive motor and compressor housing together fully or semi-hermetically sealed to the environment. Characteristics of such full or
  • semi-hermetically sealed compressor units is that the drive motor and compressor have a common shaft and no special sealing of the shaft of the Compressor against leakage of refrigerant fluid into the environment or the drive motor is required, as by the hermetic shielding of compressor and
  • the refrigerant fluid can be used to cool the drive motor.
  • Compressor unit of the type described above are compensated by the fact that the drive motor is selectively positioned in adeluftström, by the
  • Chiller is passed.
  • the operating temperatures of the drive motor increase so much that additional measures for cooling the engine are required under such extreme conditions.
  • Refrigerant removes the waste heat produced by the drive motor so that harmful temperature peaks are avoided.
  • this requires not only a comparatively complicated design of the components, which are flowed through by the out of the motor housing back into the compressor refrigerant, but also a
  • the object of the invention to provide a compressor unit, in which simple
  • the solution of the above-mentioned object is that in the refrigerator of such a commercial vehicle, an inventive
  • Compressor unit is used.
  • a compressor unit according to the invention for compressing refrigerant thus comprises, in accordance with the prior art described above, an electric drive motor having a motor housing which encapsulates the drive motor from the environment, and a compressor driven by the drive motor
  • the motor housing of the drive motor is now at least partially flowed around at least by a partial flow of the refrigerant suction flow, wherein the flow around is not necessarily constant, but may be required. According to the invention thus the motor housing of the drive motor of the
  • the drive motor is arranged in the refrigerant suction stream which, after having coupled it to the compressor unit according to the invention
  • Motor housing enclosed engine compartment is passed, even the motor housing itself do not meet any special requirements. It can thus be used as far as possible conventionally designed components, resulting in the cost of producing a novel
  • the compressor unit according to the invention can be arranged at any point in the intake flow of the compressor, at which the motor housing of the drive motor in sufficient for heat dissipation from the to
  • Refrigerant flow is flowed around.
  • the invention is characterized in that it comprises a motor housing jacket, which at least partially the motor housing to form a with a
  • Ansaugan Press the compressor connected flow channel einhaust through which flows in the cooling operation of the refrigerant suction flow.
  • the motor housing jacket can be the motor housing
  • Forming flow channel for the refrigerant suction flow It is also conceivable, in the manner of cooling coils, to place a tubular channel around the motor housing, through which the refrigerant suction flow flows and which is in good thermal contact with the motor housing. Likewise, it may be expedient to design the jacket housing the motor housing in such a way that the refrigerant suction stream flows against the end face of the motor housing facing away from the compressor and starts from there
  • Airflow or the like is discharged and the
  • Cooling according to the invention by the refrigerant suction flow is used only at high temperatures.
  • a control device for adjusting the refrigerant suction flow is provided, which flows around the motor housing.
  • This control device can be set, for example, so that the cooling refrigerant flow is passed only to the motor housing when a certain high outside temperature is exceeded.
  • Compressor unit additionally heated refrigerant must then be applied only in this operating condition. Even with a compressor unit according to the invention, a particularly compact design can be characterized
  • Motor housing is tightly connected to an associated side of a housing of the compressor and that
  • the leakage flow consists of refrigerant or oil, which is present in the crankcase of the compressor, wherein refrigerant and oil can of course escape as a mixture.
  • the seal may be appropriate to form the seal as a shaft seal package, which is formed by at least two in the axial direction of the drive shafts of the compressor and drive motor with spaced shaft seals, which define a sealing space between them. In such a cascade of multiple shaft seals each shaft seal is a further obstacle to the passage of refrigerant or oil into the engine compartment.
  • At least one outlet for discharging refrigerant, oil or other residues may be provided in a compressor unit according to the invention
  • Compressor enter the motor housing.
  • a shaft seal package is provided with a sealing space enclosed therein, it may be expedient to connect such an outlet to the seal chamber of the seal. In this way, the leaking from the compressor leakage volume can be deducted before it in the motor housing
  • the pollution of the environment by leaking from the compressor unit refrigerant fluid can be minimized in that the output of at least one of each provided
  • Sealing space can be increased by the fact that
  • Flow channel has a bypass section and that a control device is provided for regulating the refrigerant flow through the bypass section.
  • Refrigerant suction flow can be optimized in terms of flow so that the refrigerant flowing through the bypass to the suction side of the compressor flows out of the
  • Exhaust valve entrains escaping refrigerant and dissipates from the shaft seal.
  • Amount of heat generated in the area of the engine to dissipate via the refrigerant suction flow can be boosted by the natural heat radiation of the motor housing, in turn optionally forced by a blown against the motor housing or its casing
  • Airflow be dissipated.
  • air-cooled cooling devices can be dimensioned to a desired size, in particular reduced in size.
  • regulated flow cross sections for the suction gas used for cooling can be implemented for controlling the respective refrigerant suction flow for cooling around the motor housing or along the same.
  • Suitable devices for this purpose are, for example, valves or diaphragms.
  • Control parameters can be, for example, the temperature of the motor or the motor housing.
  • each controllable compressor in particular an axial piston compressor with stepless stroke control, such as a swash plate compressor or swash plate compressor are used.
  • a swash plate compressor or swash plate compressor are used.
  • existing compressor pressure is expediently greater than or equal to the suction pressure and less than or equal to the high pressure.
  • Fig. 1 shows a first embodiment of a compressor unit in a longitudinal section
  • Fig. 2 shows a second embodiment of a compressor unit in a longitudinal section.
  • the compressor units V1, V2 shown in the figures each include an electrically driven drive motor 1 and a compressor 2.
  • the compressor 2 is designed in the swash plate design.
  • any other type of compressor can be used, so for example one
  • Radial piston compressor or an axial piston compressor with constant piston stroke Radial piston compressor or an axial piston compressor with constant piston stroke.
  • the compressor 2 is used for compressing a refrigerant, which is, for example, a commercially available synthetic or natural refrigerant.
  • the compressor 2 For compression, the compressor 2 comprises pistons 3,4.
  • the pistons 3, 4 are linearly reciprocable in cylinder chambers 5, 6, which are formed in a cylinder block 7.
  • the pistons 3, 4 are each articulated via a connecting rod 8, 9 and in each case one sliding block 10, 11 to a swivel disk 12.
  • a drive shaft 13 of the compressor 2 with its end remote from the drive motor 1 is mounted in the cylinder block 7.
  • the swash plate 12 is rotatably in operative engagement with the drive shaft 13. It is relative to
  • Double arrow 14 illustrates.
  • the stroke of the piston 3,4 By changing the enclosed between the drive shaft 13 and the swash plate 12 inclination angle ß the stroke of the piston 3,4 and thus the geometric displacement can be adjusted continuously.
  • the swash plate 12 may also have the shape of a pivot ring.
  • the compressor 2 has a compressor housing 15, which defines a crank chamber 16.
  • the swash plate 12 is mounted on the guided drive shaft 13. It is in the crankcase 16 a
  • Embodiment is adjustable. By adjusting the crank chamber pressure PK can be adjusted in a conventional manner, the inclination of the swash plate 12 and thus
  • Crank chamber pressure PK on the crank chamber 16 associated side of the piston 3,4 works, so that at elevated Crank chamber pressure PK of the suction movement of the piston 3.4 counteracts an increased force and consequently in the
  • Suction movement covered piston travel is smaller than at a low piston chamber pressure PK.
  • the compressor 2 comprises a cylinder head 17, in which a suction chamber 18, which is acted upon by a suction pressure, and a pressure chamber 19 are arranged, which is acted upon by a high pressure. Via the suction chamber 18 to be compressed refrigerant via an inlet valve 20 into the cylinder chambers 5,6 of the compressor and is there compressed by the reciprocating piston 3,4.
  • the compressed refrigerant passes through outlet valves 21 into the pressure chamber 19, from where it is fed via an outlet, not shown here, to a heat exchanger, also not shown here, through which the atmosphere to be cooled flows.
  • the inclination angle ß can be adjusted in a conventional manner by adjusting the compressor pressure in the crank chamber 16. This can also be a se
  • Compressed gas connection 22 be unregulated while in the
  • Relief connection 23 a control valve 24 is arranged. Alternatively, however, a control valve 25 in the
  • Compressed gas connection 22 may be provided or it may be set in addition to the control valve 24 in the compressed gas connection 22, such a control valve to both the
  • crank chamber 16 Pressure relief and the pressurization can be regulated separately.
  • adjustable diaphragms or the like would also be conceivable, for example.
  • Crank chamber pressure is greater than or equal to the suction pressure and less than or equal to the high pressure to which the refrigerant is exposed in the pressure chamber 19 after compression.
  • Compressor housing 15 is guided there and engages positively and non-rotatably in a receptacle of the drive shaft 27 of the drive motor 1. In this way, a rotationally fixed, but releasable connection between the drive shafts 13,27 is formed.
  • the sealing of the compressor housing 15 with respect to the drive motor 1 is effected on the compressor side by a stuffing box 28 arranged in the region of the end wall opening and acting against the drive shaft 13.
  • a stuffing box 28 arranged in the region of the end wall opening and acting against the drive shaft 13.
  • another seal by a stuffing box 28 arranged in the region of the end wall opening and acting against the drive shaft 13.
  • Shaft seal 29 formed. To this end, the shaft seal 29 sits in an end opening formed as a receiving opening of a motor housing 30 accommodating the drive motor 1 and also acts against the associated peripheral surface of the motor housing 30 protruding
  • the gland 28 and the shaft seal 29 thus form a shaft seal package. In doing so, they define between them a sealing space 31 which is delimited on the circumference by the inner peripheral surfaces of the passage opening or a holder for the shaft seal 29 inserted therein.
  • the drive motor 1 is described here
  • Embodiments connected to a speed control device 32.
  • a stationary, unregulated operation is possible if this is sufficient for the particular application.
  • the conventionally constructed drive motor 1 is located with the end face of its motor housing 30 close to the associated end face 26 of the compressor housing 15 and is detachable with the compressor housing 15 in a conventional manner by means not shown here screws
  • the drive motor 1 is encased by a motor housing shell 33, which is laid in each case at a uniform distance around the outer peripheral surface of the motor housing 30 and also remote from the compressor 2 at a distance
  • Front side 34 of the motor housing 30 covers. In this way, the motor housing 30 is circumferentially and on at its End 34 wrapped by a gap 35.
  • Motor housing jacket 33 abuts against the end face 26 of the compressor housing 15 and is connected to this tight, but also releasably connected.
  • the gap 35 delimited by the motor housing jacket 33 is connected to a suction line 37 which leads to the suction chamber 18 of the compressor 2.
  • a suction inlet 38 is formed, to which an outflow line 39 of the not shown here, of the respective
  • the refrigerant suction flow K entering the motor casing jacket 33 floods the gap 35, thereby sweeping waste heat of the drive motor 1 over the outer surfaces of the motor casing 30.
  • the refrigerant suction flow K is sent to the suction side of the compressor 2 via the discharge line 39 passed, there compacted in the manner described above and then fed back to the heat exchanger.
  • Suction inlet 38 directly to the suction line 37 leading and thus the gap 35 bypassing line 40 provided which is opened or closed depending on the temperature.
  • Leakage flow L consists of refrigerant and oil
  • a drain line 41 a is guided, which opens at the ümfangsseite of the motor housing 30 in the gap 35 near the suction outlet 36 of the motor housing shell 33.
  • About the drain line 41a passes into the sealing chamber 31 reaching refrigerant and is taken from the flowing through the gap 35 refrigerant suction flow K before it enters the engine compartment 30 enclosed by the engine compartment.
  • a bypass line 43 is also provided in the compressor unit V2 shown in FIG. 2, but in this case it is integrated in the motor housing shell 33. Through a valve combination 44, the flow through the gap 35 or the bypass line 43 of the respective
  • Ambient temperature load to be regulated accordingly.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

La présente invention concerne une unité compresseur permettant de comprimer un liquide de refroidissement et comprenant un moteur d'entraînement électrique qui présente un carter (30) enfermant hermétiquement le moteur d'entraînement (1) vis-à-bis de l'environnement (U), et un compresseur (2) qui est entraîné par le moteur d'entraînement (1) et qui assure la compression d'un liquide de refroidissement aspiré par le compresseur (2) sous la forme d'un flux de liquide de refroidissement d'aspiration (K), et un véhicule utilitaire équipé d'une telle machine de refroidissement comportant une telle unité compresseur. L'unité compresseur selon l'invention permet avec des moyens simples et même en fonctionnement à des températures ambiantes extrêmes de garantir le respect des températures de fonctionnement optimales. Le véhicule utilitaire selon l'invention garantit une grande sûreté de fonctionnement même à des températures ambiantes élevées. A cet effet, au moins une section du carter (30) du moteur d'entraînement (1) est aspergée au moins par intermittence d'un flux partiel du flux de liquide de refroidissement d'aspiration (K).
EP13811863.3A 2012-12-13 2013-12-13 Unité compresseur et véhicule utilitaire équipé d'une machine de refroidissement comportant une telle unité compresseur Withdrawn EP2932169A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012024362.6A DE102012024362A1 (de) 2012-12-13 2012-12-13 Verdichter
PCT/EP2013/076612 WO2014091018A1 (fr) 2012-12-13 2013-12-13 Unité compresseur et véhicule utilitaire équipé d'une machine de refroidissement comportant une telle unité compresseur

Publications (1)

Publication Number Publication Date
EP2932169A1 true EP2932169A1 (fr) 2015-10-21

Family

ID=49880718

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13811863.3A Withdrawn EP2932169A1 (fr) 2012-12-13 2013-12-13 Unité compresseur et véhicule utilitaire équipé d'une machine de refroidissement comportant une telle unité compresseur

Country Status (3)

Country Link
EP (1) EP2932169A1 (fr)
DE (1) DE102012024362A1 (fr)
WO (1) WO2014091018A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3456563A1 (fr) 2017-09-15 2019-03-20 Schmitz Cargobull AG Unité de réfrigération de transport et son procédé de fonctionnement
JP7470956B2 (ja) 2019-09-27 2024-04-19 株式会社中央技研工業 コンプレッサ
EP4197834B1 (fr) * 2021-12-20 2024-05-08 Schmitz Cargobull AG Machine à réfrigérer de transport, coffre et procédé de fonctionnement d'une machine à réfrigérer de transport

Citations (4)

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Publication number Priority date Publication date Assignee Title
FR1300580A (fr) * 1961-09-15 1962-08-03 Brown Machine frigorifique et en particulier compresseur à moteur
US3859815A (en) * 1973-10-12 1975-01-14 Maekawa Seisakusho Kk Two-stage compression apparatus
EP1273468A1 (fr) * 2001-02-13 2003-01-08 Sanyo Electric Co., Ltd. Systeme de climatisation pour automobile
DE102010026648A1 (de) * 2010-07-09 2012-01-12 Gea Grasso Gmbh Kälteanlage zur Kühlung eines Conainers

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US2864551A (en) * 1957-01-30 1958-12-16 Gen Motors Corp Refrigerating apparatus
US4573324A (en) * 1985-03-04 1986-03-04 American Standard Inc. Compressor motor housing as an economizer and motor cooler in a refrigeration system
US6584784B2 (en) * 1999-02-05 2003-07-01 Midwest Research Institute Combined refrigeration system with a liquid pre-cooling heat exchanger
GB9908675D0 (en) 1999-04-15 1999-06-09 British Broadcasting Corp Diversity reception method and diversity receivers
US6223546B1 (en) 1999-04-21 2001-05-01 Robert A. Chopko Electrically powered transport refrigeration unit
JP2001200785A (ja) * 2000-01-18 2001-07-27 Toyota Autom Loom Works Ltd 電動斜板圧縮機
JP2004183605A (ja) * 2002-12-05 2004-07-02 Sanden Corp 電動圧縮機
WO2006011248A1 (fr) * 2004-07-30 2006-02-02 Mitsubishi Heavy Industries, Ltd. Appareil de refroidissement par réfrigération de l’air et système de froid connexe par réfrigération de l’air
DE102010022993B4 (de) 2010-06-08 2021-07-01 Schmitz Cargobull Aktiengesellschaft Transportkältemaschine zum Kühlen des Innenraums

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1300580A (fr) * 1961-09-15 1962-08-03 Brown Machine frigorifique et en particulier compresseur à moteur
US3859815A (en) * 1973-10-12 1975-01-14 Maekawa Seisakusho Kk Two-stage compression apparatus
EP1273468A1 (fr) * 2001-02-13 2003-01-08 Sanyo Electric Co., Ltd. Systeme de climatisation pour automobile
DE102010026648A1 (de) * 2010-07-09 2012-01-12 Gea Grasso Gmbh Kälteanlage zur Kühlung eines Conainers

Non-Patent Citations (1)

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Title
See also references of WO2014091018A1 *

Also Published As

Publication number Publication date
WO2014091018A1 (fr) 2014-06-19
DE102012024362A1 (de) 2014-06-18

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