EP4088030A1 - Compresseur à spirale - Google Patents

Compresseur à spirale

Info

Publication number
EP4088030A1
EP4088030A1 EP20700566.1A EP20700566A EP4088030A1 EP 4088030 A1 EP4088030 A1 EP 4088030A1 EP 20700566 A EP20700566 A EP 20700566A EP 4088030 A1 EP4088030 A1 EP 4088030A1
Authority
EP
European Patent Office
Prior art keywords
pressure chamber
oil return
channel
gas connection
oil
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
EP20700566.1A
Other languages
German (de)
English (en)
Other versions
EP4088030B1 (fr
Inventor
Lukas LÖHMER
Phillip BARTH
Jan BERWANGER
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.)
Pierburg GmbH
Original Assignee
Pierburg 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 Pierburg GmbH filed Critical Pierburg GmbH
Publication of EP4088030A1 publication Critical patent/EP4088030A1/fr
Application granted granted Critical
Publication of EP4088030B1 publication Critical patent/EP4088030B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow

Definitions

  • the invention relates to a scroll compressor with a compressor housing, a high pressure chamber, a low pressure chamber which is fluidically connected to the high pressure chamber via an oil return channel, an oil return throttle being provided in the oil return channel, an orbiting displacement spiral which is arranged on a driven eccentric unit and which converts into a fixed scroll engages, a sliding disk being arranged between the orbiting displacement scroll and the compressor housing, and a counter-pressure chamber adjoining the displacement scroll, which is fluidically connected to the high-pressure chamber via a gas connection channel, a gas connection throttle being provided in the gas connection channel.
  • Such scroll compressors are sufficiently known from the prior art, for example from EP 3 404 264 A1, and comprise a high-pressure chamber, a low-pressure chamber and an orbiting chamber
  • Displacement spiral and a fixed spiral that interacts with the displacement spiral Displacement spiral and a fixed spiral that interacts with the displacement spiral.
  • a sliding disk is arranged between the orbiting displacement spiral and a compressor housing.
  • the orbiting displacement scroll engages in the fixed scroll in such a way that compression chambers are formed between the displacement scroll and the fixed scroll which receive a working fluid.
  • a counter-pressure chamber is provided between the compressor housing and the displacement spiral. The pressure prevailing in the counter-pressure chamber and acting on the displacement spiral causes a resulting force in the axial direction, which causes the displacement spiral is pressed against the fixed spiral and thus the spirals are sealed to one another.
  • the pressure prevailing in the back pressure chamber is built up by a fluidic connection between the back pressure chamber and the high pressure chamber, the fluid under high pressure flowing into the back pressure chamber via a gas connection channel connecting the high pressure chamber with the back pressure chamber.
  • a gas connection throttle which controls the mass flow of the fluid flowing into the counter-pressure chamber, is arranged in the gas connection channel.
  • a disadvantage of such a gas connection throttle is that it is formed by a separate component, the provision of such a separate gas connection throttle increasing both the manufacturing and the assembly costs of the scroll compressor.
  • the scroll compressor comprises an oil return channel which fluidly connects the high pressure chamber with the low pressure chamber.
  • An oil provided for lubricating the components in the scroll compressor is separated from the compressed fluid via a separator located in the high pressure chamber and returned to the low pressure chamber via the oil return channel so that the returned oil can be used again to lubricate the components.
  • an oil return throttle is arranged in the oil return channel.
  • the oil return throttle is formed by a separate component, which is produced by an additional manufacturing process and has to be installed in the oil return duct during assembly, which increases the manufacturing and assembly costs of the scroll compressor.
  • the object is therefore to provide a scroll compressor which has reduced manufacturing and assembly costs. This object is achieved by a scroll compressor with the features of main claim 1.
  • the sliding disk having the oil return throttle and / or the gas connection throttle, simplifies the manufacture and assembly of the scroll compressor and thereby reduces the manufacturing and assembly costs.
  • the sliding disk takes on the throttle function in the oil return duct and / or in the gas connection duct, the oil return throttle or the gas connection throttle being implemented through a simple and inexpensive opening in the sliding disk and no additional components for the implementation of the oil return throttle and / or the Gas connection throttles are required.
  • the sliding disk thus reduces the sliding friction between the orbiting displacement spiral and the compressor housing and throttles the fluid flowing into the counter-pressure chamber and / or the oil flowing back into the low-pressure chamber.
  • the oil return throttle or the gas connection throttle is preferably an opening provided on the sliding washer, the opening having a smaller diameter than the oil return channel or the gas connection channel.
  • the sliding disk can be equipped with the oil return throttle and / or the gas connection throttle in a simple and inexpensive manner, with such a throttle being able to be produced by a simple and inexpensive manufacturing process, for example by means of a laser.
  • the oil return channel and / or the gas connection channel preferably extend at least in sections through the fixed spiral.
  • the gas connection channel extends from the high pressure chamber via a gas channel in the fixed scroll, through the sliding disk and via a gas channel in the compressor housing to the counter-pressure chamber.
  • the oil return duct extends from the high pressure chamber via an oil duct in the fixed scroll, through the sliding disk and via an oil duct in the compressor housing to the low pressure chamber.
  • Adjacent high pressure chamber, the oil return channel and / or the gas connection channel can be started directly from the
  • High pressure chamber to be passed to the back pressure chamber or the low pressure chamber.
  • the high-pressure chamber preferably has an oil separation chamber in which an oil separator is arranged, an inlet of the oil return channel being arranged at the lowest point of the oil separation chamber.
  • the oil separator separates the oil dissolved in the gas, the oil-free gas rising and flowing through an outlet into a cooling circuit.
  • the separated oil sinks to the bottom of the oil separation chamber and flows back into the low-pressure chamber via the oil return duct.
  • the oil can be used to lubricate the components of the scroll compressor.
  • An inlet of the gas connection channel is preferably arranged upstream of the oil separator in the direction of flow of the gas-oil mixture.
  • the gas with the oil dissolved therein is conveyed into the counter-pressure chamber, whereby the components adjoining the counter-pressure chamber, in particular bearing elements, through the oil be lubricated.
  • the inlet of the gas connection channel can be arranged after the oil separator in the direction of flow of the gas-oil mixture.
  • a filter is provided in the oil return channel and / or gas connection channel.
  • the returning oil and / or the gas flowing into the counter-pressure chamber can contain particles which, for example, arise as a result of wear of the components moving relative to one another.
  • the particles can lead to clogging of the oil return throttle or the gas connection throttle or to abrasive wear of the components moving relative to one another.
  • the filter can be used to filter out the particles from the oil or the gas and prevent clogging of the oil return channel or the gas connection channel and the abrasive wear of the components moving relative to one another.
  • the displacement spiral preferably has a circumferential groove on the side facing the sliding disk, in which a sliding ring is arranged, the sliding ring resting against the sliding disk.
  • the sliding disk is positively connected to the drive housing perpendicular to a longitudinal axis.
  • the compressor housing has at least one fixing bolt and the sliding disk has a fixing opening corresponding to the fixing bolt. Rotation and radial displacement of the sliding disk can be reliably prevented by the fixing bolt.
  • the fixing bolt can be a separate component pressed into an opening in the compressor housing, or it can be produced in one piece with the compressor housing.
  • the sliding disk preferably has at least one guide opening through which a guide pin, which is fastened to the compressor housing and guiding the orbiting displacement spiral, extends.
  • the guide pin engages eccentrically in an opening of the displacement spiral, whereby the displacement spiral is guided by the guide pin during the orbiting movement, a rotational movement of the displacement spiral being prevented by the guide pin.
  • the oil return throttle and / or the gas connection throttle preferably has a diameter which is many times smaller than the diameter of the fixing bolt or the guide pin. The oil or gas mass flow can be controlled by the size of the diameter of the oil return throttle and / or the gas connection throttle.
  • the orbiting displacement spiral is on the
  • Eccentric unit connected to a rotor shaft of a rotor of an electric motor, the electric motor being arranged in the low-pressure chamber.
  • the arrangement of the electric motor in the low-pressure chamber cools the electric motor and thereby increases the service life of the scroll compressor.
  • a scroll compressor for an air conditioning system of a motor vehicle which has a gas connection channel extending from the high pressure chamber to the counter pressure chamber and / or an oil return channel extending from the high pressure chamber to the low pressure chamber, a gas connection channel arranged in the gas connection channel and / or an oil return channel arranged in the oil return channel. Throttle is provided in a simple and inexpensive way by the sliding disk and thereby the assembly and manufacturing costs of the scroll compressor can be reduced.
  • An embodiment of a scroll compressor according to the invention is shown in the figure and described below.
  • Figure 1 shows a sectional view of a scroll compressor according to the invention
  • FIG. 2 shows a plan view of a sliding disk of the scroll compressor from FIG. 1.
  • the scroll compressor 2 comprises a multi-part compressor housing 10 with a first compressor housing part 12, a second compressor housing part 14 axially adjoining the first compressor housing part 12 and a third compressor housing part 16 adjoining the second compressor housing part 14.
  • the first compressor housing part 12, the second compressor housing part 14 and the third compressor housing part 16 delimit an engine compartment 18.
  • the second compressor housing part 14 and the third compressor housing part 16 delimit a compressor space 20.
  • An electric motor 22 with a stator 24 and a rotor 26 is arranged in the engine compartment 18.
  • the rotor 26 is fastened on a rotor shaft 28.
  • the rotor shaft 28 extends from the engine compartment 18 through a central opening 29 of the second compressor housing part 14 into the compressor compartment 20.
  • the rotor shaft 28 is mounted in two shaft bearings 40, 42 via two end-side shaft bearing sections 30, 34 so that it can rotate about a rotor shaft rotation axis.
  • the first shaft bearing 40 is arranged in the engine compartment 18 and supports the first shaft bearing section 30.
  • the second shaft bearing 42 is arranged in the compressor chamber 20 and supports the second shaft bearing section 34.
  • a shaft sealing ring 43 is provided on the side of the second shaft bearing 42 facing the engine compartment 18 , which rests against the rotor shaft 28 on the radially inner side and is supported on the radially outer side by the second compressor housing part 14.
  • the shaft sealing ring 43 fluidically seals the engine compartment 18 from a counter-pressure chamber 82 of the compressor compartment 20.
  • a compressor unit 58 which has an orbiting displacement spiral 60 and a stationary spiral 62, is arranged in the compression chamber 20.
  • the orbiting displacement scroll 60 is about a
  • Eccentric shaft bearing 64 is arranged on an eccentric unit 50 which is fastened to the rotor shaft 28 and lies via a sliding washer 70 on a surface of the second facing the compressor chamber 20
  • Compressor housing part 14 the displacement spiral 60 having a sliding ring 142 arranged in a circumferential groove 140 on the side facing the sliding disk 70.
  • the fixed scroll 62 is fixedly arranged in the compressor housing 10, the fixed scroll 62 being axially supported by the second compressor housing part 14 and the third compressor housing part 16.
  • a refrigerant is introduced through a compressor inlet 85 into the engine compartment 18 of the scroll compressor 2, the refrigerant flowing through the engine compartment 18 into the compressor compartment 20.
  • the orbiting displacement spiral 60 and the stationary spiral 62 are designed in such a way that they delimit a compression chamber 63 and, through the orbiting movement of the displacement spiral 60, convey a refrigerant from a radially outer inlet 66 of the compression chamber 63 to a radially inner outlet 68 of the compression chamber 63 and thereby is compressed.
  • the compression chamber 20 has a high pressure chamber 80 and a counter pressure chamber 82.
  • the high-pressure chamber 80 is delimited by the third compressor housing part 16 and by the stationary spiral 62 and is fluidly arranged between the outlet 68 and a compressor outlet 84, the refrigerant flowing from the outlet 68 via the high-pressure chamber 80 to the compressor outlet 84.
  • the high-pressure chamber 80 has an oil separation chamber 86 which is fluidly arranged directly in front of the compressor outlet 84 and which has an oil separator 88.
  • the oil separator 88 is designed as a cyclone separator, the refrigerant flowing through the oil separator 88 to the compressor outlet 84 and the oil released from the refrigerant settling on the bottom of the oil separating chamber 86, ie at the lowest point of the oil separating chamber 86.
  • an inlet 89 of an oil return duct 90 is provided at the bottom of the oil separation chamber 86, which fluidly connects the oil separation chamber 86 and thus the high pressure chamber 80 with a low pressure chamber 87, the engine compartment 18 forming the low pressure chamber 87.
  • the oil return duct 90 extends through the third compressor housing part 16, the fixed spiral 62 and through the second compressor housing part 14, a filter 130 being arranged in the oil return duct 90.
  • the back pressure chamber 82 is delimited by the second compressor housing part 14 and the orbiting displacement scroll 60, the pressure prevailing in the back pressure chamber 82 acting on the axially displaceable, orbiting displacement scroll 60 and resulting in an axial load on the displacement scroll.
  • This axial load leads to an improved seal between the end faces of the orbiting displacement scroll 60 and the stationary scroll 62.
  • the counterpressure chamber 82 is connected to the via a gas connection channel 100 High pressure chamber 80 fluidically connected.
  • the gas connection channel 100 runs from the high-pressure chamber 80 through the fixed spiral 62 and through the second compressor housing part 14.
  • a gas connection throttle is arranged in the gas connection channel 100, which controls the mass flow of the gas flowing into the counter-pressure chamber 82.
  • the oil return duct 90 and the gas connection duct 100 run through the sliding disk 70 arranged between the second compressor housing part 14 and the fixed scroll 62, the sliding disk 70, which is shown in FIG. 2, having an oil return throttle 92 and a gas connection throttle 96.
  • the sliding disk 70 has a first bore 94 in its radially outer region and a second bore 98 spaced apart from the first bore 94 in the circumferential direction.
  • the first bore 94 has a smaller diameter than the rest of the course of the oil return line 90, so that the first bore 94 forms the oil return throttle 92.
  • the second bore 98 has a smaller diameter than the rest of the course of the gas connection line 100, so that the second bore 98 forms the gas connection throttle 96.
  • the sliding disk 70 has two fixing openings 102, 104 in the radially outer area and six guide openings 110, 112, 114, 116, 118, 120 in the radially inner area, the fixing openings 102, 104 and the guide openings 110, 112, 114, 116, 118, 120 have a significantly larger diameter than the bores 94, 98.
  • a fixing bolt 103 fastened to the second compressor housing part 14 engages in each of the two fixing openings 102, 104 a, whereby the sliding disk 70 is fixed perpendicular to a longitudinal axis 106 of the scroll compressor 2.
  • the six guide openings 110, 112, 114, 116, 118, 120 penetrate each one on the second
  • Guide pin 122 fastened to the compressor housing part 14, the guide pins 122 engaging eccentrically in a respective guide bores 124 provided on the displacement spiral 60.
  • the guide bores 124 have a larger diameter than the guide pins 122, the guide pins 122 sliding on the respective inner circumferential surface of the guide bore 124 during the orbiting movement of the displacement spiral 60.
  • a slide bearing sleeve 126 is arranged in each of the guide bores 124.
  • a scroll compressor 2 is thus created which can be manufactured with reduced manufacturing and assembly costs, the oil return throttle 92 and the gas connection throttle 96 being provided in a simple and inexpensive manner by the sliding disk 70 and no additional components and associated manufacturing and assembly steps are required.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne un compresseur à spirale comprenant un boîtier (10) ; une chambre haute pression (80) ; une chambre basse pression (87) qui est reliée en terme de circulation des fluides par un canal de recirculation d'huile (90) à la chambre haute pression (80), le canal de recirculation d'huile (90) présentant un étranglement de recirculation d'huile (92) ; une spirale mobile (60) à mouvement orbital qui est disposée au niveau d'une unité excentrique (50) entraînée et qui vient en prise dans une spirale fixe (62), un disque coulissant (70) étant agencé entre la spirale mobile (60) à mouvement orbital et le boîtier (10) du compresseur ; et une chambre de contre-pression (82) qui est adjacente à la spirale mobile (60) et qui est reliée en termes de circulation des fluides à la chambre haute pression (80) par un canal de liaison gazeuse (100), le canal de liaison gazeuse (100) présentant un étranglement de liaison gazeuse (96). Afin de réduire la complexité de montage et de réalisation du compresseur à spirale, le canal de recirculation d'huile (90) et/ou le canal de liaison gazeuse (100) traverse le disque coulissant (70), le disque coulissant (70) présentant l'étranglement de recirculation d'huile 892) et/ou l'étranglement de liaison gazeuse (96).
EP20700566.1A 2020-01-09 2020-01-09 Compresseur à spirales Active EP4088030B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2020/050435 WO2021139890A1 (fr) 2020-01-09 2020-01-09 Compresseur à spirale

Publications (2)

Publication Number Publication Date
EP4088030A1 true EP4088030A1 (fr) 2022-11-16
EP4088030B1 EP4088030B1 (fr) 2024-03-06

Family

ID=69159774

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20700566.1A Active EP4088030B1 (fr) 2020-01-09 2020-01-09 Compresseur à spirales

Country Status (3)

Country Link
US (1) US11965506B2 (fr)
EP (1) EP4088030B1 (fr)
WO (1) WO2021139890A1 (fr)

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7101160B2 (en) * 2003-03-31 2006-09-05 Kabushiki Kaisha Toyota Jidoshokki Electric compressor
JP5637151B2 (ja) * 2012-01-20 2014-12-10 株式会社豊田自動織機 差圧弁及び差圧弁を備える電動圧縮機
JP6135126B2 (ja) 2012-12-26 2017-05-31 株式会社豊田自動織機 スクロール型圧縮機
KR101642178B1 (ko) * 2013-07-02 2016-07-25 한온시스템 주식회사 스크롤 압축기
DE102017105175B3 (de) * 2017-03-10 2018-08-23 OET GmbH Verdrängermaschine nach dem Spiralprinzip, Verfahren zum Betreiben einer Verdrängermaschine, Verdrängerspirale, Fahrzeugklimaanlage und Fahrzeug
DE102017110913B3 (de) 2017-05-19 2018-08-23 OET GmbH Verdrängermaschine nach dem Spiralprinzip, Verfahren zum Betreiben einer Verdrängermaschine, Fahrzeugklimaanlage und Fahrzeug

Also Published As

Publication number Publication date
US20230349379A1 (en) 2023-11-02
EP4088030B1 (fr) 2024-03-06
WO2021139890A1 (fr) 2021-07-15
US11965506B2 (en) 2024-04-23

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