[go: up one dir, main page]

WO2021260759A1 - Compresseur rotatif - Google Patents

Compresseur rotatif Download PDF

Info

Publication number
WO2021260759A1
WO2021260759A1 PCT/JP2020/024342 JP2020024342W WO2021260759A1 WO 2021260759 A1 WO2021260759 A1 WO 2021260759A1 JP 2020024342 W JP2020024342 W JP 2020024342W WO 2021260759 A1 WO2021260759 A1 WO 2021260759A1
Authority
WO
WIPO (PCT)
Prior art keywords
vane
groove
rotary compressor
end portion
chamber
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.)
Ceased
Application number
PCT/JP2020/024342
Other languages
English (en)
Japanese (ja)
Inventor
博之 山田
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2022531252A priority Critical patent/JP7313560B2/ja
Priority to PCT/JP2020/024342 priority patent/WO2021260759A1/fr
Priority to CN202080102123.XA priority patent/CN115698508B/zh
Publication of WO2021260759A1 publication Critical patent/WO2021260759A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member

Definitions

  • the present disclosure relates to a rotary compressor in which a cylinder chamber formed in a cylinder is divided into a suction chamber and a compression chamber by a vane.
  • the compression mechanism of the rotary compressor includes a cylinder, a rolling piston, a vane, and a spring.
  • a cylinder chamber having a substantially cylindrical shape is formed in the cylinder. Further, the cylinder is formed with a vane groove in which one end communicates with the cylinder chamber and the other end communicates with the spring storage chamber in which the spring is stored.
  • the rolling piston is housed in the cylinder chamber of the cylinder. Further, the rolling piston is attached to the eccentric portion of the drive shaft. Therefore, when the drive shaft rotates, the rolling piston eccentrically rotates in the cylinder chamber.
  • the vane is slidably held in the vane groove of the cylinder. Further, the first end portion of the vane is in contact with the outer peripheral surface of the rolling piston. In addition, the vane slides in the vane groove following the rolling piston that rotates eccentrically in the cylinder chamber, and the first end of the vane is prevented from separating from the outer peripheral surface of the rolling piston. The second end, which is the end opposite to the portion, is pushed toward the rolling piston by a spring.
  • the cylinder chamber is divided into a suction chamber and a compression chamber by a vane. In other words, the space surrounded by the inner peripheral surface of the cylinder chamber and the outer peripheral surface of the rolling piston is divided into a suction chamber and a compression chamber by a vane. Then, the rolling piston moves eccentrically in the cylinder chamber due to the rotation of the drive shaft, so that the rotary compressor simultaneously sucks the refrigerant into the suction chamber and compresses the refrigerant in the compression chamber.
  • the vane when the rolling piston approaches the vane groove, the vane is pushed by the rolling piston and is stored in the vane groove while sliding in the vane groove. Therefore, when the vane is retracted into the cylinder chamber, the first end portion of the vane does not separate from the outer peripheral surface of the rolling piston.
  • Patent Document 1 a conventional rotary compressor has been proposed in which the frictional force between the vane and the vane groove is reduced. Specifically, in the rotary compressor described in Patent Document 1, a fine recess is formed in the sliding surface of the vane with the vane groove or the sliding surface of the vane with the vane, and the vane and the vane groove are formed. We are trying to reduce the frictional force between them.
  • metal powder is generated due to friction between the vanes and the vane grooves. Further, in the rotary compressor, a sliding portion is present at a position other than between the vane and the vane groove. When a rotary compressor is used, metal powder is also generated from sliding portions other than between the vane and the vane groove. Further, in the rotary compressor, a product is also generated by the reaction between the refrigerant and the refrigerating machine oil. For this reason, in a conventional rotary compressor that reduces the frictional force between the vane and the vane groove, if the rotary compressor is used for a long period of time, the above-mentioned metal powder and products will be vanes and vanes.
  • the vane protrudes into the cylinder chamber on at least one of the surface facing the vane groove in the vane and the surface facing the vane in the vane groove.
  • At least one first groove is formed in which the internal pressure increases when advancing, and at least one second groove is formed in which one end communicates with the first groove and the other end communicates with the spring storage chamber.
  • FIG. 3 is a cross-sectional view taken along the line AA of FIG. It is a figure for demonstrating the operation at the time of advancing the vane of the rotary compressor which concerns on Embodiment 1. It is a figure for demonstrating the operation at the time of retreating of the vane of the rotary compressor which concerns on Embodiment 1. It is a top view for demonstrating the compression mechanism part of the rotary compressor which concerns on Embodiment 2.
  • FIG. 20 is a sectional view taken along the line CC of FIG. It is a figure which observed another example of the vane of the rotary compressor which concerns on Embodiment 5 from the 1st side.
  • the electric motor 10 includes a stator 11 fixed to the closed container 1 and a rotor 12 that is rotated by the magnetic force generated by the stator 11.
  • the facing surface on the compression chamber 24 side is referred to as the first side surface 43.
  • the surface facing the suction chamber 23 is referred to as the second side surface 44. That is, the first side surface 43 and the second side surface 44 are facing surfaces of the vane 40 with the vane groove 27.
  • the facing surface on the compression chamber 24 side is designated as the first wall surface 28.
  • the surface facing the suction chamber 23 is referred to as a second wall surface 29. That is, the first wall surface 28 and the second wall surface 29 are facing surfaces of the vane groove 27 with the vane 40.
  • the surface facing the vane groove in the vane is a flat surface. Further, in the conventional general rotary compressor, the surface facing the vane in the vane groove is also a flat surface.
  • vane separation may occur in which the outer peripheral surface of the rolling piston is separated from the outer peripheral surface. Specifically, when the vane retracts, the vane is pushed by the rolling piston 30, so that vane separation does not occur.
  • the vane moves forward due to the pressing force of the spring, if the frictional force between the vane and the vane groove is large, the vane cannot follow the rolling piston and vane separation occurs.
  • the vane 40 is configured as follows in order to suppress the occurrence of vane separation when the vane 40 is advanced.
  • the refrigerating machine oil is supplied between the vane 40 and the vane groove 27 while the rotary compressor 100 is being driven.
  • the refrigerating machine oil supplied between the vane 40 and the vane groove 27 moves together with the vane 40 due to the viscosity of the refrigerating machine oil. Therefore, as shown in FIG. 5, when the vane 40 is advanced, the refrigerating machine oil flows from the end portion 51c toward the top portion 51b in the convex portion 51a of the first groove 51.
  • the refrigerating machine oil flowing through the two grooves forming the convex portion 51a joins at the top portion 51b, and the pressure at the position of the top portion 51b increases.
  • the shape is such that it protrudes from the portion 42 toward the first end portion 41.
  • the first groove 51 and the second groove 52 may be formed on both the surface of the vane 40 facing the vane groove 27 and the surface of the vane groove 27 facing the vane 40. That is, if the first groove 51 and the second groove 52 are formed on at least one of the surface facing the vane groove 27 in the vane 40 and the surface facing the vane 40 in the vane groove 27, the vane is separated for a long period of time. Can be suppressed.
  • the rotary compressor 100 includes a cylinder 21, a rolling piston 30, a vane 40, and a spring 34.
  • a cylinder chamber 22 is formed in the cylinder 21.
  • the rolling piston 30 is housed in the cylinder chamber 22 and eccentrically rotates in the cylinder chamber 22.
  • the vane 40 the first end 41 is in contact with the outer peripheral surface of the rolling piston 30, and the cylinder chamber 22 is divided into a suction chamber 23 and a compression chamber 24.
  • the spring 34 is housed in the spring storage chamber 33 and pushes the second end 42, which is the end of the vane 40 opposite to the first end 41, toward the rolling piston 30.
  • the gap between the first side surface 43 of the vane 40 and the first wall surface 28 of the vane groove 27 is smaller on the spring storage chamber 33 side and larger on the cylinder chamber 22 side.
  • the gap between the first side surface 43 of the vane 40 and the first wall surface 28 of the vane groove 27 is smaller on the second end 42 side and larger on the first end 41 side. Therefore, the first side surface 43 of the vane 40 easily comes into contact with the end portion 28a on the first wall surface 28 of the vane groove 27 on the spring storage chamber 33 side.
  • the gap between the second side surface 44 of the vane 40 and the second wall surface 29 of the vane groove 27 is smaller on the cylinder chamber 22 side and larger on the spring storage chamber 33 side.
  • FIG. 9 is a view of the vane of the rotary compressor according to the second embodiment observed from the first side surface.
  • FIG. 10 is a view of the vane of the rotary compressor according to the second embodiment observed from the second side surface.
  • the gap between the first side surface 43 of the vane 40 and the first wall surface 28 of the vane groove 27 is the gap between the second side surface 44 of the vane 40 and the second wall surface 29 of the vane groove 27.
  • the second end 42 side becomes smaller.
  • the gap between the second side surface 44 of the vane 40 and the second wall surface 29 of the vane groove 27 is the first as compared with the space between the first side surface 43 of the vane 40 and the first wall surface 28 of the vane groove 27.
  • the end 41 side becomes smaller.
  • the distance between the first groove 51 formed on the second end portion 42 side of the first side surface 43 of the vane 40 and the second end portion 42 is the second most on the second side surface 44 of the vane 40. It is shorter than the distance between the first groove 51 formed on the end portion 42 side and the second end portion 42. Further, the distance between the first groove 51 formed on the first end portion 41 side of the first side surface 43 of the vane 40 and the first end portion 41 is the most first end portion on the second side surface 44 of the vane 40. It is longer than the distance between the first groove 51 formed on the 41 side and the first end portion 41.
  • FIG. 11 is a plan view showing an example of a vane of the rotary compressor according to the second embodiment.
  • the first side surface 43 of the vane 40 is most likely to come into contact with the end portion 28a on the first wall surface 28 of the vane groove 27 on the spring storage chamber 33 side. Become. Therefore, it is preferable that the first groove 51 is formed on the first side surface 43 of the vane 40 in a range facing the end 28a when the vane 40 slides in the vane groove 27.
  • the second side surface 44 of the vane 40 is most likely to come into contact with the end portion 29a on the cylinder chamber 22 side of the second wall surface 29 of the vane groove 27. Therefore, it is preferable that the first groove 51 is formed on the second side surface 44 of the vane 40 in a range facing the end portion 29a when the vane 40 slides in the vane groove 27.
  • the point on the side of the first end 41 is set as the starting point lgd1.
  • the point on the second end 42 side is defined as the end point lgd2.
  • the formation range of the first groove 51 on the second side surface 44 of the vane 40 is defined as lgs.
  • the point on the side of the first end 41 is set as the starting point lgs1.
  • the point on the second end 42 side is defined as the end point lgs2.
  • the first side surface 43 of the vane 40 advances from the first end 41 to the second end 42 along the X direction by the vane groove length lvgd. At the position, it faces the end 28a of the vane groove 27. Therefore, the starting point lgd1 of the formation range lgd of the first groove 51 on the first side surface 43 of the vane 40 is a position advanced from the first end portion 41 along the X direction by the vane groove length lvgd to the second end portion 42. Is preferable. Further, as shown in FIG.
  • the end portion 28a By forming the first groove 51 in such a formation range lgd on the first side surface 43 of the vane 40, the end portion 28a most likely to come into contact with the first side surface 43 of the vane 40 when the vane 40 slides is the vane 40. Contact with the first side surface 43 of the above can be further suppressed. Therefore, the frictional force between the vane 40 and the vane groove 27 can be further reduced.
  • the second side surface 44 of the vane 40 faces the end portion 29a of the vane groove 27 at the position of the first end portion 41. Therefore, it is preferable that the start point lgs1 of the formation range lgs of the first groove 51 on the second side surface 44 of the vane 40 is the position of the first end portion 41. Further, as shown in FIG. 7, in the state where the vane 40 is most advanced, the vane 40 is tilted with respect to the vane groove 27, but the second side surface 44 of the vane 40 is roughly in the X direction from the start point lgs1.
  • the end point lgs2 of the formation range lgs of the first groove 51 on the second side surface 44 of the vane 40 is a position advanced from the start point lgs1 along the X direction by the stroke amount Xst to the second end portion 42. ..
  • the first groove 51 and the second groove 52 may be formed on the first wall surface 28 and the second wall surface 29 which are the facing surfaces of the vane groove 27 with the vane 40. ..
  • the first groove 51 is formed at the following position. Specifically, the distance between the first groove 51 formed on the second end portion 42 side of the first wall surface 28 and the second end portion 42 is set on the second end portion 42 side of the second wall surface 29. It is shorter than the distance between the formed first groove 51 and the second end portion 42. Further, the distance between the first groove 51 formed on the first end portion 41 side of the first wall surface 28 and the first end portion 41 is formed on the first end portion 41 side of the second wall surface 29. It is longer than the distance between the first groove 51 and the first end 41.
  • Embodiment 3 By setting the depth of the second groove 52 as in the third embodiment, it becomes easier to discharge the metal powder and the product that have entered between the vane 40 and the vane groove 27, and the vane separation can be performed for a longer period of time. It can be suppressed.
  • the items not specifically described are the same as those of the first embodiment or the second embodiment, and the same functions and configurations as those of the first embodiment or the second embodiment are the same as those of the first embodiment or the second embodiment. It will be described using the same reference numerals as those in the second embodiment.
  • FIG. 12 is a view of the vane of the rotary compressor according to the third embodiment observed from the first side surface.
  • FIG. 13 is a cross-sectional view taken along the line BB of FIG. As shown in FIGS. 12 and 13, in the third embodiment, the depth of the second groove 52 is deeper than the depth of the first groove 51.
  • the average flow velocity of the fluid is 1/2 of the slip velocity. Therefore, the flow rate of the fluid flowing between the two planes is the product of the average flow velocity and the cross-sectional area. That is, by increasing the depth of the second groove 52, the flow rate of the refrigerating machine oil in the second groove 52 increases. Further, due to the increase in the flow rate of the refrigerating machine oil in the second groove 52, the inflow amount of the refrigerating machine oil from the first groove 51 to the second groove 52 also increases when the vane 40 retracts, and the refrigerating machine oil in the first groove 51 The flow velocity of is also increased. Therefore, by increasing the depth of the second groove 52, the metal powder and the product that have entered between the vane 40 and the vane groove 27 can be more easily discharged.
  • the convex portion 51a of the first groove 51 has a shape in which two linear grooves are communicated with each other at the top portion 51b.
  • a shape of the convex portion 51a is merely an example.
  • the convex portion 51a can have various shapes as long as the refrigerating machine oil flows toward the top 51b when the vane 40 advances.
  • some examples of the shape of the convex portion 51a will be introduced.
  • the shape of the second groove 52 shown in the first to third embodiments is only an example.
  • the second groove 52 can have various shapes as long as it communicates with the first groove 51 and the spring storage chamber 33. In the fourth embodiment, some examples of the shape of the second groove 52 will be introduced.
  • the items not specifically described are the same as those of the first to the third embodiments, and the same functions and configurations as those of the first to third embodiments are carried out. It will be described using the same reference numerals as any of the first to third embodiments of the above.
  • FIG. 14 is a view of an example of the vane of the rotary compressor according to the fourth embodiment observed from the first side surface. As shown in FIG. 14, at least a part of the convex portion 51a of the first groove 51 may be a curved groove. Note that FIG. 14 shows an example in which all of the convex portions 51a of the first groove 51 are composed of curved grooves.
  • FIG. 15 is a view of an example of the vane of the rotary compressor according to the fourth embodiment observed from the first side surface.
  • the curved groove constituting the convex portion 51a of the first groove 51 is a groove having a protruding shape from the first end portion 41 toward the second end portion 42.
  • at least a part of the convex portion 51a of the first groove 51 has a curved shape having a protruding shape from the second end portion 42 toward the first end portion 41. It may be a groove.
  • FIG. 15 an example in which all the convex portions 51a of the first groove 51 are formed of curved grooves having a protruding shape from the second end portion 42 toward the first end portion 41. Shows.
  • FIG. 16 is a view of an example of the vane of the rotary compressor according to the fourth embodiment observed from the first side surface.
  • the direction perpendicular to the sliding direction of the vane 40 is defined as the width direction of the vane 40.
  • the vertical direction of the paper surface is the width direction of the vane 40.
  • the convex portion 51a of the vane 40 described above has a symmetrical shape with respect to a virtual line passing through the center in the width direction of the vane 40 and parallel to the sliding direction of the vane 40.
  • the convex portion 51a of the vane 40 passes through the center in the width direction of the vane 40 and has an asymmetric shape with respect to the virtual line parallel to the sliding direction of the vane 40. May be.
  • FIG. 17 is a view of an example of the vane of the rotary compressor according to the fourth embodiment observed from the first side surface.
  • the vane 40 described above was provided with one convex portion 51a.
  • the vane 40 may include a plurality of convex portions 51a. Note that FIG. 17 shows an example in which the two convex portions 51a are arranged side by side in the width direction of the vane 40.
  • FIGS. 18 and 19 are views of an example of the vane of the rotary compressor according to the fourth embodiment observed from the first side surface.
  • the axis parallel to the sliding direction of the vane 40 when the vane 40 is viewed from the side is defined as the Y axis.
  • the above-mentioned second groove 52 is parallel to the Y-axis when the vane 40 is viewed from the side.
  • the second groove 52 may be tilted with respect to the Y axis when the vane 40 is viewed from the side.
  • the inclination of the second groove 52 with respect to the Y axis is small.
  • the angle ⁇ which is the angle extending toward the second end portion 42, is preferably smaller than 45 °.
  • FIG. 20 is a view of the vane of the rotary compressor according to the fifth embodiment observed from the first side surface.
  • 21 is a sectional view taken along the line CC of FIG.
  • the depth of the convex portion 51a of the first groove 51 according to the fifth embodiment decreases from the end portion 51c toward the top portion 51b.
  • FIGS. 20 and 21 describe an example in which the depth of the groove constituting the convex portion 51a changes linearly.
  • the depth of the groove constituting the convex portion 51a may change in a curved shape or may change in a stepped shape.
  • the method of changing the depth of the second groove 52 is also the same.
  • FIG. 22 shows an example in which the width of the groove constituting the convex portion 51a changes linearly.
  • the width of the groove constituting the convex portion 51a may change in a curved shape or may change in a stepped shape.
  • the method of changing the width of the second groove 52 is the same.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

La présente invention divulgue un compresseur rotatif comprenant : un cylindre dans lequel une chambre de cylindre est formée ; un piston roulant destiné à effectuer un mouvement de rotation excentrique à l'intérieur de la chambre de cylindre ; une aube dont une première section d'extrémité est en contact avec une surface circonférentielle externe du piston roulant afin de diviser la chambre de cylindre ; et un ressort rangé dans une chambre de rangement de ressort et destiné à exercer une pression sur une seconde section d'extrémité de l'aube, c'est-à-dire une section d'extrémité opposée à la première section d'extrémité, vers le piston roulant. Une rainure d'aube, en communication avec la chambre de cylindre et avec la chambre de rangement de ressort, et destinée à retenir coulissante l'aube, est formée sur le cylindre. Sur une surface exposée de l'aube faisant face à la rainure d'aube, et/ou sur une surface exposée de la rainure d'aube faisant face à l'aube, une première rainure, dont une pression interne est augmentée lorsque l'aube se déplace vers l'avant de manière à faire saillie dans la chambre de cylindre, et une seconde rainure, dont une extrémité est en communication avec la première rainure et dont l'autre extrémité est en communication avec la chambre de rangement de ressort, sont formées.
PCT/JP2020/024342 2020-06-22 2020-06-22 Compresseur rotatif Ceased WO2021260759A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2022531252A JP7313560B2 (ja) 2020-06-22 2020-06-22 ロータリ圧縮機
PCT/JP2020/024342 WO2021260759A1 (fr) 2020-06-22 2020-06-22 Compresseur rotatif
CN202080102123.XA CN115698508B (zh) 2020-06-22 2020-06-22 旋转压缩机

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2020/024342 WO2021260759A1 (fr) 2020-06-22 2020-06-22 Compresseur rotatif

Publications (1)

Publication Number Publication Date
WO2021260759A1 true WO2021260759A1 (fr) 2021-12-30

Family

ID=79282680

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2020/024342 Ceased WO2021260759A1 (fr) 2020-06-22 2020-06-22 Compresseur rotatif

Country Status (3)

Country Link
JP (1) JP7313560B2 (fr)
CN (1) CN115698508B (fr)
WO (1) WO2021260759A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115289018A (zh) * 2022-07-22 2022-11-04 广州市德善数控科技有限公司 压缩机及温度调节系统

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61197791A (ja) * 1985-02-27 1986-09-02 Toshiba Corp 圧縮機
JPS62271985A (ja) * 1986-05-20 1987-11-26 Matsushita Electric Ind Co Ltd 密閉型回転式圧縮機

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010112173A (ja) * 2008-11-04 2010-05-20 Panasonic Corp ロータリ圧縮機
JP5442638B2 (ja) * 2008-12-26 2014-03-12 パナソニック株式会社 回転式圧縮機
WO2013061606A1 (fr) * 2011-10-28 2013-05-02 パナソニック株式会社 Compresseur rotatif et dispositif de cycle de réfrigération
JP6091303B2 (ja) * 2013-04-12 2017-03-08 三菱電機株式会社 ローリングピストン形圧縮機
CN110836184B (zh) * 2018-08-17 2022-03-04 Lg电子株式会社 旋转式压缩机

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61197791A (ja) * 1985-02-27 1986-09-02 Toshiba Corp 圧縮機
JPS62271985A (ja) * 1986-05-20 1987-11-26 Matsushita Electric Ind Co Ltd 密閉型回転式圧縮機

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115289018A (zh) * 2022-07-22 2022-11-04 广州市德善数控科技有限公司 压缩机及温度调节系统

Also Published As

Publication number Publication date
JP7313560B2 (ja) 2023-07-24
JPWO2021260759A1 (fr) 2021-12-30
CN115698508A (zh) 2023-02-03
CN115698508B (zh) 2024-10-01

Similar Documents

Publication Publication Date Title
US6132195A (en) Rotary compressor
CN110520624B (zh) 旋转式压缩机
US10982675B2 (en) Rotary compressor with groove for supplying oil
KR20100084079A (ko) 로터리 압축기
KR20180095391A (ko) 로터리 압축기
KR20180094411A (ko) 로터리 압축기
WO2017061014A1 (fr) Compresseur rotatif
EP3770378B1 (fr) Compresseur rotatif
CN203796562U (zh) 旋转活塞型压缩机
JP7313560B2 (ja) ロータリ圧縮機
JP2010180703A (ja) スクロール圧縮機
CN105782030B (zh) 一种涡旋压缩机
US8454333B2 (en) Rotary fluid machine having outer and inner cylinder chambers with different heights
KR102442465B1 (ko) 로터리 압축기
JP5799258B2 (ja) 摺動部材及び圧縮機
US11732584B2 (en) Rotary compressor with unequally spaced vane slots
US20230332600A1 (en) Flange and Pump Body Assembly with Same
US10794187B2 (en) Rotary compressor with a valve in the vane
JP6758422B2 (ja) 回転圧縮機
JP2009108762A (ja) 回転式流体機械
KR101954533B1 (ko) 로터리 압축기
JP2002221165A (ja) ロータリ圧縮機
CN111065824B (zh) 旋转式压缩机
KR20180094410A (ko) 로터리 압축기
JPH08284857A (ja) 密閉形回転圧縮機

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 20941680

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2022531252

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 20941680

Country of ref document: EP

Kind code of ref document: A1