US3760478A - Method for assembling a rotary sliding vane compressor - Google Patents

Method for assembling a rotary sliding vane compressor Download PDF

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Publication number
US3760478A
US3760478A US00185994A US3760478DA US3760478A US 3760478 A US3760478 A US 3760478A US 00185994 A US00185994 A US 00185994A US 3760478D A US3760478D A US 3760478DA US 3760478 A US3760478 A US 3760478A
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United States
Prior art keywords
cylinder
rotor
compressor
rear plate
contact point
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Expired - Lifetime
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US00185994A
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English (en)
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L Harlin
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Borg Warner Corp
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Borg Warner Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0872—Vane tracking; control therefor by fluid means the fluid being other than the working fluid
    • 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
    • F04C18/344—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 inner member
    • F04C18/3441—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 inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F04C29/025—Lubrication; Lubricant separation using a lubricant pump
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/603—Centering; Aligning
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/04—PTFE [PolyTetraFluorEthylene]
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49229—Prime mover or fluid pump making
    • Y10T29/49236—Fluid pump or compressor making
    • Y10T29/49245—Vane type or other rotary, e.g., fan
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49826—Assembling or joining
    • Y10T29/4984—Retaining clearance for motion between assembled parts
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49995—Shaping one-piece blank by removing material
    • Y10T29/49996—Successive distinct removal operations

Definitions

  • This invention relates generally to a rotary compressor of the sliding vane type and more particularly to an arrangement and an assembling method for enhancing the compressors performance, capacity, efficiency and reliability.
  • the invention is especially attractive when practiced with respect to a rotary sliding vane compressor adapted for use in an automotive air-conditioning system and will be described in that environment.
  • vanes are slidably received in slots of a rotor revolving within a cylindrical wall of a cylinder and about a rotational axis offset oreccentric relative to the walls axis.
  • the contact point At the point of closest spacing between the rotor and cylinder (called the contact point), very little clearance is provided in order that a crescent-shaped compression chamber is formed between the rotor and cylindrical wall and between parallel spaced front and rear bearing plates respectively positioned adjacent to the two sides of the cylinder.
  • vanes bear against the cylindrical wall as the rotor rotates so that gas introduced into one end or side (called the low pressure side)'of the compression chamber is compressed and discharged from the other end or high pressure side at a higher pressure.
  • the clearance at the contact point be minimized to effectively seal or isolate the high and low pressure sides of the compression chamber from each other. The greater the clearance at the contact point, the greater will be the leakage through that point fromthe high to the low pressure side of the, compression chamber, and the greater will be the loss of compression.
  • the present invention is calculated to overcome these shortcomings of prior rotary compressors by providing a novel assembling method which ensures and maintains an optimum contact point clearance to achieve less leakage than previously obtainable while at the same time introducing no significant friction.
  • an object of the invention to provide a unique arrangement for optimizing the contact point clearance in a rotary sliding vane compressor.
  • a further object is to provide a compressor that is more reliable and immune to failure than those previously developed.
  • An additional goal is to provide a method for assembling the uniquely constructed compressor so that precise alignment of the compressors parts will always be retained under the most severe operating conditions.
  • a method for assembling a rotary sliding vane compressor wherein a slottedrotor, with an external cylindrical surface of self-lubricating material, has its drive shaft joumalled in bearings of parallel spaced front and rear bearing plates to rotatably mount the rotor eccentrically within an internal cylindrical wall of a cylinder positioned between the bearing plates thereby to provide, between the cylindrical surface and wall and between the bearing plates, a crescent-shaped compression chamber having high and low pressure sides sealed from each other, and in which dowel pins extend between the cylinder and front and rear plates to maintain their alignment and to prevent any shifting of those three elements relative to each other.
  • the novel method comprises the steps of rotatably mounting the drive shaft in the bearing of the rear plate, and positioning the cylinder around the rotor and adjacent to the rear plate. Thereafter the cylinder is pivoted relative to the rear plate to establish a contact point, between the rotors cylindrical surface and the cylinders cylindrical wall, that provides a line-to-line sealing fit withzero clearance.
  • the front and rear plates, cylinder and rotor are then held in assembled relationship, after which at least one hole is drilled and reamed parallel to the rotors axis and through portions of the front plate and the cylinder, and at least one other hole is drilledand reamed parallel to the rotors axis and through portions of the cylinder and the rear plate.
  • a dowel pin is then driven into each of the holes.
  • FIGS. 1 and 2 are different section views of a rotary sliding vane compressor constructed in accordance with the present invention, the FIG. 1 view being taken along section line 1-1 in FIG. 2 while the sectional view of FIG. 2 is taken along section line 2-2 in FIG. 1; and,
  • FIGS. 3 and 4 are exploded, perspective views illustrating the novel manner in which the compressor of FIGS. 1 and 2 is assembled.
  • the compressor has a casing which includes a cylinder 11 having an internal cylindrical wall or bore 12 extending therethrough, a front bearing plate 15, and a rear bearing plate 16, all assembled and secured together in a manner to be described.
  • Casing 10 provides or defines a closed cylindrical cavity formed by cylindrical wall 12 and bearing plates 15 and 16 which serve as parallel spaced end walls for the cavity.
  • a rotor assembly 20 (see especially FIG.
  • rotor 21 is rotatably mounted eccentrically within wall 12 and includes a slotted rotor 21 having a series of four slots 22 arranged circumferentially and each extending along a plane parallel to the rotors axis. The closed end of each slot may be referred to, for convenience, as the bottom end.
  • Each of a series of four reciprocating vanes or blades 23 is slidably mounted in a respective one of slots 22.
  • the cylindrical surface of rotor 21 is coated or bonded with a layer 21a of self-lubricating material, such as TEFLON.
  • the eccentric positioning of rotor assembly 20 is obtained by rotatably mounting rotor 21 on an axis offset with respect to the axis of cylindrical wall 12.
  • rotor 21 As is best seen in FIG. 2, at the contact point (indicated by reference numeral 24) between coating 21a and cylindrical wall 12 there is essentially zero clearance. A seal is thus created at contact point 24 so that the open space bounded by rotor 21, cylinder 11 and bearing plates 15 and 16 provides a crescent-shaped compression chamber, identified by the numeral 25.
  • Rotor 21 and casing 10 are made so that the dimension between the parallel rotor faces 26 and 27 is slightly less than the spacing between bearing plates 15 and 16.
  • Rotor 21 has a drive shaft 30 journalled in bearings 31 and 32 affixed to bearing plates 15 and 16 respectively.
  • the left end of shaft 30 projects outwardly of front bearing plate 15 so that the shaft may be driven.
  • a V-belt pulley and clutch mechanism (not shown) would be coupled to the left end of shaft 30 to permit the compressor to be driven by the engine fan belt or accessory drive belt of the automobile.
  • the disclosed compressor may, of course, be employed in many different environments and may be used in other than refrigeration or air-conditioning systems to compress a variety of different gaseous fluids. Whatever the driving means, it may conveniently be coupled to drive shaft 30.
  • the compressor is designed to operate when rotor assembly 20 revolves in a clockwise direction as viewed in FIG. 2, during which time vanes 23 firmly bear against cylindrical wall 12 and establish fluid-tight sealed connections thereto.
  • suction refrigerant gas from the evaporator of the automotive airconditioning system is admitted to an inlet 35 formed in cylinder 11.
  • this refrigerant gas flows into the suction portion of compression chamber 25.
  • the gas is'trapped between two adjacent vanes 23 and carried forward toward the discharge area. As this occurs, the volume between the adjacent vanes is reduced thereby resulting in a corresponding increase in pressure of the gas.
  • a discharge valve assembly 36 is located in the discharge zone for assuring proper compression of the gases issuing from three rows of outlet or discharge ports 37 in cylinder 11 and for preventing reverse flow of gases back into compression chamber 25.
  • Valve assembly 36 is of the reed type comprising three valve reeds 38 respectively held in place by three valve guards or stops 39.
  • the compressed refrigerant gas emanating from ports 37 flows into a chamber 42 defined by cylinder 11 and a cover plate 43.
  • pressurized oil is supplied to all of the moving components and bearing surfaces to provide proper lubrication and to assist in isolating the high and low pressure sides of the compression chamber from each other.
  • oil is delivered to the bottom ends of slots 22 to force vanes 23 outwardly and toward wall 12.
  • a reservoir of oil or sump 44 is provided in the lower portion of a shell 46, the open end of which is attached and hermetically sealed to a mounting ring 47 in turn affixed to casing 10.
  • a preferred construction of oil pump 54 is shown in detail in copending U.S. Pat. application Ser. No.
  • passage 49 communicates to the pump inlet, while the pump outlet fluidly connects to the axially extending, large cross section bore 68 in drive shaft 30.
  • inner gear 57 likewise rotates and effects pumping of oil from sump 44 to axial bore 68.
  • the pressurized oil may flow through the entire length of bore 68 without appreciably dropping in pressure due to the bores large cross section. Since the oil pressure is the same throughout passage 68, it effectively constitutes a source of pressurized oil.
  • a single radially extending passage 69 in shaft 30 couples oil source 68 to a circumferential annular groove 71 which in turn communicates, via a series of four radially extending passages 72 drilled in rotor 21, to the bottom ends of slots 22.
  • the high pressureoil exiting from oil pump 54 is delivered to the slots behind vanes 23 thereby to impel the vanes toward and in sealed engagement with cylindrical wall 12.
  • the magnitude of the oil pressure is set so that during start-up the pressurized oil alone will be sufficient to cause the vanes to move out of their slots and establish fluid-tight connections with the cylindrical wall.
  • the pressure level will be just adequate to make the required sealed contact between the vane tips and cylindrical wall, but yet will not cause undue strain on the vanes and needless wear.
  • radially extending passage 81 and circumferential groove 82 in shaft 30 communicate oil passage 68 to hydrostatic bearing cavity 76.
  • Passages 77 and 81 have relatively small cross sections so that they will function as flow control orifices. In this way, the oil flow to each of cavities 75 and 76 experiences a substantial pressure drop in the associated orifice 77, 81.
  • a hydrostatic force is produced in each cavity75, 76 depending on the lubricant pressure in the cavity and the area of the cavity.
  • Orifices 77 and 81 and cavities 75 and 76 may be dimensioned and shaped so that under normal conditions equal pressure drops occur in the orifices and in the two clearances 28, 29, as a result of which equal pressures and hydrostatic forces are established in the cavities to center rotor 21 between bearing plates 15 and 16.
  • Oil separation in the disclosed compressor takes place within shell 46.
  • a passageway formed by openings 85, 86 and 87 in cylinder 11, rear bearing plate 16 and mounting ring 47, respectively, together with tube 88 communicates chamber 42 to the extreme end of shell 46.
  • Tube 88 extends through an oil separating filter screen 89 comprised of gas permeable material, such as coarse mesh metal fibers as in a scouring pad.
  • the periphery of separator 89 has the same contour as that of the shell so that its edges fit against the internal diameter of the shell. In this way, separator 89 constitutes a partition to define two different chambers 91 and 92 within shell 46.
  • Element 93 serves as a support bracket for separator 89, while element 94 constitutes a baffle.
  • the discharge gas together with the entrained oil flows out of chamber 42 and into chamber 91 through the conduit provided by bores 85, 86 and 87 and tube 88. At that point the velocity of the gas is greatly reduced as it expands into a much larger volume.
  • the gas strikes the end of shell 46 and reverses direction as a consequence of which most of the oil separates on the rear surface of the shell and flows down into sump 44.
  • the discharge gas flowing into chamber 92 will thus be oil-free.
  • a discharge oulet 95 mounted on shell 46 permits the gas to flow out of chamber 92.
  • Baffle 94 prevents the turbulent gas from reaching and stirring up oil pool 44 and re-entraining oil back into the gas.
  • pin 101 The diameter of pin 101 is less than that of hole 102 so that the pin may be passed freely through that hole and then screwed into tapped hole 103.
  • cylinder 11 may be pivoted in a horizontal plane around a pivot point provided by pin 101.
  • cylindrical wall 12 By pivoting cylinder 11 relative to rear plate 16, cylindrical wall 12 may be brought into engagement with the coating 21a of selflubricating material on the rotors cylindrical surface, thereby establishing at contact point 24 a line-to-line sealing fit with zero clearance.
  • Front plate is now placed over cylinder 11 so that the upper end of shaft 30 (as viewed in FIG. 3) is received by bearing 31. It is then necessary to temporarily hold the bearing plates, cylinder and rotor in assembled relationship. This is made possible by three subassembly bolts 105 each of which may be inserted through a pair of aligned openings 106 and 107 in plate 15 and cylinder 11 respectively and then screwed into a tapped hole 108 of rear plate 16. Of course, the diameters of holes 106 and 107 are sufficiently large to permit bolts to be extended therethrough and screwed into rear plate 16 regardless of the relative positions of the cylinder and rear plate.
  • a third hole 113 is drilled and reamed from the top of and through the reduced thickness portion 11c and rear plate 16.
  • the two dowel pins 115 are then driven into respective ones of holes 111 from the top of the front plate, and the third dowel pin 117 is driven from the top of the cylinder through hole 113.
  • the dowel pins thus fit extremely snub or tight within their associated holes, as a consequence of which absolutely no shifting of the cylinder relative to either one of the bearing plates is possible. Misalignment therefore cannot occur during operation when gases are compressed, and the desired zero clearance at the contact point'will not be disturbed.
  • the assembled casing and rotor are then removed from the jig.
  • the oil separator is assembled within shell 46 and mounting ring 47 is secured, such as by brazing, to the open end of the shell. Rigidly affixed to mounting ring 47 are six circumferentially arranged main assembly studs 119. Shell 46 and the assembled oil separator may be attached to the casing, rotor assembly and oil pump, while at the same time additional holding forces are provided, by inserting studs 119 through respective ones of the six large, unnumbered openings in each of plates 15 and 16 and cylinder 11. Each stud 119 is capped by a nut 121, see especially FIG. 1.
  • Cover plate 43 may be mounted to cylinder 11 at any convenient step in the assembling procedure.
  • the invention provides, therefore, a unique method for assembling a rotary sliding vane compressor in which an optimum contact point clearance is established and maintained in order to minimize both friction'and leakage at that point, thereby to enhance the compressors performance, capacity, efficiency and reliability.
  • a method for assembling a rotary sliding vane compressor wherein a slotted rotor, with an external cylindrical surface'of self-lubricating material, has its drive shaft journalled in bearings of parallel spaced front and rear bearing plates torotatably mount the rotor eccentric ally within an internal cylindrical wall of a cylinder positioned between the bearing plates thereby to provide, between the cylindrical surface and wall and between the bearing plates, a crescent-shaped compression chamber having high and low pressure sides sealed from each other, and in which dowel pins extend between the cylinder and front and rear plates to maintain their alignment and to prevent any shifting of those three elements relative to each other, the method comprising the steps of:
  • a method according to claim 1 in which, prior to the drilling and reaming steps, a plurality of subassembly bolts are extended through the front plate and cylinder and screwed into the rear plate to hold the plates, cylinder and the rotor in assembled relationship.
  • a method according to claim 3 in which, after the dowel pinsare driven into place, a plurality of main assembly studs are extended through the plates and cylinder and are then capped with nuts to provide additional forces to hold the assembled compressor together.
  • thermal differentials between the rotor and cylinder may cause expansion of at least one of those elements as a result of which the self-lubricating material on the rotors cylinrical surface wears until a desired very close sealing fit, with minimum friction, is established at the contact point.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
US00185994A 1971-10-04 1971-10-04 Method for assembling a rotary sliding vane compressor Expired - Lifetime US3760478A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US18599471A 1971-10-04 1971-10-04

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US3760478A true US3760478A (en) 1973-09-25

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US (1) US3760478A (enrdf_load_stackoverflow)
JP (1) JPS5550198B2 (enrdf_load_stackoverflow)
AU (1) AU464004B2 (enrdf_load_stackoverflow)
BR (1) BR7206524D0 (enrdf_load_stackoverflow)
CA (1) CA965064A (enrdf_load_stackoverflow)
DE (1) DE2248647A1 (enrdf_load_stackoverflow)
FR (1) FR2155583A5 (enrdf_load_stackoverflow)
GB (1) GB1383034A (enrdf_load_stackoverflow)
IT (1) IT986855B (enrdf_load_stackoverflow)

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US3913198A (en) * 1974-07-01 1975-10-21 Ford Motor Co Alignment of the major housings in a wankel rotary engine
US4563124A (en) * 1984-02-24 1986-01-07 Figgie International Inc. Double suction, single stage volute pump
US5170555A (en) * 1990-03-26 1992-12-15 Copeland Corporation Method of assembling a refrigeration compressor
WO2003056179A1 (de) * 2001-12-27 2003-07-10 Luk Fahrzeug-Hydraulik Gmbh & Co.Kg Pumpe
CN101871366A (zh) * 2010-07-02 2010-10-27 西安交通大学 一种滑片槽底引压的滑片式膨胀机
CN103967529A (zh) * 2014-05-08 2014-08-06 重庆大学 一种滑片膨胀机
CN104074550A (zh) * 2014-07-08 2014-10-01 重庆春升科技发展有限公司 一种无润滑油的滑片膨胀机和/或压缩机
CN104607847A (zh) * 2015-01-28 2015-05-13 安徽众汇制冷有限公司 一种气液分离器焊接夹具及其使用方法和制造方法
CN113090525A (zh) * 2021-04-15 2021-07-09 重庆交通大学 一种旋叶式压缩机密闭腔体复合动态测量装置
CN113898585A (zh) * 2021-10-26 2022-01-07 浙江象睿机电设备有限公司 一种空气压缩机的能耗智能控制装置
US11428224B2 (en) * 2018-11-09 2022-08-30 Lg Electronics Inc. Vane rotary compressor having a bearing with back pressure pockets
CN115741004A (zh) * 2022-11-11 2023-03-07 长兴佰菲特机械有限公司 一种分配式油泵协同装配装置及方法
US12163516B1 (en) * 2023-06-06 2024-12-10 Rivian Ip Holdings, Llc Pump assembly fixture
EP4310334A4 (en) * 2021-03-19 2025-04-16 LG Electronics Inc. ROTARY COMPRESSOR

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JPS52115628A (en) * 1976-03-24 1977-09-28 Hitachi Ltd Ink jet recorder
IT1085211B (it) * 1976-04-07 1985-05-28 Gen Signal Corp Pompa ad anello liquido
EP0003572B2 (de) * 1978-02-06 1991-12-11 b a r m a g Barmer Maschinenfabrik Aktiengesellschaft Flügelzellenpumpe
FR2517380B1 (fr) * 1981-11-30 1986-04-18 Rivapompe Sa Pompe a vide rotative a palettes destinees a maintenir un niveau de vide dans une capacite
FR2541388B1 (fr) * 1982-05-13 1987-05-07 Zimmern Bernard Injection pour compresseur a vis haute pression
JPS63176117U (enrdf_load_stackoverflow) * 1987-05-01 1988-11-15
DE19526303A1 (de) * 1995-07-19 1997-01-23 Leybold Ag Ölgedichtete Drehschiebervakuumpumpe mit einer Ölversorgung
CN111397888B (zh) * 2020-04-30 2022-07-12 庆安集团有限公司 一种磁悬浮离心压缩机用旋转检测装置及检测方法

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US2467121A (en) * 1944-04-10 1949-04-12 Oilgear Co Method of making vane tracks
US3011449A (en) * 1960-04-15 1961-12-05 Thompson Grinder Co Vaned hydraulic unit
US3190183A (en) * 1962-05-10 1965-06-22 Cooper Bessemer Corp Air tool improvement
US3415058A (en) * 1967-04-26 1968-12-10 Borg Warner Hydraulic pump control system
US3642388A (en) * 1969-04-09 1972-02-15 Renault Variable-capacity vane pumps
US3552895A (en) * 1969-05-14 1971-01-05 Lear Siegler Inc Dry rotary vane pump

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US3913198A (en) * 1974-07-01 1975-10-21 Ford Motor Co Alignment of the major housings in a wankel rotary engine
US4563124A (en) * 1984-02-24 1986-01-07 Figgie International Inc. Double suction, single stage volute pump
US5170555A (en) * 1990-03-26 1992-12-15 Copeland Corporation Method of assembling a refrigeration compressor
WO2003056179A1 (de) * 2001-12-27 2003-07-10 Luk Fahrzeug-Hydraulik Gmbh & Co.Kg Pumpe
FR2835573A1 (fr) * 2001-12-27 2003-08-08 Luk Fahrzeug Hydraulik Pompe
US20050163631A1 (en) * 2001-12-27 2005-07-28 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Pump
US7520732B2 (en) * 2001-12-27 2009-04-21 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Pump
CN101871366A (zh) * 2010-07-02 2010-10-27 西安交通大学 一种滑片槽底引压的滑片式膨胀机
CN103967529A (zh) * 2014-05-08 2014-08-06 重庆大学 一种滑片膨胀机
CN104074550A (zh) * 2014-07-08 2014-10-01 重庆春升科技发展有限公司 一种无润滑油的滑片膨胀机和/或压缩机
CN104607847A (zh) * 2015-01-28 2015-05-13 安徽众汇制冷有限公司 一种气液分离器焊接夹具及其使用方法和制造方法
CN105414859A (zh) * 2015-01-28 2016-03-23 安徽众汇制冷有限公司 一种气液分离器焊接夹具的使用方法
CN105414858A (zh) * 2015-01-28 2016-03-23 安徽众汇制冷有限公司 一种制造气液分离器焊接夹具的方法
US11428224B2 (en) * 2018-11-09 2022-08-30 Lg Electronics Inc. Vane rotary compressor having a bearing with back pressure pockets
EP4310334A4 (en) * 2021-03-19 2025-04-16 LG Electronics Inc. ROTARY COMPRESSOR
CN113090525A (zh) * 2021-04-15 2021-07-09 重庆交通大学 一种旋叶式压缩机密闭腔体复合动态测量装置
CN113898585A (zh) * 2021-10-26 2022-01-07 浙江象睿机电设备有限公司 一种空气压缩机的能耗智能控制装置
CN113898585B (zh) * 2021-10-26 2023-08-04 浙江象睿机电设备有限公司 一种空气压缩机的能耗智能控制装置
CN115741004A (zh) * 2022-11-11 2023-03-07 长兴佰菲特机械有限公司 一种分配式油泵协同装配装置及方法
US12163516B1 (en) * 2023-06-06 2024-12-10 Rivian Ip Holdings, Llc Pump assembly fixture
US20240410366A1 (en) * 2023-06-06 2024-12-12 Rivian Ip Holdings, Llc Pump assembly fixture

Also Published As

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IT986855B (it) 1975-01-30
JPS4844805A (enrdf_load_stackoverflow) 1973-06-27
AU4645872A (en) 1974-03-14
DE2248647A1 (de) 1973-05-17
BR7206524D0 (pt) 1973-08-21
GB1383034A (en) 1975-02-05
JPS5550198B2 (enrdf_load_stackoverflow) 1980-12-16
FR2155583A5 (enrdf_load_stackoverflow) 1973-05-18
AU464004B2 (en) 1975-08-14
CA965064A (en) 1975-03-25

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