US3865515A - Self adjusting tangency-clearance compressor with liquid purge capability - Google Patents

Self adjusting tangency-clearance compressor with liquid purge capability Download PDF

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Publication number
US3865515A
US3865515A US421988A US42198873A US3865515A US 3865515 A US3865515 A US 3865515A US 421988 A US421988 A US 421988A US 42198873 A US42198873 A US 42198873A US 3865515 A US3865515 A US 3865515A
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United States
Prior art keywords
cylinder
rotor
housing
tangency
fluid
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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.)
Expired - Lifetime
Application number
US421988A
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English (en)
Inventor
Clifford H Allen
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.)
Northrop Grumman Space and Mission Systems Corp
Original Assignee
TRW Inc
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 TRW Inc filed Critical TRW Inc
Priority to US421988A priority Critical patent/US3865515A/en
Priority to CA213,260A priority patent/CA1031307A/en
Priority to GB48913/74A priority patent/GB1479911A/en
Priority to AU75723/74A priority patent/AU488203B2/en
Priority to BR10023/74A priority patent/BR7410023A/pt
Priority to FR7439562A priority patent/FR2253917B1/fr
Priority to SU742081921A priority patent/SU847942A3/ru
Priority to JP13942874A priority patent/JPS5442448B2/ja
Priority to DE2457319A priority patent/DE2457319C3/de
Priority to ES432604A priority patent/ES432604A1/es
Priority to IT30197/74A priority patent/IT1026801B/it
Application granted granted Critical
Publication of US3865515A publication Critical patent/US3865515A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/001—Radial sealings for 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
    • 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
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S418/00—Rotary expansible chamber devices
    • Y10S418/01—Non-working fluid separation

Definitions

  • 1975 pressing refrigerant in air-conditioning systems has a vane carrying rotor mounted on fixed center bearings and surrounded by an eccentrically positioned cylinder guiding the vane motion and confining and controlling the compression process which is free to swing toward the rotor and maintain a line of tangency Contact therewith providing a direct barrier between the discharge and suction sides of the compression chamber.
  • a spring loaded end plate pressed against one end of the cylinder serves as a relief valve to purge liquid such as lubricant which might collect in the compression cavities during a shut-down period and which could otherwise create a lock-up condition.
  • a fixed front bearing plate or end head has a cupshaped housing piloted thereon surrounding the cylinder and providing a rear bearing mounting for the rotor.
  • the front plate has an inlet port supplying the compression cavities between the rotor and cylinder.
  • the cylinder has an outlet adjacent the tangency seal line of contact between the rotor and cylinder which discharges to a chamber between the housing and cylinder that is surrounded by porous fibrous strips effective to separate lubricant entrained in the compressed refrigerant.
  • the refrigerant is discharged to an outlet port in the front bearing plate and the separated lubricant collects in the bottom of the housing and is circulated back to the bearings and vane slots of the rotor.
  • the above-mentioned deficiencies of the prior art are eliminated by piloting the rear bearing support for the rotor shaft on the front main bearing plate or end head to insure accurate alignment ofthe front and rear shaft bearings, by pivoting the cylinder on its outer periphery midway between its end faces, by allowing the cylinder to swing on its pivot during operation of the compressor so that the tangency seal load will be controlled by the pressures in the high-pressure cavities of the compressor and by providing a retractable end plate for the rotor and cylinder which will release liquid from the compressor cavities to prevent lock-up upon starting.
  • the invention provides wick means for separating lubricant which might be entrained with compressed refrigerant enroute to the outlet port. The separated lubricant is collected in a sump provided in the bottom of the compressor housing and is recirculated back to the bearings and vane slots to lubricate the bearings and vanes.
  • the pivot for the cylinder is a shoe carried by the housing.
  • a spring also carried by the housing urges the cylinder to rotate about its pivot into contact with the rotor to maintain a minimum load tangency seal which, of course, is additionally loaded by the pressures in the compression cavities. This arrangement eliminates the heretofore required accurate positioning of pivot pins and prevents binding of the swinging of the cylinder.
  • the cylinder is surrounded in spaced relation by a cup-shaped housing piloted on the end head or front bearing plate of the compressor and has outlet holes in the top thereof immediately ahead of the tangency line of contact with the rotor which discharge the compressed refrigerant into a localized compartment between the cylinder and housing bounded by fibrous strips.
  • the refrigerant passes through these strips to an outlet port in the front hearing plate or main end head of the compressor. Any lubricant entrapped with the compressed refrigerant is wicked from the refrigerant by the fibrous strip material and accumulates to drip down to a collection sump in the bottom of the housing.
  • a passageway in the end head conveys the collected lubricant from the sump through the shaft bearings and center of the rotor for lubricating the bearings and the vanes.
  • vane-type compressors as used herein will serve to encompass pumps, motors, and compressors having eccentrically related rotors and encompassing chamber defining members on which fingers projecting from the rotor will ride and wherein the rotor has a tangency seal relationship with the encompassing member between the high pressure and low pressure sides of the device.
  • Another object of the invention is to provide a selfliquid purging gas or vapor compressor.
  • Another object of the invention is to provide a vapor or gas compressor separating liquid from the compressed gas or vapor and utilizing the liquid to lubricate the compressor parts.
  • Another object of this invention is to provide a rotary vane compressor with a free swinging rotor encompassing cylinder which guides the vanes and establishes a tangency seal between the high and low pressure sides of the compressor at a sealing load created by the pressures in the compressor cavities.
  • Another object of the invention is to provide a rotary vane compressor with a swinging rotor encompassing cylinder on which the vanes ride which is spring-loaded into sealed contact with the rotor along a line of tangency between the high pressure and low pressure compressor cavities.
  • a further object of the invention is to provide a rotary vane compressor with a housing cylinder pivoted on an external shoe and swung into a tangency sealing line of contact with the rotor under the influence of pressures in the compressor cavities between the rotor and cylinder.
  • a further object 'of the invention is to provide a rotary vane compressor with a rotor mounted on fixed center bearings, a cylinder surrounding the rotor in eccentric relation, a housing surrounding the cylinder in spaced relation and a pivot shoe carried by the housing allowing the cylinder to swing for establishing and maintaining a tangency seal line of contact with the rotor between the high pressure and low pressure sides of the compressor.
  • a still further object of the invention is to provide a refrigerant compressor especially suited for airconditioning systems having a front bearing carrying end head, a bearing carrying cup housing piloted on the end head, a vane carrying rotor mounted on a shaft supported in bearings carried by the end head and cup housing, a cylinder in the housing surrounding the rotor and guiding the rotor vanes, a pivot shoe carried by the housing cooperating with the periphery of the cylinder, a spring swinging the cylinder about the pivot shoe into sealed contact with the rotor, a spring loaded end plate in the housing pressed against an end face of the cylinder and adapted to be deflected therefrom and means between the housing and cylinder for separating lubricant from refrigerant compressed by the rotor and vane.
  • FIG. 1 is a front end elevational view of a rotary vane compressor of this invention
  • FIG. 2 is a longitudinal, cross sectional view taken along the line II--II of FIG. 1;
  • FIG. 3 is a transverse cross sectional view taken along the line III-III of FIG. 2;
  • FIG. 4 is a transverse, cross sectional view taken along the line IV-IV of FIG. 4;
  • FIG. 5 is a fragmentary plan view along the line V-V of FIG. 6;
  • FIG. 6 is a cross sectional view along the line VI.-Vl of FIG. 5;
  • FIG. 7 is a transverse, cross sectional viewalong the line VII--Vll of FIG. 3; v
  • FIG. 8 is a somewhat diagrammatic view similar to FIG. 3 showing the forces for swinging the cylinder into tangency sealed relation with the rotor;
  • FIG. 9 is a view similar to FIG. 3 but with the internal parts omitted to show the back wall of the cup-shaped housing.
  • FIG. 10 is a cross sectional view along the line X-X of FIG. 1.
  • the compressor 10 has a front bearing plate or main end head 11, a cup-shaped housing 12 with a cylindrical month 13 seated on a cylindrical pilot portion 14 of the end head 11 and hottomed against an end shoulder 15 of the end head.
  • An O-ring seal 16 is confined between the mouth 13, the pilot l4 and the end face 15.
  • the cup housing 12 has internally threaded boss portions 17 spaced around its periphery as shown in FIGS. 2 and 3 opening to the shoulder 15 of the end head 11 and bolts 18 having heads bottomed on the outer face of the end head 11 are threaded into these bosses to unite the end head 11 and cup 12 in integral, fixed, sealed relationship.
  • the end head 11 as shown in FIGS. 1, 2, and 4 has an inlet port 19 and an outlet port 20.
  • a relief valve 21 communicates with the port passageway 20 to relieve excess pressures which might damage the system supplied by the compressor.
  • the end head also has legs 22 and bosses 22a to mount the compressor in a refrigerant system such as an automobile air-conditioning system assembly.
  • a hub 23 at the center of the end head 11, as shown in FIG. 2, has a cylindrical bore 24 therethrough with an enlarged counterbore 25 at the inner end thereof.
  • This counterbore mounts a ball bearing assembly 26 which is held against the shoulder 27 between the counterbore 25 and bore 24 by a snap ring 28.
  • a shaft seal assembly 29 is mounted in the bore 24 including a shaft mounted spring loaded face ring part 29a and a hub mounted fixed mating ring part 29b held in the bore 24 by a snap retaining ring 30.
  • a rotor shaft 31 projects through the hub 23 of the end head 11 into a cylindrical hub 32 projecting from the rear end 33 of the cup-shaped housing 12 toward the end head 11. Roller or needle bearings 34 support this end of the shaft 31 in the hub 32 of the housing 12.
  • the shaft 31 has retainer rings 35 projecting from grooves therein into abutting relation with both end faces of the inner race ring of the ball bearing assembly 26, thereby holding the shaft against axial shifting relative to the hubs 23 and 32.
  • the shaft 31' is rotatably mounted on bearing supports provided by the end head 11 and the housing 12 which is accurately piloted on this end head so that true alignment of the bearing supports is established and maintained.
  • the rotor 36 for the compressor 10 is mounted on the rotor shaft 3' 1 for corotation therewith
  • the rotor 36 has four radial slots 37 in equally spaced circumferential relation extending inwardly from pockets 38 in the periphery of the rotor as shown in FIG. 3 for a depth to accommodate the height of vanes 39 slidably mounted therein when shoes 40 on the ends of the vanes are retracted into the pockets.
  • Two pairs of pins 41 and 42 extend through holes through the shaft and inner portion of the rotor into the slots 37 and receive coil springs 43 therearound acting on the inner ends of the vanes 39 to urge them outwardly from the bottoms of the slots.
  • one pair of pins 41 with the springs 43 therearound act on one pair of diametrically opposite vanes 39 while the other pair of pins 42 and their springs 43, offset from the pins 41, act on the other pair of diametrically opposite vanes 39.
  • a cylinder 44 as shown in FIGS. 2 and 3 is mounted in the housing 12 and envelops the rotor 36.
  • This cylinder has an inner peripheral wall 45 eccentrically related to the periphery 46 of the rotor 36 and spaced therefrom except at a single line of contact 47 at the point of tangency between the cylinder and rotor to establish a tangency seal between the low and high pressure sides of the compressor.
  • vanes 39 projecting from the rotor to have their slippers or pivot ends 40 riding on the inner wall 45 of the cylinder 44 divide the space between the wall 45 of the cylinder 44 and the periphery 46 of the rotor 36 into cavities receiving refrigerant from the inlet port 19 and discharging compressed refrigerant to the outlet port 20 as will be more fully hereinafter explained.
  • the cylinder 44 is pivoted in the housing 12 on a shoe 48 carried by a rib 49 of the housing 12 which projects inwardly from the periphery of the housing in circumferentially spaced relation upstream from the tangency seal line 47.
  • the shoe 48 has a nose 48a seated in a groove or recess 50 of a pivot plate 51 which is bolted to a flat peripheral portion 52 of the cylinder 44 by means of bolts 53.
  • the rib 49 carrying the shoe 48 and the recess 50 receiving the nose 48a of the shoe must be located within relatively broad limits at a point on the circumference of the cylinder 44 where the resultant couple due to pressures in the cylinder tends to pivot the cylinder in a direction tending to eliminate clearance at the line of tangency between the cylinder and rotor 36.
  • tolerances relative to locations of the pivot are not critical.
  • a reed valve 54 composed of a thin metal plate is clamped under the plate 51 by the bolts 53 and as shown in FIG. 3 the plate 51 is bowed outwardly from the flat surface 52 of the cylinder 44 at its unbolted or free end so that the reed valve 54 may be deflected outwardly from its seat on this flat area 52.
  • the cylinder 44 has a row of outlet ports 55 therethrough underlying the free end of the reed valve 54 and positioned just upstream or ahead of the tangency seal line 47 of the cylinder 44 with the rotor 36.
  • the compressed refrigerant is discharged through these ports 55 and raises the reed valve 54 to flow into a localized chamber 560 separated from the main annular space 56 between the housing 12 and cylinder 44 by fibrous side strips 57 extending from the end head 11 to the back wall 33 of the housing 12.
  • the inner ends of these strips 57 are seated in grooves 58 and the outer ends of these strips fit between ribs 59 on the inner periphery of the housing 12 as shown in FIG. 3.
  • this localized chamber 56a is bounded by a third fibrous strip 60 which, as shown in FIG. 2, spans the gap between the back wall 33 of the housing 12 and an end plate 61 which is bottomed on the end face of the cylinder 44 to define with the cylinder and end head 11, the working chamber of the compressor.
  • the plate 61 is pivotally seated on the hub 32 of the end wall 33 of the housing 12 and an o-ring seal 62 seals the inner periphery of the plate to the hub but accommodates tilting and sliding of the plate on the hub.
  • the plate 61 is spring pressed against the end of the cylinder 44 by a plurality of coil springs 63 seated in pockets defined by ribs 64 projecting from the end wall 33 of the housing 12.
  • the strip 60 is bent over one of these pocket-defining ribs 64 as shown in FIG. 9 and has its end legs seated between opposed ribs 65.
  • the strip 60 is sufficiently resilient so that the plate 61 may tilt or slide away from the cylinder 44 to provide its relief function as more fully hereinafter described.
  • the valve plate 54 To facilitate opening of the reed valve 54 by the compressed refrigerant from the ports 55, the valve plate 54, as shown in FIGS. 5 and 6, has a U-shaped slot 66 isolating a tongue 69 which underlies the embossment forming the groove 50 in the pivot plate 51 that receives the nose 48a of the shoe 48. In this manner, the free end of the reed valve 54 can flex without interference from the embossed portion of the overlying plate.
  • the compressed refrigerant in the localized chamber 56a flows through the strips 57 and 60 into the main space or chamber 56 where it is effective to cooperate with the springs 63 in holding the plate 61 against the cylinder 44.
  • the strips are composed of a fibrous material which will coalesce or wick out the lubricant entrained in the compressed refrigerant.
  • Such materials are optically opaque, synthetic fibers and are known in the trade as synthetic felt composed of nylon, Dacron (trademark) and the like.
  • the felt is porous and is wet by the oil lubricant thereby acting as a demister.
  • the material must be capable of withstanding high temperatures in the order of 400F.
  • the cylinder 44 has a plurality of bleeder holes 550 therethrough downstream from the port holes and just ahead of the tangency seal line as shown in FIGS. 3, 5, and 8. These bleeder holes vent to the chamber 56a any oil trapped at the tangency line.
  • the compressed refrigerant free of lubricant in the chamber 56 flows to the outlet port 20 in the end 11 from which it is discharged.
  • the wicked-out oil drips from the fibrous strips 57 and to the bottom of the housing 12 where, as shown in FIG. 2, it collects in a pond P which is exposed to the pressure of the compressed refrigerant in the chamber 56.
  • the end head 11 is drilled to provide a passageway 68 joining the pond P with the hub 23 behind the seal ring 29b so that oil backed by pressure in the chamber 56 flows from the pond into the hub to lubricate the shaft seal 29 and the bearing 26.
  • the pressured oil flows through the vane slots 37 of the rotor to lubricate the vanes 39 and cylinder wall 45 and also flows into the hub 32 to lubricate the rear bearing 34.
  • the oil is returned to the cavities between the rotor and cylinder, and the moving parts of the compressor are amply lubricated from oil that is separated from the compressed refrigerant and returned to the refrigerant being compressed.
  • a helper spring 69 shown in FIGS. 3 and 7 is provided to rock the cylinder 44 about the pivot nose 48a so as to place a minimum load at the tangency seal line 47.
  • the spring 69 is in the form of a finger or leaf seated in a recess 70 in the outer face of the cylinder 44 and bottomed on a rib 71 of the housing 12. As shown in FIG. 7, the spring 69 extends from the end plate 61 to the mouth 13 of the housing 12. The spring is positioned in spaced relation downstream from the tangency seal line 47 and since the pivot nose 49 is upstream from this tangency seal line 47, the spring will rock the cylinder 44 into contact with the rotor 36 at the tangency line 47.
  • the refrigerant to be compressed enters the inlet port 19 and in operation of the compressor a suction stop valve 72 in the inlet port is unseated from its seat 73 to allow the refrigerant to flow through a screen 74 to an inlet port 75 on the inner face of the end head 11.
  • This port 75 feeds the expanding cavities C and C between the rotor 36 and cylinder 44 thereby drawing the refrigerant into the suction side of the compressor.
  • the valve 72 will not open unless the pressure in the cavities C and C is less than the pressure of the refrigerant being fed to the compressor.
  • the valve is effective to close for maintaining a negative pressure in the expanding cavities C and C
  • the refrigerant is then compressed in the contracting cavities C and C to be discharged through the port holes 55 unseating the reed valve 54 and enters the fibrous strip bounded chamber 56a.
  • the compressed refrigerant is then freed of its oil as it passes through the fibrous strips 57 and 60 into the main chamber 56 and is then discharged through the port in the end head 11.
  • the pressures designated by the arrows in the contracting cavities C and C act on the cylinder 44 causing it to swing about the pivot nose 48a in the direction shown by the arrow A.
  • This swinging of the cylinder 44 will press it against the rotor 36 at the tangency seal line 47 thereby increasing the seal load as the pressures in the contracting cavities C and C increase.
  • the helper spring 69 only maintains a very light sealing load at the tangency seal line 47 and since the pressure developed by the operating compressor increases this load as needed to maintain a seal between the inlet and outlet sides of the compressor, operating friction of the compressor is minimized without loss of sealing capacity.
  • this invention provides a tangency seal rotary fluid pressure apparatus such as a pump, a motor or a compressor which develops its own tangency seal pressure in operation, purges itself of liquid that might cause a lock-up on rapid starting, separates liquid from compressed vapor or gas or lubricates the bearings and other components thereof with the separated liquid.
  • the preferred embodiment of the invention is a rotary sliding vane refrigerant compressor for automotive airconditioning systems which has a free swinging eccentric cylinder guiding the vanes and loaded against the vane carrying rotor at a line of tangency by pressure of the refrigerant being compressed.
  • a tangency seal fluid pressure device of the type having a housing with a fluid inlet and outlet, a rotor rotatably mounted in the housing and means projecting from the rotor acting on fluid between the inlet and outlet, the improvement of a free swinging member in said housing eccentrically enveloping said rotor, guiding said means projecting from the rotor and pressed against the rotor along a line of tangency between the member and rotor by pressures between the rotor and member, said inlet and outlet communicating with the interior of the member on opposite sides of the tangency line.
  • a tangency seal fluid pressure apparatus which comprises a rotor, fixed bearings supporting the rotor, a member enveloping the rotor in eccentric relation therewith and defining expanding and contracting cavities around the rotor, fluid inlet and outlet means communicating with said cavities means carried by the rotor riding on said member through said cavities, said member being sealed relative to the rotor along a line of tangency between the minimum volume contracting and expanding cavities, and a pivot support for said member accommodating swinging of the member in response to pressures in the contracting cavities to increase the sealing pressure between the rotor and enveloping member at the line of tangency contact therebetween.
  • a tangency seal fluid pressure device comprising a housing, a rotor rotatably mounted in the housing, a cylinder swingable in the housing and surrounding the rotor in eccentric spaced relation therewith, members carried by the rotor riding on the inner wall of said cylinder dividing the space between the rotor and cylinder into expanding fluid receiving cavities and contracting fluid expelling cavities, an inlet port in the housing communicating with the expanding cavities, a pivot in the housingfor said cylinder, said pivot being positioned in the housing relative to the contracting cavities so that pressure therein will swing the cylinder into sealing contact with the rotor along the line of tangency separating the expanding and contracting cavities, said cylinder having a discharge opening therethrough immediately upstream from the tangency line of contact with the rotor for discharging the fluid into the housing around the cylinder, and said housing having an outlet port receiving said fluid.
  • a tangency seal rotary vane compressor comprising a housing having an inlet and an outlet, front and rear fixed bearing supports in said housing, bearing in said supports, a shaft rotatably carried by said bearings, a rotor secured on said shaft for corrotation, said rotor having vane slots, vanes slidable in said slots, a cylinder swingable in said housing surrounding said rotor and receiving the ends of the vanes in riding contact therewith, a pivot support for said cylinder in said housing accommodating swinging of the cylinder in response to fluid pressure between the rotor and cylinder for swinging the cylinder into a tangency line contact with the rotor, said cylinder having outlet openings therethrough upstream from said tangency line contact with the rotor, oil separating fibrous material between the housing and cylinder defining with the housing and cylinder a first chamber receiving compressed fluid from said outlet openings, said housing and cylinder defining a second chamber receiving oil-freed fluid and separated oil passed through the fibrous material from said first chamber, said outlet dis
  • a plate in the housing spring-pressed against an end of the cylinder and adapted to be unseated from the cylinder by liquid compressed between the rotor and cylinder for purging the liquid to the sump, and said inlet communicating with the interior of the cylinder dow stream from the tangency line contact between the rotor and cylinder.
  • a self-oil purging rotary vane compressor adapted for compressing refrigerant in automotive airconditioning systems which comprises an end head having an inlet, an outlet, and a bearing supporting hub, a cup-shaped housing piloted on said end head having a bearing supporting hub aligned with the hub of the end head, bearings in the hubs of the end head and housing, a shaft rotatably mounted in said bearings, a vane carrying rotor mounted on said shaft between said bearings, a cylinder in said housing surrounding said rotor in eccentric relation and having one end bottomed on said end head, a plate slidably piloted on the hub of said housing spring-pressed against the other end of said cylinder, a pivot shoe carried by said housing cooperating with the outer periphery of said cylin der accommodating swinging of the cylinder in the housing in response to pressures developed between the rotor and cylinder to load the cylinder against the rotor along a line of tangency, said cylinder having openings therethrough joining the interior
  • pivot support for the member is a shoe cooperating with the outer periphery of the member.
  • the device of claim 3 including a shoe carried by the housing cooperating with the cylinder to form the pivot support therefor.
  • the device of claim 3 including a reed valve on the cylinder controlling flow of fluid from the cxpelling cavities to the housing and a guard plate overlying the reed valve cooperating with a housing carried shoe to form the pivot for the cylinder.
  • the device of claim 3 including a liquid purge valve cooperating with the cylinder to relieve liquid from the cavities to the housing.
  • the apparatus of claim 2 including a helper spring acting on the member enveloping the rotor to rock the member about the pivot support for maintaining a minimum pressure at the line of tangency between the rotor and member.
  • the device of claim 3 having an annular chamber between the housing and the cylinder with fibrous strips isolating a sub-chamber receiving fluid from the discharge opening of the cylinder effective to separate liquid entrained with the compressed fluid.
  • the device of claim 3 including a spring loaded plate engaging one end of the cylinder and adapted to be deflected from said one end to provide a relief pas sage connecting the cavities between the rotor and cylinder with the interior of the housing.
  • pivot support for the cylinder includes a rigid plate bolted to the periphery of the cylinder and having a recess midway between the ends of the cylinder and a shoe carried by the housing seats in said recess.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US421988A 1973-12-05 1973-12-05 Self adjusting tangency-clearance compressor with liquid purge capability Expired - Lifetime US3865515A (en)

Priority Applications (11)

Application Number Priority Date Filing Date Title
US421988A US3865515A (en) 1973-12-05 1973-12-05 Self adjusting tangency-clearance compressor with liquid purge capability
CA213,260A CA1031307A (en) 1973-12-05 1974-11-07 Self-adjusting tangency-clearance compressor with liquid purge capability
GB48913/74A GB1479911A (en) 1973-12-05 1974-11-12 Fluid pressure devices
AU75723/74A AU488203B2 (en) 1973-12-05 1974-11-25 Self-adjusting tangency-clearance compressor with liquid purge capability
BR10023/74A BR7410023A (pt) 1973-12-05 1974-11-29 Aparelho de pressao fluida com vedacao tangencial
FR7439562A FR2253917B1 (enrdf_load_stackoverflow) 1973-12-05 1974-12-03
SU742081921A SU847942A3 (ru) 1973-12-05 1974-12-04 Ротационный пластинчатый компрессор
JP13942874A JPS5442448B2 (enrdf_load_stackoverflow) 1973-12-05 1974-12-04
DE2457319A DE2457319C3 (de) 1973-12-05 1974-12-04 Rotationskolbenmaschine mit Hubeingriff und Schlupfeingriff
ES432604A ES432604A1 (es) 1973-12-05 1974-12-04 Un dispositivo de presion de fluido de cierre de tangencia.
IT30197/74A IT1026801B (it) 1973-12-05 1974-12-05 Apparecchio in particolare compressore con gioco di tagenza con autoregolazione e in grado di spurgare liquido

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US421988A US3865515A (en) 1973-12-05 1973-12-05 Self adjusting tangency-clearance compressor with liquid purge capability

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US3865515A true US3865515A (en) 1975-02-11

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US421988A Expired - Lifetime US3865515A (en) 1973-12-05 1973-12-05 Self adjusting tangency-clearance compressor with liquid purge capability

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US (1) US3865515A (enrdf_load_stackoverflow)
JP (1) JPS5442448B2 (enrdf_load_stackoverflow)
BR (1) BR7410023A (enrdf_load_stackoverflow)
CA (1) CA1031307A (enrdf_load_stackoverflow)
DE (1) DE2457319C3 (enrdf_load_stackoverflow)
ES (1) ES432604A1 (enrdf_load_stackoverflow)
FR (1) FR2253917B1 (enrdf_load_stackoverflow)
GB (1) GB1479911A (enrdf_load_stackoverflow)
IT (1) IT1026801B (enrdf_load_stackoverflow)
SU (1) SU847942A3 (enrdf_load_stackoverflow)

Cited By (18)

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US3988080A (en) * 1974-02-20 1976-10-26 Diesel Kiki Co., Ltd. Rotary vane compressor with outlet pressure biased lubricant
US4255098A (en) * 1977-03-22 1981-03-10 Barmag Barmer Machinenfabrik Aktiengesellschaft Rotary vane pump assembly
US4269576A (en) * 1978-07-29 1981-05-26 Diesel Kiki Co., Ltd. Vane compressor with reticulate or porous separator element and fluid guide means therein
US4340339A (en) * 1979-02-17 1982-07-20 Sankyo Electric Company Limited Scroll type compressor with oil passageways through the housing
US5330335A (en) * 1991-07-31 1994-07-19 Sanden Corporation Horizontally oriented rotary machine having internal lubication oil pump
US5536153A (en) * 1994-06-28 1996-07-16 Edwards; Thomas C. Non-contact vane-type fluid displacement machine with lubricant separator and sump arrangement
US5664941A (en) * 1995-12-22 1997-09-09 Zexel Usa Corporation Bearings for a rotary vane compressor
US6135742A (en) * 1998-08-28 2000-10-24 Cho; Bong-Hyun Eccentric-type vane pump
US20070065326A1 (en) * 2005-09-19 2007-03-22 Orsello Robert J Rotary piston and methods for operating a rotary piston as a pump, compressor and turbine
US20090032315A1 (en) * 2007-08-03 2009-02-05 David Porter Systems for Powering Vehicles using Compressed Air and Vehicles Involving Such Systems
ITBO20110601A1 (it) * 2011-10-25 2013-04-26 D V P Vacuum Technology S R L Pompa a palette per il vuoto a montaggio semplificato e preciso.
CN103925189A (zh) * 2013-01-14 2014-07-16 斯瓦本冶炼厂汽车股份有限公司 用于降低启动扭矩的具有泄压的气泵
US20150132168A1 (en) * 2012-06-04 2015-05-14 Calsonic Kansei Corporation Gas compressor
US20150147216A1 (en) * 2012-08-22 2015-05-28 Calsonic Kansei Corporation Gas compressor
US20150147213A1 (en) * 2012-06-05 2015-05-28 Calsonic Kansel Corporation Gas compressor
CN108397391A (zh) * 2018-01-05 2018-08-14 陈正茂 一种一字滑板式空压机的密封,润滑结构
US20190309752A1 (en) * 2016-07-08 2019-10-10 Nestec S.A. Rotary Compressor Arrangement
US20250250980A1 (en) * 2024-02-05 2025-08-07 Adel K Alsubaih Rotary radial vane compressor

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DE2815471C2 (de) * 1978-04-10 1986-05-07 Robert Bosch Gmbh, 7000 Stuttgart Verdichter, insbesondere Kältemittelverdichter
JPS6088888A (ja) * 1983-10-20 1985-05-18 Mitsubishi Electric Corp 回転式圧縮機のストレ−ナ装置
JPS60252188A (ja) * 1984-05-28 1985-12-12 Hitachi Ltd 可動翼型圧縮機
JPS6159892U (enrdf_load_stackoverflow) * 1984-09-27 1986-04-22
DE102007011792A1 (de) * 2006-10-02 2008-04-03 Robert Bosch Gmbh Förderaggregat
JP6714971B2 (ja) * 2015-02-10 2020-07-01 ナブテスコオートモーティブ株式会社 真空ポンプ

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US2447744A (en) * 1944-04-01 1948-08-24 Gilbert & Barker Mfg Co Pumping unit
US2700341A (en) * 1948-12-24 1955-01-25 Borg Warner Pump arrangement for operating automatic clutches
US3652191A (en) * 1970-06-22 1972-03-28 Trw Inc Compressor
US3743445A (en) * 1970-04-02 1973-07-03 Bosch Gmbh Robert Regulated pump with constant displacement volume

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Publication number Priority date Publication date Assignee Title
US2447744A (en) * 1944-04-01 1948-08-24 Gilbert & Barker Mfg Co Pumping unit
US2700341A (en) * 1948-12-24 1955-01-25 Borg Warner Pump arrangement for operating automatic clutches
US3743445A (en) * 1970-04-02 1973-07-03 Bosch Gmbh Robert Regulated pump with constant displacement volume
US3652191A (en) * 1970-06-22 1972-03-28 Trw Inc Compressor

Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3988080A (en) * 1974-02-20 1976-10-26 Diesel Kiki Co., Ltd. Rotary vane compressor with outlet pressure biased lubricant
US4255098A (en) * 1977-03-22 1981-03-10 Barmag Barmer Machinenfabrik Aktiengesellschaft Rotary vane pump assembly
US4269576A (en) * 1978-07-29 1981-05-26 Diesel Kiki Co., Ltd. Vane compressor with reticulate or porous separator element and fluid guide means therein
US4340339A (en) * 1979-02-17 1982-07-20 Sankyo Electric Company Limited Scroll type compressor with oil passageways through the housing
US5330335A (en) * 1991-07-31 1994-07-19 Sanden Corporation Horizontally oriented rotary machine having internal lubication oil pump
US5536153A (en) * 1994-06-28 1996-07-16 Edwards; Thomas C. Non-contact vane-type fluid displacement machine with lubricant separator and sump arrangement
US5664941A (en) * 1995-12-22 1997-09-09 Zexel Usa Corporation Bearings for a rotary vane compressor
US6135742A (en) * 1998-08-28 2000-10-24 Cho; Bong-Hyun Eccentric-type vane pump
US20070065326A1 (en) * 2005-09-19 2007-03-22 Orsello Robert J Rotary piston and methods for operating a rotary piston as a pump, compressor and turbine
US20090032315A1 (en) * 2007-08-03 2009-02-05 David Porter Systems for Powering Vehicles using Compressed Air and Vehicles Involving Such Systems
ITBO20110601A1 (it) * 2011-10-25 2013-04-26 D V P Vacuum Technology S R L Pompa a palette per il vuoto a montaggio semplificato e preciso.
US20150132168A1 (en) * 2012-06-04 2015-05-14 Calsonic Kansei Corporation Gas compressor
EP2889486A4 (en) * 2012-06-04 2016-03-30 Calsonic Kansei Corp GAS BOOSTERS
US9695818B2 (en) * 2012-06-04 2017-07-04 Calsonic Kansei Corporation Gas compressor
US9771936B2 (en) * 2012-06-05 2017-09-26 Calsonic Kansei Corporation Gas compressor
US20150147213A1 (en) * 2012-06-05 2015-05-28 Calsonic Kansel Corporation Gas compressor
US9695691B2 (en) * 2012-08-22 2017-07-04 Calsonic Kansei Corporation Gas compressor
US20150147216A1 (en) * 2012-08-22 2015-05-28 Calsonic Kansei Corporation Gas compressor
DE102013200410B4 (de) * 2013-01-14 2017-12-07 Schwäbische Hüttenwerke Automotive GmbH Gaspumpe mit Druckentlastung zur Reduzierung des Anfahrdrehmoments
DE102013200410A1 (de) * 2013-01-14 2014-07-17 Schwäbische Hüttenwerke Automotive GmbH Gaspumpe mit Druckentlastung zur Reduzierung des Anfahrdrehmoments
EP2754896A1 (de) * 2013-01-14 2014-07-16 Schwäbische Hüttenwerke Automotive GmbH Gaspumpe mit Druckentlastung zur Reduzierung des Anfahrdrehmoments
CN103925189A (zh) * 2013-01-14 2014-07-16 斯瓦本冶炼厂汽车股份有限公司 用于降低启动扭矩的具有泄压的气泵
CN103925189B (zh) * 2013-01-14 2018-01-19 斯瓦本冶炼厂汽车股份有限公司 用于降低启动扭矩的具有泄压的气泵
EP2754896B1 (de) * 2013-01-14 2018-08-22 Schwäbische Hüttenwerke Automotive GmbH Gaspumpe mit Druckentlastung zur Reduzierung des Anfahrdrehmoments
EP3421802A1 (de) * 2013-01-14 2019-01-02 Schwäbische Hüttenwerke Automotive GmbH Gaspumpe mit druckentlastung zur reduzierung des anfahrdrehmoments
US11506204B2 (en) 2013-01-14 2022-11-22 Schwäbische Hüttenwerke Automotive GmbH Gas pump with pressure relief for reducing the starting torque
US20190309752A1 (en) * 2016-07-08 2019-10-10 Nestec S.A. Rotary Compressor Arrangement
US10876530B2 (en) * 2016-07-08 2020-12-29 Societe Des Produits Nestle S.A. Rotary compressor arrangement
CN108397391A (zh) * 2018-01-05 2018-08-14 陈正茂 一种一字滑板式空压机的密封,润滑结构
US20250250980A1 (en) * 2024-02-05 2025-08-07 Adel K Alsubaih Rotary radial vane compressor

Also Published As

Publication number Publication date
IT1026801B (it) 1978-10-20
FR2253917A1 (enrdf_load_stackoverflow) 1975-07-04
DE2457319C3 (de) 1980-01-17
SU847942A3 (ru) 1981-07-15
GB1479911A (en) 1977-07-13
ES432604A1 (es) 1977-02-16
BR7410023A (pt) 1976-05-25
JPS5442448B2 (enrdf_load_stackoverflow) 1979-12-14
AU7572374A (en) 1976-05-27
CA1031307A (en) 1978-05-16
DE2457319A1 (de) 1975-06-12
FR2253917B1 (enrdf_load_stackoverflow) 1980-11-28
JPS5086706A (enrdf_load_stackoverflow) 1975-07-12
DE2457319B2 (de) 1979-05-17

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