US3729277A - Adjustable rotary vane tangency compressor - Google Patents

Adjustable rotary vane tangency compressor Download PDF

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Publication number
US3729277A
US3729277A US3729277DA US3729277A US 3729277 A US3729277 A US 3729277A US 3729277D A US3729277D A US 3729277DA US 3729277 A US3729277 A US 3729277A
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United States
Prior art keywords
rotor
end cap
assemblies
compressor
end caps
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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
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English (en)
Inventor
C Allen
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Northrop Grumman Space and Mission Systems Corp
Original Assignee
TRW Inc
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Publication date
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Publication of US3729277A publication Critical patent/US3729277A/en
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Classifications

    • 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
    • F01C21/089—Construction of vanes or vane holders for synchronised movement of the vanes
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/603—Centering; Aligning

Definitions

  • ABSTRACT Gluck Attorney-Hill, Sherman, Meroni, Gross & Simpson [5 7 ABSTRACT A compressor having a closed-ended cylindrical compression chamber with an eccentrically positioned vane carrying rotor received therein and supported by end plates closing the cylinder, wherein the said end plates are pivotably attached to the cylinder by means of pivot pins allowing adjustment of the radial positioning of the rotor within the cylinder to establish zero clearance at the point of tangency after assembly and prior to final tightening, while maintaining the ac tual contact between the rotor and cylinder at the desired line of tangency and a locking means whereby the initial positioning of the rotor relative to the cylinder is assured against change during the operating life 01 the compressor.
  • This invention relates to rotary vane compressors and more particularly to a pivotable attachment between the compressor cylinder end plates and the compressor cylinder.
  • Such compressors normally include a rotatable rotor member carrying radially movable vanes in grooves therein which is positioned interior of a cylindrical member.
  • the cylindrical member is closed at either end by end caps.
  • the rotor is eccentrically positioned within the cylinder and retained in place by the end caps which may include anti-friction bearing assemblies for supporting the rotor axis.
  • the eccentricity of the rotor In order for such compressors to act efficiently, the eccentricity of the rotor must be such that its outer diameter is tangent to the inner diameter of the cylindrical member along a line extending from one end plate to the other. This line of tangency divides the high pressure area from the low pressure area of the compressor chamber and the pressure drop across the line of tangency may be quite great. It is therefore desirable to assemble the compressor with a zero clearance between the rotor and the cylinder wall at the line of tangency or with a clearance which will approach zero as the compressor approaches operating temperatures.
  • This invention is directed to the solution of the above problem by providing a hinged connection between the cylindrical member and the rotor supporting end caps which will allow the members to be assembled together in a loose fit relationship and then pivoted with respect to one another around a pivot point which will assure contact of the rotor at the desired point of tangency.
  • the rotor may be pivoted to the point of tangency after preliminary assembly of the system, and be maintained there at a desired force while the assembly is tightened.
  • a lock member is provided to insure against misalignment after tightening of the assembly. In this manner, normal manufacturing variances in component sizes are accommodated by providing for setting of the tangency contact by a method which does not rely specifically upon low-tolerance fits between the components.
  • FIG. 1 is a cross sectional view of the compressor of this invention
  • FIG. 2 is a transverse cross sectional view of the compressor illustrated in FIG. 1 taken along the lines II-II of FIG. 1;
  • FIG. 3 is a fragmentary longitudinal cross sectional view of the compressor of FIGS. 1 and 2 taken along the lines III-III of FIG. 2;
  • FIG. 4 (on Sheet 1) is a perspective view of the locking member utilized to maintain alignment between the end plates and compressorcylinder;
  • FIG. 5 is a cross sectional view of the compressor of FIG. 1 taken along the lines V-V of FIG. 1 illustrating the end cap and inlet.
  • the compressor as best illustrated in FIG. 1 includes a cup-shaped housing 11 which is partially closed at the open end 12 thereof by an end cap 13 secured thereto by projecting bolt lugs 14 and nuts 15.
  • An internal end cap 16 is disposed within the housing 11 spaced from the bottom thereof, and is attached to the end cap 13 by means of a plurality of circumferentially spaced bolts 17. Entrapped between the end cap 13 and the end cap 16 is an internally cylindrical compression chamber member 18.
  • a central cup-shaped depression 19 in the end cap 16 receives an anti-friction bearing assembly 20 which in turn supports one end 21 of a shaft 22.
  • An anti-friction assembly 23 disposed in a central bore 24 in the end cap 13 provides support for the shaft 22 on the other side of the compression chamber member 18.
  • the end 26 of the shaft' projects out of the end cap 13 through a collar 27 which combines with a seal member 28 to close the bore 24 of the end cap 13.
  • the axis of the shaft 21, as supported by the end caps 13 and 16 is, in the final assembly, offset from the axis of the internally cylindrical compression chamber member 18.
  • the shaft 21 supports a rotor 30 within the compression member 18. The rotor 30 extends from the end cap 13 to the end cap 16 and when the shaft 21 is rotated, the rotor will sealingly engage the side walls of the end caps and rotate therebetween.
  • the rotor 30 has a plurality of circumferentially spaced slots 31 extending thereinto from the circumference 32 thereof and ter minating at a point 33 spaced from the shaft 21.
  • the slots 31, illustrated as being four in number, are equally disposed around the circumference of the rotor.
  • a pair of bores 35 extend from the bottom 33 of the slots 31 and communicate with bores 36 through the shaft 21.
  • the bores 36 communicate the bores 35 of opposed slots 31.
  • Vanes 37 are received in the slots 31 and receive shoes 38 on their outer ends.
  • Blind bores 39 in the bottoms 40 of the vanes 37 are aligned with the bores 35.
  • Pins 42 are received in the blind bores 39 and extend through the bores 35 and 36 into the blind bores 39 of the opposed vane. In this manner, opposed vanes operate as a set.
  • Coil springs 43 are disposed around the pins 42 and bottom against the bottoms 40 of the vanes 37.
  • Portions of the rotor 30 in the area of the slots 31 adjacent the bores 35 are hollowed out as at 35b to accommodate the coil spring 43 when the vane 37 moves outwardly from the slots.
  • the action of the coil springs, entrapped around the pins 42, causes opposed vanes to operate as a unit so that when one of the opposed vanes is forced into its respcc- I tive slot, the other vane is urged outwardly from its slot.
  • the bores pertaining to one set of opposed vanes are spaced from the bores pertaining to the other set of opposed vanes in the 4-vane embodiment illustrated.
  • the rotor 30 is received.
  • the point 48 is known as the point or line of tangency and consists of an axially extending line of contact from end cap to end cap.
  • the location of point 48 is controlled by maintaining the distance B the same on both the compression chamber 18 and the end caps 13 and 16, the dimension B being the distance from the center of the pin 62 to the tangency point 48.
  • the pressure loading area A of the tangency seal 48a is controlled.
  • the vanes 37 project from the outer diameter 45 of the rotor until the shoes 38 are brought into contact with the inner diameter 46 of the member 18 thereby dividing the space between the rotor and the member 18 into four quadrants.
  • the area of each of the quadrants changes as the rotor rotates. As each quadrant approaches the line of tangency, the area encompassed thereby becomes smaller, compressing any fluids entrapped therein.
  • the line of tangency 48 divides the compression chamber into high pressure and low pressure sides.
  • the rotor rotates counter-clockwise and an exit port 49 is placed on the high pressure side of the tangency line 48 adjacent thereto.
  • the area upstream of the line of tangency 48 will contain fluid under considerable pressure during the operation of the compressor while the area immediately downstream or to the low pressure side will have a considerably lower pressure.
  • This invention overcomes this difficulty by providing a hinged connection between the end caps and the cylindrical member.
  • Blind bores 60 are provided in the opposed faces of the end caps at a position circumferentially spaced from the desired tangency point.
  • Complementary blind bores 61 are provided iri the radial thickness of the compressor member 18 at a complementary point.
  • Pins 62 are positioned in the bores 60 and 61 so as to hang the member 18 from the end caps.
  • the compressor is assembled by first assembling the end caps, cylindrical member, rotor and shaft assemblies loosely together with the pins 62 received in the bores 60 and 61. Thereafter, the pivotable connection is moved to bring the outer diameter of the rotor into contact with the wall 46 of the cylinder at the tangency point.
  • tangency seal 48a is illustrated in place along the line of tangency.
  • the seal may be received in a groove which is ported as at 48b to provide a pressure release from the bottom of the groove whereby the seal may be pressure backed against the rotor.
  • the hinge connection allows the setting of a desired preload against this seal at the time of assembly.
  • lands 65 are provided circumferentially around the cylindrical member 18.
  • the lands 65 have grooves 66 therein through which extend the bolts 17.
  • the bolts 17 are received in the grooves 66 with clearance.
  • a locking member 68 is provided for one or more of the-grooves 69 circumferentially spaced from the pivot connections.
  • the locking member 68 is a cylindrical tube having an outer diameter equal to the dimension of the groove 69 so as to be snugly received therein.
  • the ends 70 and 71 of the locking member 68 have bevelled knife edges thereon.
  • the locking member 68 is dimensioned to be axially longer than the space between the opposed faces of the end caps when they are in assembled relationship.
  • the end cap 16 has associated therewith a plurality of increased radial dimensioned bosses 75 thereon, circumferentially spaced from one another to provide bottoming points for the nut heads 76 of the bolts 17. These lands 75 have grooves 78 associated therewith to receive the shank of the bolts 17 with the heads 76 on the outer side thereof.
  • the land 75b adjacent the groove 69 which receives the locking member 68 has its corresponding groove 78b dimensioned smaller than the groove 69 so that the knife edge 70 associated with the locking member will bite into the inner surface of the land 75b of the end cap 16 adjacent the groove 78b when the assembly is tightened together.
  • the opposing knife edge 71 of the locking member 68 will bite into the inner face 80 of the end cap 13 circumferentially around the bolt 17b. In this manner, the positioning of the cylindrical member 18 with respect to the end caps to the desired tangency clearance which is done while the bolts 17 are loose, will be maintained after they have been tightened by the connecting action of the locking member 68.
  • inspection standards may be set to determine if wear has occurred at the tangency line resulting in a pressure loss.
  • the compressor may be partially disassembled and the bolts 17 loosened to where the locking action of the locking member 68 ceases.
  • the end caps and cylindrical member 18 may again be adjusted by moving them with respect to one another at the pivotable connection to obtain a new tangency clearance setting. Thereafter, tightening the assembly will restore it to an operating condition without the heretofore necessary expense of extensive re-machinin g or parts replacement.
  • my invention provides for an improved rotary vane compressor wherein the rotor is supported by end caps pivotably connected to the compressor chamber defining member whereby the rotor may be swung on the pivotable connection with respect to the chamber defining member to provide for precise setting of the tangency line location. and tangency clearance. Further, my invention provides for a locking member to maintain the desired setting.
  • a rotary vane compressor comprising an interiorly cylindrical compressor chamber defining member, a rotor having vanes associated therewith eccentrically received in said member, end caps closing the ends of said member in contact with end walls of said rotor, one of said end caps having a plurality of threaded openings therein radially outwardly from the said rotor, said'openings facing the other of said end caps, the said other of said end caps having a plurality of abutting surfaces aligned with said openings, a plurality of bolts having heads abutting the said abutting surfaces and threaded portions received in the said holes whereby the said bolts may be tightened to enclamp the said member between the said end caps and the said member having grooves in the outer diameter thereof in which the bolts are received to restrict excessive rotation of the said member with respect to the said end caps, hinged connections between the said member and the said end caps, the hinged connections comprising an axially aligned pivot point connection between the said member and each of the said end caps,
  • a rotary vane compressor comprising: a cupshaped housing, a first end cap assembly closing the open end of said housing, a second end cap assembly positioned within said housing, means for fastening said second end cap assembly to said first end cap assembly in spaced-apart relation, a compressor chamber defining member entrapped between said end cap assemblies having an open interior, a rotor supported by said end cap assemblies within said open interior eccentric to said member, a hinge connection between said member and each of said end caps whereby said member may be arcuately moved around said hingeconnection to contact the outer diameter of said rotor, and means for maintaining the said member in position with respect to the said rotor and end caps, said means including a device having knife edges adapted to cut into portions of the said end cap assemblies to lock the said member in position relative to the said end cap assemblies.
  • a constant volume rotary vane compressor comprising: a cup-shaped housing, a first end cap assembly closing the open end of said housing, a second end cap assembly positioned within said housing, means for fastening said second end cap assembly to said first end cap assembly in spaced-apart relation, a compressor chamber defining member entrapped between said end cap assemblies having an open interior, a rotorsupported by said end cap assemblies within said open interior eccentric tosaid member, hinge connections between said member and each of said end cap assemblies whereby said member may be arcuately moved relative to said end cap assemblies around said hinge connections to contact the outer diameter of said rotor to complete an operational constant volume orientation of the member and the rotor:
  • a constantrvolume vane compressor comprising:

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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)
US3729277D 1970-07-15 1970-07-15 Adjustable rotary vane tangency compressor Expired - Lifetime US3729277A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US5501070A 1970-07-15 1970-07-15

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US3729277A true US3729277A (en) 1973-04-24

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US3729277D Expired - Lifetime US3729277A (en) 1970-07-15 1970-07-15 Adjustable rotary vane tangency compressor

Country Status (6)

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US (1) US3729277A (enrdf_load_stackoverflow)
JP (1) JPS52252B1 (enrdf_load_stackoverflow)
CA (1) CA943111A (enrdf_load_stackoverflow)
DE (1) DE2129881A1 (enrdf_load_stackoverflow)
FR (1) FR2101655A5 (enrdf_load_stackoverflow)
GB (1) GB1338772A (enrdf_load_stackoverflow)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3876337A (en) * 1973-03-15 1975-04-08 Varian Associates High vacuum pumping systems
DE2924755A1 (de) * 1979-06-20 1981-01-22 Miele & Cie Verfahren und vorrichtung zum herstellen von blechformteilen in stufenwerkzeugen
WO2012031833A3 (de) * 2010-09-09 2013-01-17 Robert Bosch Gmbh Verfahren zur justierung eines hubrings einer flügelzellenpumpe
US11480173B2 (en) 2019-01-31 2022-10-25 Stackpole International Engineered Products, Ltd. Pressure relief valve integrated in pivot pin of pump

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2700522A1 (de) * 1977-01-07 1978-07-13 Borsig Gmbh Gekapselter rotationskolbenkompressor, insbesondere kaeltekompressor

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2142275A (en) * 1937-08-24 1939-01-03 Eclipse Aviat Corp Fluid pump
US2493525A (en) * 1946-04-10 1950-01-03 Harry J Bush Variable and reversible flow pump
US2552860A (en) * 1945-06-27 1951-05-15 Genevieve R Oliver Fluid power device
FR1183989A (fr) * 1957-10-07 1959-07-16 Blackmer Pump Company Pompe volumétrique à palettes rotatives à débit variable
US3185241A (en) * 1952-02-14 1965-05-25 Case Co J I Fluid drive tractor
US3385513A (en) * 1966-04-11 1968-05-28 Trw Inc Refrigerant vapor compressor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2142275A (en) * 1937-08-24 1939-01-03 Eclipse Aviat Corp Fluid pump
US2552860A (en) * 1945-06-27 1951-05-15 Genevieve R Oliver Fluid power device
US2493525A (en) * 1946-04-10 1950-01-03 Harry J Bush Variable and reversible flow pump
US3185241A (en) * 1952-02-14 1965-05-25 Case Co J I Fluid drive tractor
FR1183989A (fr) * 1957-10-07 1959-07-16 Blackmer Pump Company Pompe volumétrique à palettes rotatives à débit variable
US3385513A (en) * 1966-04-11 1968-05-28 Trw Inc Refrigerant vapor compressor

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3876337A (en) * 1973-03-15 1975-04-08 Varian Associates High vacuum pumping systems
DE2924755A1 (de) * 1979-06-20 1981-01-22 Miele & Cie Verfahren und vorrichtung zum herstellen von blechformteilen in stufenwerkzeugen
WO2012031833A3 (de) * 2010-09-09 2013-01-17 Robert Bosch Gmbh Verfahren zur justierung eines hubrings einer flügelzellenpumpe
US11480173B2 (en) 2019-01-31 2022-10-25 Stackpole International Engineered Products, Ltd. Pressure relief valve integrated in pivot pin of pump

Also Published As

Publication number Publication date
CA943111A (en) 1974-03-05
FR2101655A5 (enrdf_load_stackoverflow) 1972-03-31
GB1338772A (en) 1973-11-28
JPS52252B1 (enrdf_load_stackoverflow) 1977-01-06
DE2129881A1 (de) 1972-01-20

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