EP1291522A1 - Taumelscheibenkompressor mit variablem hubraum - Google Patents

Taumelscheibenkompressor mit variablem hubraum Download PDF

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Publication number
EP1291522A1
EP1291522A1 EP01930053A EP01930053A EP1291522A1 EP 1291522 A1 EP1291522 A1 EP 1291522A1 EP 01930053 A EP01930053 A EP 01930053A EP 01930053 A EP01930053 A EP 01930053A EP 1291522 A1 EP1291522 A1 EP 1291522A1
Authority
EP
European Patent Office
Prior art keywords
swash
swash plate
plate
rotational
center
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP01930053A
Other languages
English (en)
French (fr)
Other versions
EP1291522A4 (de
Inventor
Hiroyuki Zexel Valeo Climate Control Corp. ISHIDA
Takeo Zexel Valeo Climate Control Corp. MIZUSHIMA
Hiromichi Zexel Valeo Climate Control Corp TANABE
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.)
Valeo Thermal Systems Japan Corp
Original Assignee
Zexel Valeo Climate Control Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Zexel Valeo Climate Control Corp filed Critical Zexel Valeo Climate Control Corp
Publication of EP1291522A1 publication Critical patent/EP1291522A1/de
Publication of EP1291522A4 publication Critical patent/EP1291522A4/de
Withdrawn legal-status Critical Current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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1072—Pivot mechanisms

Definitions

  • This invention relates to a variable capacity swash plate compressor which has its delivery quantity changed by variation of the stroke length of each piston occurring according to an angle of inclination of a swash plate.
  • FIG. 6 is a cross-sectional view of a shaft and components associated therewith of a conventional variable-capacity swash plate compressor.
  • the shaft 105 has a thrust flange 140 rigidly fixed thereto, and a swash plate 110 mounted thereon via a hinge ball 109.
  • the hinge ball 109 is mounted in a manner slidable along the shaft 105, and restricts the inclination of the swash plate 11 with respect to the shaft 105.
  • the thrust flange 140 and the swash plate 110 are connected by a linkage 142 via which the rotation of the shaft 105 is transmitted from the thrust flange 140 to the swash plate 110.
  • the piston 107 is connected to the swash plate 110 via a pair of shoes 111 relatively rotating on the sliding surfaces of the swash plate 110, and performs linear reciprocating motion within a cylinder bore (not shown) according to the rotation of the swash plate 110.
  • variable capacity swash plate compressor in response to a change in pressure in a crankcase 108 accommodating the swash plate 110, the angle of inclination of the swash plate 110 is changed, whereby the stroke length of the piston 107 is changed.
  • the swash plate 110 is inclined about the center 01 of the hinge ball 109, and hence the position of the center of gravity O3 of the swash plate 110 is changed with respect to the shaft 105.
  • FIG. 7 is a diagram useful in explaining the static imbalance of a swash plate with respect to the angle of inclination of the swash plate.
  • Static imbalance occurs in a rotary member (swash plate 110 or thrust flange 140) rotating about the shaft 105.
  • the amount of static imbalance is represented by the product (kg ⁇ cm) of a mass (kg) of the swash plate 110 (thrust flange 140) and the distance (cm) from the shaft 105 to the center of gravity of the swash plate 110 (thrust flange 140).
  • a, b, c, d, and e represent a static imbalance of the thrust flange, a static imbalance of the whole rotational assembly, a static imbalance occurring when the center of the hinge ball is positioned toward the front side with respect to the center of a plate portion of the swash plate, a static imbalance of the center of the hinge ball, and a static imbalance of the swash plate, respectively.
  • the angle of inclination of the thrust flange 140 is not varied, and hence the thrust flange has a fixed amount of static imbalance (see straight line e).
  • the angle of inclination of the swash plate 110 is changed, and hence the swash plate 110 has an amount of imbalance which varies at a fixed rate (see straight line b).
  • the sum of the amounts of static imbalance of the two members is the amount of the static imbalance of the whole rotational assembly (see straight line b).
  • FIG. 8 is a diagram useful for explaining the position of center of gravity of a swash plate.
  • A1, A2, B1, and B2 represent positions of center of gravity
  • Amax represents an amount of displacement of the position of center of gravity of the swash plate in the direction of the Y axis during the maximum stroke
  • Amin represents an amount of displacement of the swash plate in the direction of the Y axis during the minimum stroke
  • Bmax represents an amount of displacement of the position of center of gravity of the swash plate in the direction of the Y axis during the maximum stroke when a weight is added to the rear side
  • Bmin represents an amount of displacement of the swash plate in the direction of the Y axis during the minimum stroke when the weight is added to the rear side.
  • variable capacity swash plate compressor In the variable capacity swash plate compressor, a weight (extra thickness) is added to the front side of the swash plate 110 to strike the balance with the inertial force. This weight increases as the compressor becomes faster.
  • the increased rotational speed of the compressor can be coped with by adding the weight to the front side of the swash plate 110, the rotation-related first-order vibration becomes large, which causes the vehicle to produce larger vibration and noise. Therefore, conventionally, a weight 112 is also added to the rear side of the swash plate 110 to thereby make the position of center of gravity of the swash plate 110 closer to the center O1 of the hinge ball (see FIG. 6).
  • the present invention provides a variable capacity swash plate compressor including a rotational member fixed to a shaft and rotating in unison with the shaft, a swash rotational plate connected to the rotational member via a linkage and rotating in unison with the rotational member according to rotation thereof, an angle-limiting member slidably mounted on the shaft, for limiting an angle of the swash rotational plate with respect to the shaft, and a piston connected to the swash rotational plate via shoes relatively rotating on sliding surfaces of the swash rotational plate, and performing linear reciprocating motion within a cylinder bore according to rotation of the swash rotational plate, wherein the angle of inclination of the swash rotational plate changes according to a change in pressure in a crankcase within which the swash rotational plate is received, to thereby change a length of stroke of the piston, characterized in that a center of the angle-limiting member is positioned toward a front side with respect to a center of a plate portion of the swash rotational plate
  • the center of the angle-limiting member is positioned toward the front side with respect to the center of the plate portion of the swash rotational plate, the center of the angle-limiting member is made closer to the center of gravity of the swash plate, whereby the distance from the center of the angle-limiting member to the center of gravity of the swash plate is reduced. Therefore, the center of the angle-limiting member becomes closer to the center of gravity of the swash rotational plate, which reduces the amount of static imbalance.
  • the center of the angle-limiting member is made coincident with a center of gravity of the swash rotational plate.
  • the center of the angle-limiting member is made coincident with the center of gravity of the swash rotational plate, the amount of static imbalance is reduced to zero. Therefore, the mass of the rotational member can be reduced, whereby the weight of the compressor can be further reduced.
  • the present invention provides a variable capacity swash plate compressor including a rotational member fixed to a shaft and rotating in unison with the shaft, a swash rotational plate connected to the rotational member via a linkage and rotating in unison with the rotational member according to rotation thereof, a shaft insertion central hole formed through the swash rotational plate, and having the shaft extending therethrough, the shaft insertion central hole limiting an angle of the swash rotational plate with respect to the shaft, and a piston connected to the swash rotational plate via shoes relatively rotating on sliding surfaces of the swash rotational plate, and performing linear reciprocating motion within a cylinder bore according to rotation of the swash rotational plate, wherein the angle of inclination of the swash rotational plate changes according to a change in pressure in a crankcase within which the swash rotational plate is received, to thereby change a length of stroke of the piston, characterized in that a center of a circle formed by an edge line of the shaft insertion central hole is positioned toward
  • the center of the angle-limiting member Since the center of the circle formed by the edge line of the shaft insertion central hole is positioned toward the front side with respect to the center of the plate portion of the swash rotational plate, the center of the angle-limiting member is made closer to the center of gravity of the swash plate, whereby the distance from the center of the angle-limiting member to the center of gravity of the swash plate is reduced. Therefore, the center of the angle-limiting member becomes closer to the center of gravity of the swash rotational plate, which reduces the amount of static imbalance.
  • the center of the circle formed by the edge line of the shaft insertion central hole is made coincident with a center of gravity of the swash rotational plate.
  • FIG. 1 is a longitudinal cross-sectional view of a variable capacity swash plate compressor according to a first embodiment of the invention
  • FIG. 2 is a diagram useful in explaining the position of center of gravity of a swash plate.
  • A1, A2, D1, and D2 represent positions of center of gravity
  • Amax represents an amount of displacement of the position of center of gravity of the swash plate 10 in the direction of the Y axis during the maximum stroke
  • Amin represents an amount of displacement of the swash plate 10 in the direction of the Y axis during the minimum stroke
  • Dmax represents an amount of displacement of the position of center of gravity of the swash plate 10 in the direction of the Y axis during the maximum stroke when the center O1 of a hinge ball 9 is positioned toward the front side with respect to the center O2 of a plate portion 10c of the swash plate
  • Dmin represents an amount of displacement of the swash plate 10 in the direction of the Y axis during the minimum stroke when the center O1 of the hinge ball 9 is positioned toward the front side with respect to the center O2 of the plate portion 10c of the swash plate 10.
  • variable capacity swash plate compressor has a cylinder block 1 having one end thereof secured to a rear head 3 via a valve plate 2 and the other end thereof secured to a front head 4.
  • the cylinder block 1 has a plurality of cylinder bores 6 axially extending therethrough at predetermined circumferential intervals about the shaft 5.
  • Each cylinder bore 6 has a piston 7 received therein.
  • a pair of shoes 11 are slidably supported at one end of the piston 7.
  • the periphery of the swash plate 10 enters between the shoes 11, and respective flat portions of the shoes 11 are in contact with the sliding surfaces 10a, 10b of the swash plate 10.
  • the front head 4 defines therein a crankcase 8 in which is received the swash plate (swash rotational plate) 10 which rotates about the hinge ball (angle-limiting member) 9 in a manner interlocked with rotation of the shaft 5.
  • the hinge ball 9 is slidably mounted on the shaft 5, and limits the angle of inclination of the swash plate 10 with respect to the shaft 5.
  • the center O1 of the hinge ball 9 is positioned toward the front side with respect to the center O2 of the plate portion 10c of the swash plate 10. At this time, between Amax, Amin, Bmax, Bmin, Dmax, and Dmin, there is a relationship defined as (Amax - Amin) > (Bmax - Bmin) > (Dmax - Dmin) (see FIG. 2 and 7).
  • a discharge chamber 12 Within the rear head 3, there are formed a discharge chamber 12, and a suction chamber located around the discharge chamber 12.
  • the valve plate 2 is formed with refrigerant outlet ports 16 each for communicating between a compression chamber 6a of a cylinder bore 6 and the discharge chamber 12, and refrigerant inlet ports 15 each for communicating between a compression chamber 6a of a cylinder bore 6 and the suction chamber 13.
  • the refrigerant outlet ports 16 and the refrigerant inlet ports 15 are arranged at predetermined circumferential intervals.
  • the refrigerant outlet ports 16 are opened and closed by respective discharge valves 17.
  • the discharge valves 17 are fixed to a rear head-side end face of the valve plate 2 by a bolt 19 together with a valve stopper 18.
  • the refrigerant inlet ports 15 are opened and closed by respective suction valves 21 arranged between the valve plate 2 and the cylinder block 1.
  • the shaft 5 has a rear-side end thereof supported by a radial bearing 24 and a thrust bearing 25 and a front-side end thereof supported by a radial bearing 26.
  • a pressure control valve 32 arranged in an intermediate portion of a communication passage 31 communicating between the discharge chamber 12 and the crankcase 8 controls pressure in the discharge chamber 12 and pressure in the crankcase 8.
  • the shaft 5 has a thrust flange (rotational member) 40 fixed thereto, and the swash plate 10 mounted thereon via the hinge ball 9.
  • the hinge ball 9 is slidably fitted on the shaft 5.
  • the thrust flange 40 and the swash plate 10 are connected by a linkage 42, and rotation of the shaft 5 is transmitted from the thrust flange 40 to the swash plate 10 via the linkage 42.
  • a coil spring 51 is fitted between the hinge ball 9 and the thrust flange 40.
  • the coil spring 51 urges the hinge ball 9 toward the cylinder block side so as to decrease the angle of inclination of the swash plate 10.
  • variable capacity swash plate compressor constructed as above
  • the swash plate 10 performs rotating motion about the hinge ball 9 in unison with the thrust flange 40 according to rotation of the thrust flange 40.
  • the rotating motion of the swash plate 10 is transmitted via the shoes 11 to the piston 7, and converted to linear reciprocating motion of the piston 7.
  • the volume of a compression chamber 6a within the cylinder bore 6 changes, which causes suction, compression and delivery of refrigerant gas to be sequentially carried out, whereby the refrigerant gas is delivered in an amount corresponding to the angle of inclination of the swash plate 10.
  • the corresponding suction valve 21 opens to draw low-pressure refrigerant gas from the suction chamber 13 into the compression chamber 6a within the cylinder bore 6.
  • the corresponding discharge valve 17 opens to deliver high-pressure refrigerant gas from the compression chamber 6a to the discharge chamber 12.
  • the stroke length of the piston 7 is increased to increase the delivery quantity of the compressor.
  • the center O1 of the hinge ball 9 is close to the center of gravity O3 of the swash plate 10, and hence the amount of static imbalance becomes smaller, which makes it possible to suppress generation of vibrations and noise of the vehicle during high-speed rotation of the compressor without increasing the weight of the swash plate 10 (compressor), and adjust the amount of static imbalance more easily than by adding a weight to the rear side of the swash plate 10 to make the position of center of gravity of the same closer to the center of the hinge ball.
  • FIG. 3 is a diagram useful in explaining the center Of gravity of a swash plate.
  • This diagram shows a case in which when the center O1 of the hinge ball 9 is positioned toward the front side with respect to the center O2 of the plate portion 10c of the swash plate 10, the center O1 of the hinge ball 9 is made coincident with the center of gravity O3 of the swash plate 10.
  • the amount of static imbalance is reduced to zero, the mass of the thrust flange 40 can be reduced, whereby the weight of the variable capacity swash plate compressor can be further reduced.
  • the invention is applied to a variable capacity swash plate compressor which uses the hinge ball 9, this is not limitative, but it may be applied to a variable capacity swash plate compressor which does not use the hinge ball 9.
  • FIG. 4 is a longitudinal cross-sectional view of a variable capacity swash plate compressor according to a second embodiment of the invention, and component parts identical to those of the first embodiment are designated by the same reference numerals and description thereof will be omitted.
  • This embodiment is distinguished from the first embodiment in that an angle-limiting member is formed by a slider 59 which is axially slidable on the shaft 5 and a pin 58 perpendicular to the axial direction of the slider 59.
  • the swash plate 60 is made variable in the angle of inclination thereof by the slider 59 and the pin 58, and a through hole 61 limits the angle of inclination of the swash plate 60 with respect to the shaft 5.
  • the center O1 of the slider 59 is positioned toward the front side with respect to the center O2 of a plate portion 60a of the swash plate 60.
  • FIG. 5 is a longitudinal cross-sectional view of a variable capacity swash plate compressor according to a third embodiment of the invention, and component parts identical to those of the first embodiment are designated by the same reference numerals and description thereof will be omitted.
  • This embodiment is distinguished from the first embodiment in that an angle-limiting member is formed by a shaft insertion central hole 81 formed through a swash plate 80.
  • the shaft insertion central hole 81 limits the angle of inclination of the swash plate 80 with respect to the shaft 5.
  • the shaft insertion central hole 81 is restricted in diameter at a center of the plate portion 80a of the swash plate 80, and increased toward the front side and the rear side.
  • the center 01 of a circle formed by an edge line 81a of the shaft insertion central hole 81 is positioned toward the front side with respect to the center O2 of the plate portion 80a of the swash plate 80.
  • the amount of static imbalance can be reduced to zero to thereby reduce the weight of the thrust flange 40, whereby the weight of the variable capacity swash plate compressor can be further reduced.
  • variable capacity swash plate compressors in which the swash plates 10, 60, and 80 rotate in unison with the shaft 5
  • this is not limitative, but the invention can be applied to other compressors, such as a wobble plate compressor.
  • the wobble plate corresponds to the swash rotational plate of the present invention.
  • variable capacity swash plate compressor is useful as a refrigerant compressor for an air conditioner installed on a vehicle, such as a passenger car, a bus or a truck, and particularly suitable for an air conditioner which controls the delivery quantity of refrigerant gas according to the demanded degree of cooling capacity.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP01930053A 2000-06-07 2001-05-11 Taumelscheibenkompressor mit variablem hubraum Withdrawn EP1291522A4 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2000170659 2000-06-07
JP2000170659A JP4565367B2 (ja) 2000-06-07 2000-06-07 可変容量型斜板式圧縮機
PCT/JP2001/003927 WO2001094785A1 (fr) 2000-06-07 2001-05-11 Compresseur a cylindree variable de type a plateau oscillant

Publications (2)

Publication Number Publication Date
EP1291522A1 true EP1291522A1 (de) 2003-03-12
EP1291522A4 EP1291522A4 (de) 2003-10-15

Family

ID=18673343

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01930053A Withdrawn EP1291522A4 (de) 2000-06-07 2001-05-11 Taumelscheibenkompressor mit variablem hubraum

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Country Link
US (1) US20030136256A1 (de)
EP (1) EP1291522A4 (de)
JP (1) JP4565367B2 (de)
WO (1) WO2001094785A1 (de)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4794274B2 (ja) * 2005-10-27 2011-10-19 カルソニックカンセイ株式会社 可変容量圧縮機
KR20090118513A (ko) * 2008-05-14 2009-11-18 학교법인 두원학원 사판식 압축기

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0282190A1 (de) * 1987-02-19 1988-09-14 Sanden Corporation Taumelscheibenverdichter
EP0740076A2 (de) * 1995-04-13 1996-10-30 Calsonic Corporation Schiefscheibenverdichter mit veränderlicher Verdrängung
FR2760793A1 (fr) * 1997-02-28 1998-09-18 Toyoda Automatic Loom Works Compresseur a refrigerant pour conditionnement d'air de vehicule, a capacite variable
DE19911635A1 (de) * 1998-03-18 1999-10-14 Toyoda Automatic Loom Works Verdichter mit veränderlichem Verdrängungsvolumen

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2451380C2 (de) * 1974-10-29 1985-08-14 Linde Ag, 6200 Wiesbaden Einstellbarer Axialkolbenmotor mit einem Schwenkflügelstellantrieb
JP2892718B2 (ja) * 1989-11-17 1999-05-17 株式会社日立製作所 可変容量形圧縮機
US5055004A (en) * 1990-05-23 1991-10-08 General Motors Corporation Stroke control assembly for a variable displacement compressor
JP3417652B2 (ja) * 1994-04-21 2003-06-16 株式会社豊田自動織機 容量可変型斜板式圧縮機
US6368073B1 (en) * 1997-05-26 2002-04-09 Zexel Corporation Swash plate compressor
EP1172556A3 (de) * 2000-07-14 2004-05-12 Kabushiki Kaisha Toyota Jidoshokki Kolbenschuhanordnung in einem Taumelscheibenkompressor
JP2002147348A (ja) * 2000-11-08 2002-05-22 Sanden Corp 容量可変型斜板式圧縮機
WO2005124314A1 (ja) * 2004-06-21 2005-12-29 The Chugoku Electric Power Co., Inc. クリープ余寿命の評価方法

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0282190A1 (de) * 1987-02-19 1988-09-14 Sanden Corporation Taumelscheibenverdichter
EP0740076A2 (de) * 1995-04-13 1996-10-30 Calsonic Corporation Schiefscheibenverdichter mit veränderlicher Verdrängung
FR2760793A1 (fr) * 1997-02-28 1998-09-18 Toyoda Automatic Loom Works Compresseur a refrigerant pour conditionnement d'air de vehicule, a capacite variable
DE19911635A1 (de) * 1998-03-18 1999-10-14 Toyoda Automatic Loom Works Verdichter mit veränderlichem Verdrängungsvolumen

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO0194785A1 *

Also Published As

Publication number Publication date
JP2001349274A (ja) 2001-12-21
WO2001094785A1 (fr) 2001-12-13
EP1291522A4 (de) 2003-10-15
US20030136256A1 (en) 2003-07-24
JP4565367B2 (ja) 2010-10-20

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