EP1067288A2 - Lager für die Taumelscheibe eines Kompressors - Google Patents

Lager für die Taumelscheibe eines Kompressors Download PDF

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Publication number
EP1067288A2
EP1067288A2 EP00114538A EP00114538A EP1067288A2 EP 1067288 A2 EP1067288 A2 EP 1067288A2 EP 00114538 A EP00114538 A EP 00114538A EP 00114538 A EP00114538 A EP 00114538A EP 1067288 A2 EP1067288 A2 EP 1067288A2
Authority
EP
European Patent Office
Prior art keywords
cam plate
rotor
drive shaft
thrust bearing
variable displacement
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Withdrawn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
EP00114538A
Other languages
English (en)
French (fr)
Inventor
Tetsuhiko c/o K.K. Toyoda Jidoshokki Fukanuma
Masakazu c/o K.K. Toyoda Jidoshokki Murase
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.)
Toyota Industries Corp
Original Assignee
Toyoda Jidoshokki Seisakusho KK
Toyoda Automatic Loom Works Ltd
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 Toyoda Jidoshokki Seisakusho KK, Toyoda Automatic Loom Works Ltd filed Critical Toyoda Jidoshokki Seisakusho KK
Publication of EP1067288A2 publication Critical patent/EP1067288A2/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Withdrawn legal-status Critical Current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
    • 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
    • F04B27/0804—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 rotary cylinder block
    • F04B27/0821—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 rotary cylinder block component parts, details, e.g. valves, sealings, lubrication
    • F04B27/0852—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 rotary cylinder block component parts, details, e.g. valves, sealings, lubrication machine housing
    • F04B27/0856—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 rotary cylinder block component parts, details, e.g. valves, sealings, lubrication machine housing cylinder barrel bearing means
    • 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
    • F04B27/1063—Actuating-element bearing means or driving-axis bearing means
    • 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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • 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
    • F04B27/14—Control

Definitions

  • the present invention relates to a variable displacement compressor for air-conditioning vehicles.
  • Fig. 6 shows such a variable displacement compressor (simply called compressor herein).
  • the compressor of Fig. 6 has a housing 102, which includes a crank chamber 101.
  • a drive shaft 103 is supported by the housing 102 and passes through the crank chamber 101.
  • a lug plate 104 is fixed to the drive shaft 103 in the crank chamber 101.
  • a swash plate 105 slides on the drive shaft 103 and inclines relative to the axis L of the drive shaft 103.
  • a hinge mechanism 106 is located between the lug plate 104 and the swash plate 105.
  • the hinge mechanism 106 includes a guide pin 111 and a support arm 112.
  • the guide pin 111 which is formed on the swash plate 105, includes a spherical portion 111a.
  • the hinge mechanism 106 causes the swash plate 105 to rotate integrally with the drive shaft 103 and permits the swash plate 105 to incline with respect to the drive shaft 103.
  • Cylinder bores 108 are formed in the housing 102. Pistons 107 are accommodated in the corresponding cylinder bores 108. The pistons 107 are coupled to the swash plate 105. Rotation of the drive shaft 103 is converted into reciprocation of the pistons 107 through the hinge mechanism 106 and the swash plate 105. This repeats a cycle of drawing refrigerant gas into the cylinder bores 108, compressing the gas, and discharging the gas from the cylinder bores 108.
  • a thrust bearing 109 is located between the lug plate 104 and an inner wall 102a of the housing 102.
  • the thrust bearing 109 receives a compression force F applied to the lug plate 104 from the pistons 107 through the swash plate 105 and the hinge mechanism 106.
  • the compressor displacement is adjusted by varying the inclination of the swash plate 105.
  • the hinge mechanism 106 permits the inclination of the swash plate 105 to vary, which varies the stroke of the pistons 107, that is, the compressor displacement.
  • the maximum inclination of the swash plate 105 is determined by abutment of the swash plate 105 against the lug plate 104. More specifically, a stop member 110, which is diametrically opposite to the hinge mechanism 106 with respect to the axis L, contacts the lug plate 104.
  • the compression load F is maximized when the compressor displacement is maximized.
  • the compression load F is transmitted from the swash plate 105 to the lug plate 104 through a place of engagement S (the contact point between the spherical portion 111a and the guide hole 112a) and the stop member 110. Accordingly, the compression load F is transmitted to the lug plate 104 at opposite sides of the axis L, which prevents a moment based on the compression load F from inclining the lug plate 104 relative to the drive shaft 103.
  • the stop member 110 When the compressor displacement is less than the maximum displacement, the stop member 110 does not contact the lug plate 104. Accordingly, the compression load F (about the same as that when the displacement is maximized) is transmitted from the swash plate 105 to the lug plate 104 only through the place of engagement S of the hinge mechanism 106. Therefore, the transmission of the compression load F to the lug plate 104 is unbalanced about the axis L.
  • the thrust bearing 109 is annular and receives the compression load F within the radius 11. However, the radius 11 is less than the distance between the place of engagement S and the axis L when the inclination of the swash plate 105 is maximized. Accordingly, the thrust bearing 109 does not receive the compression load F from the place of engagement S within the radius 11 when the swash plate 105 is greatly inclined and the stop member 110 does not contact the lug plate 104.
  • An objective of the present invention is to provide a variable displacement compressor that prevents the inclination of the lug plate when the compressor displacement is less than maximum displacement.
  • a housing includes a housing member and a cylinder block having a cylinder bore.
  • a crank chamber is formed in the housing.
  • a drive shaft is supported by the housing member and the cylinder block. The drive shaft passes through the crank chamber.
  • a piston is accommodated in the cylinder bore formed in the cylinder block.
  • the piston is connected to a cam plate.
  • the cam plate converts rotation of the drive shaft into reciprocation of the piston to cause the piston to perform a gas compression operation.
  • the cam plate inclines with respect to the drive shaft.
  • the displacement of the compressor varies in accordance with the inclination of the cam plate.
  • a rotor is fixed to the drive shaft and located in the crank chamber.
  • a hinge mechanism connects the cam plate to the rotor so that the cam plate is driven by the rotor.
  • the hinge mechanism permits the inclination angle of the cam plate to vary.
  • the position of a place of engagement in the hinge mechanism between the cam plate and the rotor varies according to the inclination of the cam plate.
  • a stop member is connected to the cam plate. The stop member restricts the inclination of the cam plate when the stop member contacts the rotor.
  • An annular thrust bearing is located in the crank chamber between the rotor and the housing member. The thrust bearing receives a compression load acting on the rotor.
  • the compression load results from the compression of gas by the piston.
  • the radius of the outermost force-transmitting points of the thrust bearing is equal to or greater than the radial distance between the place of engagement and the axis of the drive shaft when the inclination angle of the cam plate is maximum.
  • a front housing member 11 is coupled to the front (left in Fig. 1) of a cylinder block 12.
  • a rear housing member 13 is coupled to the rear (right in Fig. 1) of the cylinder block 12 through a valve plate 14.
  • the front housing member 11, the cylinder block 12, and the rear housing member 13 form a compressor housing.
  • a crank chamber 15 is defined between the front housing member 11 and the cylinder block 12.
  • a drive shaft 16 passes through the crank chamber 15 and is supported by the front housing member 11 and the cylinder block 12.
  • a rotor, or lug plate 17 is fixed to the drive shaft 16 in the crank chamber 15.
  • a cam plate, which is a swash plate 18 in this embodiment, is located in the crank chamber 15.
  • the drive shaft 16 passes through a central hole 18a of the swash plate 18.
  • a hinge mechanism 19 is located between the lug plate 17 and the swash plate 18.
  • two guide pins 20 of the hinge mechanism 19 are formed on the front surface of the swash plate 18 and are symmetrical to one another with respect to a plane that includes the axis L and a line D1.
  • the line D1 marks a top dead center location on the swash plate 18.
  • a spherical portion 20a is formed in the distal end of each guide pin 20.
  • Two support arms 21 are formed on the rear surface of the lug plate 17 and are symmetrical to with respect to the previously mentioned plane.
  • a guide hole 21a is formed in the distal end of each support arm 21 as shown in Fig. 1.
  • the spherical portions 20a are received in the corresponding guide holes 21a and engage the cylindrical walls of the guide holes 21a.
  • the spherical portions 20a slide in the corresponding guide holes 21a, and the swash plate 18 is supported by the drive shaft 16 through the central hole 18a. Accordingly, the swash plate 18 slides on the surface of the drive shaft 16 and inclines relative to the drive shaft 16.
  • Cylinder bores 12a are formed in the cylinder block 12 and equally spaced from the axis L at predetermined angular intervals.
  • Each piston 22 includes a head 22a, which is accommodated in the corresponding cylinder bore 12a, and a neck 22b, which is coupled to the periphery of the swash plate 18 through shoes 23. Rotation of the drive shaft 16 is converted into reciprocation of the pistons 22 through the swash plate 18 and the shoes 23.
  • a suction chamber 24 and a discharge chamber 25 are formed in the rear housing member 13, respectively.
  • the valve plate 14 includes suction ports 26, suction valves 27, discharge ports 28, and discharge valves 29.
  • refrigerant gas in the suction chamber 24 is drawn to the cylinder bores 12a through the corresponding suction ports 26 and suction valves 27 by the movement of the pistons 22 from the top dead center to the bottom dead center. Then, movement of the pistons 22 from the bottom dead center to the top dead center compresses the refrigerant gas in the cylinder bores 12a to a certain pressure and discharges the refrigerant gas to the discharge chamber 25 through the corresponding discharge ports 28 and discharge valves 29.
  • a bleed passage 30 connects the crank chamber 15 to the suction chamber 24.
  • a pressurizing passage 31 connects the discharge chamber 25 to the crank chamber 15.
  • a displacement control valve 32 is located in the pressurizing passage 31. The control valve 32 adjusts the opening size of the pressurizing passage 31, which adjusts the flow rate of high-pressure gas from the discharge chamber 25 to the crank chamber 15. The relationship between the flow rate of gas into the crank chamber 15 and the flow rate of gas released from the crank chamber 15 to the suction chamber 24 determines the pressure in the crank chamber 15. When the pressure in the crank chamber 15 is varied, the difference between the pressure in the crank chamber 15 and the pressure in the cylinder bores 12a is varied, which varies the inclination of the swash plate 18 and adjusts the compressor displacement.
  • an annular thrust bearing 61 is located between the lug plate 17 and an inner wall 11a of the front housing member 11.
  • the thrust bearing 61 is centered about the axis L of the drive shaft 16.
  • the thrust bearing 61 receives a compression load F applied from the pistons 22 to the lug plate 17 through the swash plate 18 and the hinge mechanism 19.
  • the thrust bearing 61 includes a rear annular race 62, which is fixed to the lug plate 17, a front annular race 63 fixed to the wall 11a of the front housing member 11, and rollers 64 (only two are shown), which are between the races 62, 63.
  • the rollers 64 are radially arranged about the axis L.
  • the front race 64 rotates relative to the rear race 62 when the lug plate 17 rotates. Accordingly, the rollers 64 rotate about the axis L while the lug plate 17 rotates.
  • the thrust bearing 61 receives the compression load F within the radius 11.
  • the radius 11 is greater than the distance 12, which is between the place of engagement S and the axis L when the swash plate 18 is at the maximum inclination position.
  • the radius 11 corresponds to the radius of a circle drawn by the outermost points of contact between the races 62, 63 and the rollers 64.
  • the stop member 35 does not contact the lug plate 17. Accordingly, the compression load F from the swash plate 18 is applied to the lug plate 17 only through the place of engagement S (the magnitude of the compression load F and the location of the place of engagement S may be considered to be the same as those when the displacement is maximized). Therefore, the compression load F is transmitted to the lug plate 17 in an unbalanced manner with respect to the axis L.
  • the radius 11 of the thrust bearing 61 is greater than the distance 12 between the place of engagement S and the axis L when the inclination of the swash plate 18 is maximized. Even if the compression load F is transmitted to the lug plate 17 only through the place of engagement S when the displacement becomes less than the maximum displacement, the places of engagement S remain within the radius 11. As a result, the lug plate 17 properly receives the compression load F and is not inclined by an inclination moment based on the compression load F. This prevents noise and vibration of the compressor.
  • the swash plate 18 is supported by the drive shaft 16 in a different manner, and the structure of a hinge mechanism 71 is different, compared to the hinge mechanism 19 of the first embodiment.
  • a sleeve 72 slides axially on the drive shaft 16.
  • Two support pins 73 (only one shown) are located on opposite sides of the sleeve 72.
  • the support pins 73 define a pivot axis that is perpendicular to the axis L.
  • the swash plate 18 is supported by the sleeve 72 through the support pins 73, and the inclination of the swash plate 18 varies.
  • a support arm 75 is formed on the rear of the lug plate 17 at a location corresponding to a top dead center line D1 of a swash plate 18.
  • An elongated guide hole 75a passes through the distal end of the support arm 75 in as shown in Fig. 5.
  • a link pin 74 which is located in front of the line D1, engages the guide hole 75a of the support arm 75. The pin 74 is supported by the swash plate 18 as shown in Fig. 5.
  • the guide hole 75a guides the link pin 74.
  • the sleeve 72 supports the swash plate 18 and slides on the drive shaft 16. Accordingly, the swash plate 18 moves axially and inclines with respect to the drive shaft 16.
  • the sleeve 72 moves toward the cylinder block 12, the inclination of the swash plate 18 decreases.
  • the place of engagement S (a line of contact between the link pin 74 and the guide hole 75a as shown in Fig. 5) moves toward the axis L along the guide hole 75a.
  • a front part of the sleeve 72 is a stop member.
  • the radius 11 of the thrust bearing 61 is greater than the distance 12 between the place of engagement S and the axis L when the inclination of the swash plate 18 is maximized as shown in Fig. 5. Accordingly, the present invention has the same operation and advantages as the first embodiment.
  • the guide pins 20 (and the spherical portions 20a) may be fixed to the lug plate 17, and the support arms 21 (and the guide holes 21a) may be formed on the swash plate 18.
  • the link pin 74 may be formed on the lug plate 17, and the support arm 75 (and the guide hole 75a) may be formed on the swash plate 18.
  • only one guide pin 20 (and one spherical portion 20a) and one support arm 21 (and one guide hole 21a) may be employed.
  • At least one of the races 62, 63 may be omitted from the thrust bearing 61.
  • the rollers 64 directly roll on the front surface of the lug plate 17 or the inner wall 11a of the front housing member 11. This reduces the number of parts.
  • the rollers 64 of the thrust bearing 61 may be balls.
  • the thrust bearing is not limited to roller bearing and may be a slide bearing without rollers.
  • the present invention may be applied to a wobble-type variable displacement compressor.
  • a variable displacement compressor that prevents inclination of a lug plate when the displacement is less than the maximum displacement.
  • a thrust bearing 61 is located between the lug plate 17 and the front housing member 11. The thrust bearing 61 is annular and centered on the axis L of the drive shaft 16. The thrust bearing 61 receives a compression load F applied to the lug plate 17 from pistons 22 through a swash plate 18 and a hinge mechanism 19. The radius 11 of the thrust bearing 61 is greater than the distance between the contact point of the hinge mechanism 19 and the axis L of the drive shaft 16 when the inclination of the swash plate 18 is maximized. Therefore, the compression load F is applied within the radius of the thrust bearing, which reduces noise and vibration.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP00114538A 1999-07-07 2000-07-06 Lager für die Taumelscheibe eines Kompressors Withdrawn EP1067288A2 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP11192694A JP2001020858A (ja) 1999-07-07 1999-07-07 可変容量型圧縮機
JP19269499 1999-07-07

Publications (1)

Publication Number Publication Date
EP1067288A2 true EP1067288A2 (de) 2001-01-10

Family

ID=16295505

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00114538A Withdrawn EP1067288A2 (de) 1999-07-07 2000-07-06 Lager für die Taumelscheibe eines Kompressors

Country Status (5)

Country Link
EP (1) EP1067288A2 (de)
JP (1) JP2001020858A (de)
KR (1) KR20010014520A (de)
CN (1) CN1283743A (de)
BR (1) BR0002354A (de)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003065224A (ja) 2001-08-28 2003-03-05 Toyota Industries Corp 可変容量型ピストン式圧縮機
AU2009335645A1 (en) * 2008-12-18 2011-07-14 S.P.M. Flow Control, Inc. Suction port lock nut with stub buttress threads
US9157468B2 (en) 2010-06-04 2015-10-13 S.P.M. Flow Control, Inc. Packing nut lock and method of use
CN102926967B (zh) * 2012-11-23 2015-03-11 上海威乐汽车空调器有限公司 往复式斜盘压缩机结构

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Also Published As

Publication number Publication date
KR20010014520A (ko) 2001-02-26
CN1283743A (zh) 2001-02-14
BR0002354A (pt) 2001-03-13
JP2001020858A (ja) 2001-01-23

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