EP2063121A1 - Verdichter mit variabler verdrängung - Google Patents

Verdichter mit variabler verdrängung Download PDF

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Publication number
EP2063121A1
EP2063121A1 EP07806954A EP07806954A EP2063121A1 EP 2063121 A1 EP2063121 A1 EP 2063121A1 EP 07806954 A EP07806954 A EP 07806954A EP 07806954 A EP07806954 A EP 07806954A EP 2063121 A1 EP2063121 A1 EP 2063121A1
Authority
EP
European Patent Office
Prior art keywords
arm
swash plate
tilting member
drive shaft
pin
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Withdrawn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
EP07806954A
Other languages
English (en)
French (fr)
Inventor
Hiroyuki Makishima
Nobuyuki Kobayashi
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.)
Marelli Corp
Original Assignee
Calsonic Kansei 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 Calsonic Kansei Corp filed Critical Calsonic Kansei Corp
Publication of EP2063121A1 publication Critical patent/EP2063121A1/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Withdrawn legal-status Critical Current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
    • 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
    • F04B25/00—Multi-stage pumps
    • F04B25/04—Multi-stage pumps having cylinders coaxial with, or parallel or inclined to, main shaft axis

Definitions

  • the present invention relates to a variable capacity compressor equipped with a hinge mechanism which is rotatable while transmitting a rotational torque.
  • variable capacity compressor includes, as shown in Figs. 11 to 13 , a drive shaft 105, a rotor 103 fixed to the drive shaft 105 to rotate with the drive shaft, a swash plate 101 (a cam plate) slidably attached to the drive shaft 105, and pistons (not shown) reciprocatably accommodated in cylinder bores (not shown) and engaged with the swash plate 101.
  • the discharge capacity can be changed by changing the piston stroke while changing the inclination angle of the swash plate 101.
  • a hinge mechanism is provided between the rotor 103 and the swash plate 101 to change the inclination angle of the swash plate while transmitting torque from the rotor 103 to the swash plate 101.
  • the hinge mechanism includes an arm 104 of the rotor projected towards the swash plate 101 from the rotor 103, and an arm 102 of the swash plate projected towards the rotor 103 from the swash plate 101.
  • the arm 104 of the rotor and the arm 102 of the swash plate are overlapped with each other in the rotational direction, so that rotation of the rotor 103 which rotates with the drive shaft 105 is transmitted to the swash plate 101.
  • An axial-load receiving surface 106 is provided in a base portion of the arm 104 of the rotor and receives a compressive reaction (axial load) which is applied from the pistons to the swash plate 101.
  • the receiving surface 106 has a function to guide a change of the inclination angle of the swash plate 101 while being in slide contact with the arm 102 of the swash plate.
  • a position where the compressive reaction Fp from the piston is maximum is located off a position TDC in the swash plate 101 corresponding to the top dead center and located anterior to the position TDC corresponding to the top dead center in the rotational direction. Therefore, the compressive reaction Fp is not symmetrically applied to the swash plate 101 with respect to a line C passing through the position TDC in the swash plate 101 corresponding to the top dead center and a position BDC of the swash plate 101 corresponding to a bottom dead center, so that a twisting force Fn is applied to the swash plate 101 as shown in Fig. 13 .
  • the swash plate 24 thus is inclined about the line C and twisted.
  • the present invention is developed in view of such a conventional art, and an object of the present invention is to provide a variable capacity compressor capable of reducing a sliding resistance between an arm of a swash plate and an arm of a rotor by preventing the swash plate from being twisted.
  • the present invention is a variable capacity compressor including: a drive shaft; a rotation member fixed to the drive shaft to rotate with the drive shaft; a tilting member attached to the drive shaft to be slidable along an axial direction of the drive shaft and inclinable with respect to the drive shaft; a hinge mechanism configured to transmit a rotational torque of the rotation member to the tilting member while allowing the inclination of the tilting member to change; and pistons each configured to reciprocate in respective cylinder bores in response to rotation of the tilting member, the hinge mechanism includes: an arm of the rotation member protruded towards the tilting member from the rotation member; an arm of the tilting member protruded towards the rotation member from the tilting member and configured to receive the rotational torque from the arm of the rotation member; a pin provided at one of the arm of the rotation member and the arm of the tilting member; and an axial-load receiving surface provided on the other of the arm of the rotation member and the arm of the tilting member and configured to contact with the pin so as to receive an axial load produced
  • variable capacity compressor and a hinge mechanism thereof according to the present invention will be described with reference to the drawings.
  • Fig. 1 shows the maximum stroke position
  • Fig. 2 shows the minimum stroke position.
  • the variable capacity compressor 1 includes a cylinder block 2 having a plurality (six in this embodiment) of cylinder bores 3 arranged in the circumferential direction at a interval, a front housing 4 joined to a front end of the cylinder block 2 and forming a crank chamber 5 therein, and a rear housing 6 joined to a rear end of the cylinder block 2 with a valve plate 9 therebetween and forming a suction chamber 7 and a discharge chamber 8 therein.
  • the cylinder block 2, the front housing 4, and the rear housing 6 are fastened to each other by through bolts B.
  • the valve plate 9 is formed with suction holes 11 connecting and communicating the cylinder bore 3 and the suction chamber 7 and discharge holes 12 connecting and communicating the cylinder bores 3 and the discharge chamber 8.
  • a valve system (not shown) is provided on the cylinder block side of the valve plate 9 to open and close the suction holes 11.
  • a valve system (not shown) is provided on the rear housing side of the valve plate 9 to open and close the discharge holes 12.
  • a drive shaft 10 is rotatably supported by bearings 17, 18 provided in bearing holes 19 and 20 at the center of the cylinder block 2 and the front housing 4, so that the drive shaft 10 is rotatable in the crank chamber 5.
  • the crank chamber 5 accommodates therein a rotor 21 as a “rotation member” fixed to the drive shaft 10 and a swash plate 24 as a “tilting member” attached to the drive shaft 10.
  • the swash plate 24 includes a hub 25 attached to the drive shaft 10 so as to be slidable along the axis of the drive shaft and tiltable with respect to the axis of the drive shaft, and a swash plate body 26 fixed to a boss portion of the hub 25.
  • Each piston 29 is slidably accommodated in each cylinder bore 3 and is connected with the swash plate body 26 of the swash plate 24 through a pair of hemispherical piston shoes 30.
  • a hinge mechanism 40 is provided between the rotor 21 as a rotation member and the hub 25 of the swash plate 24 as a tilting member such that rotation of the rotor 21 is transmitted to the swash plate 24, permitting the inclination of the swash plate 24 to change.
  • the rotor 21 rotates with the drive shaft 10, and rotation of the rotor 21 is transmitted to the swash plate 24 via the hinge mechanism 40.
  • the rotation of the swash plate 24 is converted into reciprocation of the pistons 29 via a pair of piston shoes 30 so that the pistons 29 reciprocate in the cylinder bores 3.
  • the variable capacity compressor is provided with a pressure-control mechanism, to adjust a pressure difference (pressure balance) between a crank chamber pressure Pc in back of the pistons 29, and a suction chamber pressure Ps in front of the pistons 29 to change the inclination of the swash plate 24.
  • the pressure-control mechanism includes a gas extraction passage (not shown) which connects and communicates the crank chamber 5 and the suction chamber 7, a gas supply passage (not shown) which connects and communicates the crank chamber 5 and the discharge chamber 8, and the control valve 33 which is disposed in the midstream of the gas supply passage to open and close the gas supply passage.
  • Fig. 3 is a side view of the maximum stroke state of the assembly of the drive shaft, the swash plate and the rotor
  • Fig. 4 is a side view of the minimum stroke state of the assembly
  • Fig. 5 is a perspective view of the maximum stroke state of the assembly
  • Fig. 6 is a view of the assembly without the swash plate body as seen along the arrow VI in Fig. 3 .
  • the hinge mechanism 40 includes an arm 41 which is protruded towards the hub 25 from the rotor 21, and an arm 43 which is protruded towards the rotor 21 from the hub 25.
  • the arm 41 of the rotor and the arm 43 of the hub overlap with each other in the rotational torque transmitting direction Ft (a direction tangent to the rotational direction of the drive shaft 10), and thereby, the rotational torque of the rotor 21 is transmitted to the swash plate 24.
  • Ft a direction tangent to the rotational direction of the drive shaft 10
  • the arm 41 of the rotor has a slit 41s extending in the axial direction XY (a direction perpendicular to the rotation torque transmitting direction Ft) and is formed a fork shape.
  • the arm 43 of the swash plate is slidably fit in the slit 41s (that is, between a pair of arms 41 a and 41 b) in a sandwich manner.
  • the arm 43 of the swash plate is also formed in a fork shape.
  • a compressive reaction (axial load Fp) is applied to the swash plate 24 from the pistons 29.
  • the compressive reaction Fp is received at a contact between a pin 51 which is press fit in a hole formed in the arm 43 of the swash plate 24 and the axial-load receiving surfaces 53a and 53b formed at the tips of the arms 41a, 41b of the rotor 21.
  • the pin 51 extends in a direction tangent to the rotational direction of the rotator 21 and the swash plate 24. That is, the pin 51 extends towards the rotational torque transmitting direction Ft.
  • These axial-load receiving surfaces 53a and 53b has a function to guide a change of the inclination of the swash plate. Therefore, when the inclination of the swash plate 24 is changed, the axial load Fp (compressive reaction from a piston) is applied between the pin 51 and the axial-load receiving surfaces 53a and 53b.
  • the position where the compressive reaction FP becomes more intense in the range of 27 to 90 degrees was found to be located within the range ⁇ of 27 to 37 degrees anterior, in the rotational direction R, to the position TDC of the swash plate corresponding to the top dead center, with a parameter of the rotation speed (see Figs. 7 and 9 ).
  • the suction pressure is in a range of 0.26 to 0.51 Mpa
  • the discharge pressure is in a range of 3.16 to 1.12 Mpa.
  • theoretical pressure peak in the cylinder bore pressure peak occurs when the discharge valve starts to open
  • Fig. 7 is a graph of theoretical pressure curves in the cylinder bore when the discharge pressure Pd is the upper limit of 3.16Mpa
  • Fig. 8 is a graph of theoretical pressure curves in the cylinder bore when the discharge pressure Pd is the lower limit of 1.12Mpa.
  • the position where the compressive reaction Fp from the piston 29 is maximum was found to be located within the range of 27 to 90 degrees anterior, in the rotational direction, to the position TDC of the swash plate 24 corresponding to the top dead center.
  • the pressure difference between the discharge pressure and the suction pressure is maximum (that is, when the discharge pressure is 3.16 Mpa and the suction pressure is 0.26 Mpa)
  • the compressive reaction FP is most intense in the range of 27 to 90 degrees.
  • the theoretical position where the compression reaction FP is most intense was found to be located at 37 degree anterior, in the rotational direction, to the position TDC corresponding to the top dead center, and the actual position where the compression reaction Fp is most intense was found to be located behind a maximum of 10 degrees from the theoretical position, depending on the rotation speed. With this, the actual position was found to be located within a range ⁇ of 27 to 37 degrees anterior, in the rotational direction R, to the position TDC corresponding to the top dead center (see Figs. 7 and 9 ).
  • a contact between the pin 51 and one 53a of the axial-load receiving surfaces 53a and 53b when the swash plate 24 is in the maximum inclination angle is preferably provided within the angle range of 27 to 90 degrees anterior, in the rotational direction, to the position TDC of the swash plate 24 corresponding to the top dead center. Further, the contact is more preferably provided within the angle range of 27 to 37 degrees anterior, in the rotational direction R, to the position TDC of the swash plate corresponding to the top dead center.
  • the contact is provided at 33 degrees anterior, in the rotation direction R, to the position TDC of the swash plate 24 corresponding to the top dead center (that is, the contact is provided at the position 4 degrees behind the theoretical pressure peak of 37 degrees).
  • the axial-load receiving surface 53a receives the compressive reaction Fp via the pistons 29 right or nearly right in front of the axial-load receiving surface 53a.
  • the present embodiment has the following effects according to the above configuration.
  • the hinge mechanism 40 includes: the arm 41 protruded from the rotor 21; the arm 43 protruded from the swash plate 24 and receiving the rotational torque from the arm 41 of the rotor; a pin 51 provided at one (the arm 43 of the swash plate in this embodiment) of the arm 41 of the rotor and the arm 43 of the swash plate; and, the axial-load receiving surfaces 53a and 53b provided at the other (the arm 41 of the rotor in this embodiment) of the arm 41 and the arm 43 and configured to be in contact with the pin 51 to receive the compressive reaction Fp (axial load) from the pistons 29.
  • the position where the pin 51 and one (53a in this embodiment) of the axial-load receiving surfaces 53a, 53b contact with each other when the swash plate 24 is in the maximum inclination angle is located where the compressive reaction Fp from the piston 29 is maximum, that is, within the range of 27 to 90 degrees anterior, in the rotation direction, to the position TDC corresponding to the top dead center.
  • the position where the pin 51 and one (53a in this embodiment) of the axial-load receiving surfaces 53a and 53b when the swash plate 24 is in the maximum inclination angle is provided within the angle range ⁇ of 27 to 37 degrees anterior, in the rotational direction, to the position TDC corresponding to the top dead center. Therefore, sliding resistance between the arm 43 of the swash plate and the arm 41 of the rotor becomes smaller.
  • one (the arm 43 of the swash plate in this embodiment) of the arms 41, 43 has the slit 41s to be formed in a fork shape, and the other (the arm 41 of the rotor in this embodiment) of the arms 41, 43 is slidably fit in the slit 41s in a sandwich manner. Therefore, a backlash hardly occurs between the arms 41 and 43.
  • the pin 51 is formed of a separate member separated from and fixed to one of the arm 41 of the rotor and the arm 43 of the swash plate (the arm 43 of the swash plate in the present embodiment).
  • the pin 51 is formed of a member separated from the arm (the arm 43 of the swash plate in the present embodiment), the arm (the arm 43 of the swash plate this example) is not required to be hardened or quenched if only the pin 51 is hardened or quenched. Therefore, the manufacturing cost is reduced.
  • the arm (the arm 43 of the swash plate in the embodiment) is formed of a separate member, the peripheral surface of the pin 51 can be easily formed into a complicated shape. In such a structure, the manufacturing cost can be reduced compared with a structure in which the arm (the arm 43 of the swash plate) is formed in a complicated shape. In addition, replacing only the pin 51 is allowed.
  • the pin 51 is fixed to the arm 43 of the swash plate and the axial-load receiving surfaces 53a and 53b are formed at the arm 41 of the rotor in the above embodiment, the axial-load receiving surface may be formed at the arm 43 of the swash plate, and the pin 51 may be provided at the arm 41 of the rotor in the present invention.
  • the pin 51 may be formed integrally with the arm 41 or the arm 43.
  • the axial-load receiving surfaces 53a and 53b are symmetrically provided about the position TDC corresponding to the top dead center in the above embodiment, the axial-load receiving surfaces 53a and 53b do not have to be symmetrically provided about the position TDC corresponding to the top dead center in the present invention.
  • the arm 41 of the rotor is formed with the slit 41s and the arm 43 of the swash plate is slidably fit in the slit 41s in a sandwich manner in the above-mentioned embodiment
  • the arm 43 of the swash plate may be formed with the slit 43s and the arm 41 of the rotor may be slidably fit in the slit 43s in a sandwich manner, as seen in the modification shown in Fig. 10 , in the present invention.
  • the pin has a circular cross section in the above embodiment, it may have other sectional shapes in the present invention.
  • the swash plate 24 is assembled by combining separate members of the swash plate body 26 and the hub 25 in the above embodiment, the swash plate may be formed of a member in the present invention. Moreover, although the above embodiment has a non-sleeve structure in which the swash plate 24 is directly attached to the drive shaft 10 without a sleeve, the swash plate may be attached to the drive shaft via a sleeve in the present invention.
  • a wobble plate may be used as a substitute in the present invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP07806954A 2006-09-08 2007-09-07 Verdichter mit variabler verdrängung Withdrawn EP2063121A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006244691A JP2008064057A (ja) 2006-09-08 2006-09-08 可変容量圧縮機
PCT/JP2007/067522 WO2008029919A1 (en) 2006-09-08 2007-09-07 Variable displacement compressor

Publications (1)

Publication Number Publication Date
EP2063121A1 true EP2063121A1 (de) 2009-05-27

Family

ID=39157342

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07806954A Withdrawn EP2063121A1 (de) 2006-09-08 2007-09-07 Verdichter mit variabler verdrängung

Country Status (6)

Country Link
US (1) US20110041682A1 (de)
EP (1) EP2063121A1 (de)
JP (1) JP2008064057A (de)
KR (1) KR20090052867A (de)
CN (1) CN101512151B (de)
WO (1) WO2008029919A1 (de)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5579144B2 (ja) * 2011-09-22 2014-08-27 サンデン株式会社 可変容量圧縮機
DE112014004156B4 (de) * 2013-09-11 2019-11-21 Kabushiki Kaisha Toyota Jidoshokki Verdichter der Taumelscheibenbauart mit variabler Verdrängung durch eine Steuerungsdruckkammer
WO2017011518A1 (en) 2015-07-13 2017-01-19 University Of South Florida Protein acyl transferase inhibitors and methods of treatment
JP7028402B2 (ja) * 2018-02-28 2022-03-02 サンデン・オートモーティブコンポーネント株式会社 可変容量圧縮機

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2626292B2 (ja) * 1991-03-30 1997-07-02 株式会社豊田自動織機製作所 容量可変型斜板式圧縮機
JPH05312144A (ja) * 1992-05-08 1993-11-22 Sanden Corp 可変容量斜板式圧縮機
JP3422186B2 (ja) * 1995-11-24 2003-06-30 株式会社豊田自動織機 可変容量圧縮機
JP4007637B2 (ja) * 1997-03-31 2007-11-14 サンデン株式会社 可変容量圧縮機
JPH11264371A (ja) * 1998-03-18 1999-09-28 Toyota Autom Loom Works Ltd 可変容量型圧縮機
JPH11336657A (ja) * 1998-05-27 1999-12-07 Nippon Soken Inc 斜板型可変容量圧縮機
BR0005257A (pt) * 1999-11-09 2001-07-24 Sanden Corp Elo de ligação entre o rotor e a placa de cames de compressor com placa oscilante de deslocamento variável
KR100318772B1 (ko) * 1999-12-16 2001-12-28 신영주 가변용량 사판식 압축기
JP2002303261A (ja) * 2001-04-06 2002-10-18 Sanden Corp 容量可変型斜板式圧縮機
JP2004068756A (ja) 2002-08-08 2004-03-04 Toyota Industries Corp 容量可変型圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2008029919A1 *

Also Published As

Publication number Publication date
JP2008064057A (ja) 2008-03-21
WO2008029919A1 (en) 2008-03-13
CN101512151A (zh) 2009-08-19
CN101512151B (zh) 2011-08-17
KR20090052867A (ko) 2009-05-26
US20110041682A1 (en) 2011-02-24

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