EP2063121A1 - Variable displacement compressor - Google Patents
Variable displacement compressor Download PDFInfo
- 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- Withdrawn
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Classifications
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- 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
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- 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
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- 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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- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
- The present invention relates to a variable capacity compressor equipped with a hinge mechanism which is rotatable while transmitting a rotational torque.
- A conventional variable capacity compressor is disclosed in Japanese Patent Application Laid-Open No.
2004-068756 Figs. 11 to 13 , adrive shaft 105, arotor 103 fixed to thedrive shaft 105 to rotate with the drive shaft, a swash plate 101 (a cam plate) slidably attached to thedrive shaft 105, and pistons (not shown) reciprocatably accommodated in cylinder bores (not shown) and engaged with theswash plate 101. The discharge capacity can be changed by changing the piston stroke while changing the inclination angle of theswash plate 101. A hinge mechanism is provided between therotor 103 and theswash plate 101 to change the inclination angle of the swash plate while transmitting torque from therotor 103 to theswash plate 101. - The hinge mechanism includes an
arm 104 of the rotor projected towards theswash plate 101 from therotor 103, and anarm 102 of the swash plate projected towards therotor 103 from theswash plate 101. Thearm 104 of the rotor and thearm 102 of the swash plate are overlapped with each other in the rotational direction, so that rotation of therotor 103 which rotates with thedrive shaft 105 is transmitted to theswash plate 101. An axial-load receiving surface 106 is provided in a base portion of thearm 104 of the rotor and receives a compressive reaction (axial load) which is applied from the pistons to theswash plate 101. Thereceiving surface 106 has a function to guide a change of the inclination angle of theswash plate 101 while being in slide contact with thearm 102 of the swash plate. - In the swash plate compressor, as shown in
Figs. 12 and 13 , a position where the compressive reaction Fp from the piston is maximum is located off a position TDC in theswash 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 theswash plate 101 with respect to a line C passing through the position TDC in theswash plate 101 corresponding to the top dead center and a position BDC of theswash plate 101 corresponding to a bottom dead center, so that a twisting force Fn is applied to theswash plate 101 as shown inFig. 13 . Theswash plate 24 thus is inclined about the line C and twisted. When theswash plate 101 is twisted, a corner K1 of thearm 102 of theswash plate 101 is digged into thearm 104 of therotor 103 and also a corner K2 of thearm 104 of therotor 103 is digged into thearm 102 of theswash plate 101. With this, the sliding resistance between thearms swash plate 101 becomes extremely high. - 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 between the rotation member and the tilting member, Wherein a position where the pin and the axial-load receiving surface contacts with each other when the inclination angle of the tilting member is maximum is located within an angular range of 27 to 90 degrees anterior, in the rotation direction R, to a position in the tilting member corresponding to the top dead center.
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Fig. 1] Fig. 1 is a sectional view of a variable capacity compressor which is in a maximum stroke position according to an embodiment of the present invention. - [
Fig. 2] Fig. 2 is a sectional view of the variable capacity compressor which is in a minimum stroke position. - [
Fig. 3] Fig. 3 is a side view of an assembly of the drive shaft, rotor, and swash plate which is in the maximum stroke position of the variable capacity compressor. - [
Fig. 4] Fig. 4 is a side view of the assembly which is in the minimum stroke position. - [
Fig. 5] Fig. 5 is a perspective view of the assembly. - [
Fig. 6] Fig. 6 is a view of the assembly as seen from the direction VI inFig. 3 , in which a main body of the swash plate is removed. - [
Fig. 7] Fig. 7 is a graph of theoretical pressure curves in a cylinder bore when discharge pressure Pd is the upper limit value of 3.16Mpa. - [
Fig. 8] Fig. 8 is a graph of theoretical pressure curves in the cylinder bore when discharge pressure Pd is the lower limit value of 1.12Mpa. - [
Fig. 9] Fig. 9 is a graph of measured results showing a relation between the pressure peak in the cylinder bore and a rotation speed. - [
Fig. 10] Fig. 10 is a perspective view of a modification of the assembly of the variable capacity compressor. - [
Fig. 11] Fig. 11 is a view of a conventional variable capacity compressor counterpart toFig. 3 . - [
Fig. 12] Fig. 12 is a side view as seen along the arrow XII inFig. 11 . - [
Fig. 13] Fig. 13 is a view of a state where a swash plate inFig. 11 receives a large compressive reaction force and twisted. - Hereafter, an embodiment of a variable capacity compressor and a hinge mechanism thereof according to the present invention will be described with reference to the drawings.
- First, outline of a variable capacity compressor will be described with reference to
Figs. 1 and2 .Fig. 1 shows the maximum stroke position andFig. 2 shows the minimum stroke position. - As shown in
Figs. 1 and2 , the variable capacity compressor 1 includes acylinder block 2 having a plurality (six in this embodiment) ofcylinder bores 3 arranged in the circumferential direction at a interval, afront housing 4 joined to a front end of thecylinder block 2 and forming acrank chamber 5 therein, and arear housing 6 joined to a rear end of thecylinder block 2 with avalve plate 9 therebetween and forming asuction chamber 7 and a discharge chamber 8 therein. Thecylinder block 2, thefront housing 4, and therear housing 6 are fastened to each other by through bolts B. - The
valve plate 9 is formed withsuction holes 11 connecting and communicating thecylinder bore 3 and thesuction chamber 7 anddischarge holes 12 connecting and communicating thecylinder 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 thesuction holes 11. A valve system (not shown) is provided on the rear housing side of thevalve plate 9 to open and close thedischarge holes 12. - A
drive shaft 10 is rotatably supported bybearings bearing holes cylinder block 2 and thefront housing 4, so that thedrive shaft 10 is rotatable in thecrank chamber 5. - The
crank chamber 5 accommodates therein arotor 21 as a "rotation member" fixed to thedrive shaft 10 and aswash plate 24 as a "tilting member" attached to thedrive shaft 10. Theswash plate 24 includes ahub 25 attached to thedrive 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 aswash plate body 26 fixed to a boss portion of thehub 25. - Each
piston 29 is slidably accommodated in eachcylinder bore 3 and is connected with theswash plate body 26 of theswash plate 24 through a pair ofhemispherical piston shoes 30. - A
hinge mechanism 40 is provided between therotor 21 as a rotation member and thehub 25 of theswash plate 24 as a tilting member such that rotation of therotor 21 is transmitted to theswash plate 24, permitting the inclination of theswash plate 24 to change. When thedrive shaft 10 rotates, therotor 21 rotates with thedrive shaft 10, and rotation of therotor 21 is transmitted to theswash plate 24 via thehinge mechanism 40. The rotation of theswash plate 24 is converted into reciprocation of thepistons 29 via a pair ofpiston shoes 30 so that thepistons 29 reciprocate in thecylinder bores 3. When thepistons 29 reciprocate, refrigerant is suctioned from thesuction chamber 7 into thecylinder bores 3 through thesuction holes 11 of thevalve plate 9, compressed in the cylinder bores, and then discharged into the discharge chamber 8 through thedischarge holes 12 of thevalve plate 9. - 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 thepistons 29 to change the inclination of theswash plate 24. The pressure-control mechanism includes a gas extraction passage (not shown) which connects and communicates thecrank chamber 5 and thesuction chamber 7, a gas supply passage (not shown) which connects and communicates thecrank chamber 5 and the discharge chamber 8, and thecontrol valve 33 which is disposed in the midstream of the gas supply passage to open and close the gas supply passage. - When the gas supply passage is opened by the
control valve 33, refrigerant flows from the discharge chamber 8 into thecrank chamber 5 through the gas supply passage, thereby the crank chamber pressure Pc increases, and the inclination angle of theswash plate 24 decreases according to the pressure balance between the crank chamber pressure Pc and the suction chamber pressure Ps. As a result, the piston stroke and the discharge amount decrease. Because refrigerant keeps flowing from thecrank chamber 5 into thesuction chamber 7 through the gas extraction passage, when the gas supply passage is closed by thecontrol valve 33, the crank chamber pressure Pc decreases and thereby the inclination angle of theswash plate 24 increases according to the pressure balance between the crank chamber pressure Pc and the suction chamber pressure Ps. As a result, the piston stroke and the discharge amount increase. When thehub 25 moves toward thecylinder block 2, the inclination angle of theswash plate 24 decrease, and when thehub 25 moves away from thecylinder block 2, the inclination angle of theswash plate 24 increases. - Next, the
hinge mechanism 40 will be explained with reference toFigs. 3 to 6 . -
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, andFig. 6 is a view of the assembly without the swash plate body as seen along the arrow VI inFig. 3 . - As shown in
Figs. 3 to 6 , thehinge mechanism 40 includes anarm 41 which is protruded towards thehub 25 from therotor 21, and anarm 43 which is protruded towards therotor 21 from thehub 25. Thearm 41 of the rotor and thearm 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 therotor 21 is transmitted to theswash plate 24. In this embodiment, as shown inFigs. 3 and4 , thearm 41 of the rotor has aslit 41s extending in the axial direction XY (a direction perpendicular to the rotation torque transmitting direction Ft) and is formed a fork shape. Thearm 43 of the swash plate is slidably fit in theslit 41s (that is, between a pair ofarms arm 43 of the swash plate is also formed in a fork shape. - When the
swash plate 24 rotates and thepistons 29 reciprocate, a compressive reaction (axial load Fp) is applied to theswash plate 24 from thepistons 29. The compressive reaction Fp is received at a contact between apin 51 which is press fit in a hole formed in thearm 43 of theswash plate 24 and the axial-load receiving surfaces arms rotor 21. Thepin 51 extends in a direction tangent to the rotational direction of therotator 21 and theswash plate 24. That is, thepin 51 extends towards the rotational torque transmitting direction Ft. - These axial-
load receiving surfaces swash plate 24 is changed, the axial load Fp (compressive reaction from a piston) is applied between thepin 51 and the axial-load receiving surfaces - Since large compressive reaction (axial load Fp) is applied to the contacts between the
pin 51 and the axial-load receiving surfaces rotor 21, the axial-load receiving surfaces rotor 21 and thepin 51 are hardened or quenched. - As a result of experiment conducted by the inventor, a position where the compressive reaction Fp is maximum with parameters of the suction pressure, the discharge pressure and the rotational speed was found to be located within the range α of 27 to 90 degrees anterior, in the rotational direction R, to a position TDC of the
swash plate 24 corresponding to the top dead center (seeFigs. 7, 8 and9 ). When a compressive load is maximum (that is, when the pressure difference between the discharge pressure and the suction pressure is maximum), the compressive reaction FP becomes more intense. 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 α 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 (seeFigs. 7 and9 ). - When a refrigerant 134a or the similar is used, the suction pressure is in a range of 0.26 to 0.51 Mpa, and the discharge pressure is in a range of 3.16 to 1.12 Mpa. In these ranges, theoretical pressure peak in the cylinder bore (pressure peak occurs when the discharge valve starts to open) is located at 323 degrees (that is, 37 degrees anterior to the top dead center in the rotational direction) which is the upper limit as shown in
Fig. 7 , and at 270 degrees (that is, 90 degrees anterior to the top dead center in the rotational direction) which is the lower limit as shown inFig. 8. 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. - Actual pressure peaks in the cylinder bore occur after the theoretical pressure peak, depending on the rotation speed of the drive shaft. As a result of the experiment, the pressure peaks in the cylinder bore turned out to occur after the theoretical pressure peak by a maximum of 10 degrees, as shown in
Fig. 9 . More specifically, it occurred after the theoretical pressure peak by 4 degrees when the rotation of the drive shaft is at low speed (when the vehicle idles), and it occurred after the theoretical pressure peak by 10 degrees when the rotation of the drive shaft is at high speed (when the vehicle runs faster than 100 km/h). - Therefore, when the discharge pressure, suction pressure and rotational speed are variable, 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 theswash plate 24 corresponding to the top dead center. When 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 α of 27 to 37 degrees anterior, in the rotational direction R, to the position TDC corresponding to the top dead center (seeFigs. 7 and9 ). - Based upon the above analysis, in the present embodiment, a contact between the
pin 51 and one 53a of the axial-load receiving surfaces 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 theswash 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. When the difference between the discharge pressure and the suction pressure is maximum and the rotation speed is at low speed (the vehicle idles), the above problem is the most remarkable. Therefore, in this embodiment, the contact is provided at 33 degrees anterior, in the rotation direction R, to the position TDC of theswash plate 24 corresponding to the top dead center (that is, the contact is provided at theposition 4 degrees behind the theoretical pressure peak of 37 degrees). - According to the embodiment, the axial-
load receiving surface 53a receives the compressive reaction Fp via thepistons 29 right or nearly right in front of the axial-load receiving surface 53a. This makes torsion of theswash plate 24 smaller than the conventional art. Therefore, sliding resistance between thearm 43 of the swash plate and thearm 41 of the rotor become small so that the controllability of the compressor improves. - The present embodiment has the following effects according to the above configuration.
- First, according to the variable capacity compressor of the embodiment, the
hinge mechanism 40 includes: thearm 41 protruded from therotor 21; thearm 43 protruded from theswash plate 24 and receiving the rotational torque from thearm 41 of the rotor; apin 51 provided at one (thearm 43 of the swash plate in this embodiment) of thearm 41 of the rotor and thearm 43 of the swash plate; and, the axial-load receiving surfaces arm 41 of the rotor in this embodiment) of thearm 41 and thearm 43 and configured to be in contact with thepin 51 to receive the compressive reaction Fp (axial load) from thepistons 29. The position where thepin 51 and one (53a in this embodiment) of the axial-load receiving surfaces swash plate 24 is in the maximum inclination angle is located where the compressive reaction Fp from thepiston 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. - Therefore, the compressive reaction Fp from the
piston 29 is received by the position almost right opposite thereto, and thereby, theswash plate 24 can be prevented from being twisted unlike the above conventional art. Therefore, the sliding resistance between thearm 43 of the swash plate and thearm 41 of the rotor becomes small, and the controllability of the compressor improves. - Second, according to the variable capacity compressor of the present embodiment, the position where the
pin 51 and one (53a in this embodiment) of the axial-load receiving surfaces swash plate 24 is in the maximum inclination angle is provided within the angle range α of 27 to 37 degrees anterior, in the rotational direction, to the position TDC corresponding to the top dead center. Therefore, sliding resistance between thearm 43 of the swash plate and thearm 41 of the rotor becomes smaller. - Third, in the variable capacity compressor, one (the
arm 43 of the swash plate in this embodiment) of thearms slit 41s to be formed in a fork shape, and the other (thearm 41 of the rotor in this embodiment) of thearms slit 41s in a sandwich manner. Therefore, a backlash hardly occurs between thearms - Fourth, according to the
hinge mechanism 40 of the present embodiment, thepin 51 is formed of a separate member separated from and fixed to one of thearm 41 of the rotor and thearm 43 of the swash plate (thearm 43 of the swash plate in the present embodiment). - Since the
pin 51 is formed of a member separated from the arm (thearm 43 of the swash plate in the present embodiment), the arm (thearm 43 of the swash plate this example) is not required to be hardened or quenched if only thepin 51 is hardened or quenched. Therefore, the manufacturing cost is reduced. - Moreover, since the arm (the
arm 43 of the swash plate in the embodiment) is formed of a separate member, the peripheral surface of thepin 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 (thearm 43 of the swash plate) is formed in a complicated shape. In addition, replacing only thepin 51 is allowed. - The present invention should not be limited to the above embodiment.
- For example, although the
pin 51 is fixed to thearm 43 of the swash plate and the axial-load receiving surfaces arm 41 of the rotor in the above embodiment, the axial-load receiving surface may be formed at thearm 43 of the swash plate, and thepin 51 may be provided at thearm 41 of the rotor in the present invention. - Although the above embodiment has the
pin 51 formed of a separate member separated from the arm, thepin 51 may be formed integrally with thearm 41 or thearm 43. - Although the axial-
load receiving surfaces load receiving surfaces - Although the
arm 41 of the rotor is formed with theslit 41s and thearm 43 of the swash plate is slidably fit in theslit 41s in a sandwich manner in the above-mentioned embodiment, thearm 43 of the swash plate may be formed with theslit 43s and thearm 41 of the rotor may be slidably fit in theslit 43s in a sandwich manner, as seen in the modification shown inFig. 10 , in the present invention. - Although the pin has a circular cross section in the above embodiment, it may have other sectional shapes in the present invention.
- Although the
swash plate 24 is assembled by combining separate members of theswash plate body 26 and thehub 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 theswash plate 24 is directly attached to thedrive shaft 10 without a sleeve, the swash plate may be attached to the drive shaft via a sleeve in the present invention. - Although the swash plate is used in the above embodiment, a wobble plate may be used as a substitute in the present invention.
- Moreover, various changes and modifications may be made to the present invention without departing the scope of the invention.
Claims (5)
- A variable capacity compressor comprising: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 such that the tilting member is slidable along the axis of the drive shaft and inclinable with respect to the drive shaft;a hinge mechanism configured to transmit rotational torque of the rotation member to the tilting member while permitting the inclination of the tilting member to change; andpistons configured to reciprocate in cylinder bores in accordance with rotation of the tilting member,the hinge mechanism including:an arm projected from the rotation member toward the tilting member;an arm projected from the tilting member toward the rotation 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; andan axial-load receiving surface formed on the other of the arm of the rotation member and the arm of the tilting member and configured to contact with the pin to receive an axial load applied to the rotation member from the tilting member,wherein a position where the pin and the axial-load receiving surface contact with each other when the inclination angle of the tilting member is maximum is located within a range of 27 to 90 degrees anterior, in the rotational direction R, to a position corresponding to a top dead center.
- The variable capacity compressor according to claim 1,
wherein the position where the pin and the axial-load receiving surface contact with each other when the inclination angle of the tilting member is maximum is located within a range of 27 to 37 degrees anterior, in the rotational direction R, to the position corresponding to the top dead center. - The variable capacity compressor according to claim 1, wherein
the arm of the rotation member is formed in a fork shape with a slit in which the arm of the tilting member is slidably fit in a sandwich manner. - The variable capacity compressor according to claim 1, wherein
the arm of the tilting member is formed in a fork shape with a slit in which the arm of the rotation member is slidably fit in a sandwich manner. - The variable capacity compressor according to claim 1, wherein
the pin is formed of a separated member separated from and fixed to one of the arm of the rotation member and the arm of the tilting member.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006244691A JP2008064057A (en) | 2006-09-08 | 2006-09-08 | Variable displacement compressor |
PCT/JP2007/067522 WO2008029919A1 (en) | 2006-09-08 | 2007-09-07 | Variable displacement compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
EP2063121A1 true EP2063121A1 (en) | 2009-05-27 |
Family
ID=39157342
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07806954A Withdrawn EP2063121A1 (en) | 2006-09-08 | 2007-09-07 | Variable displacement compressor |
Country Status (6)
Country | Link |
---|---|
US (1) | US20110041682A1 (en) |
EP (1) | EP2063121A1 (en) |
JP (1) | JP2008064057A (en) |
KR (1) | KR20090052867A (en) |
CN (1) | CN101512151B (en) |
WO (1) | WO2008029919A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5579144B2 (en) * | 2011-09-22 | 2014-08-27 | サンデン株式会社 | Variable capacity compressor |
KR101889628B1 (en) * | 2013-09-11 | 2018-08-17 | 가부시키가이샤 도요다 지도숏키 | Variable-capacity swash plate compressor |
US10085981B2 (en) | 2015-07-13 | 2018-10-02 | University Of South Florida | Protein acyl transferase inhibitors and methods of treatment |
JP7028402B2 (en) * | 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 | Variable capacity compressor |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2626292B2 (en) * | 1991-03-30 | 1997-07-02 | 株式会社豊田自動織機製作所 | Variable capacity swash plate compressor |
JPH05312144A (en) * | 1992-05-08 | 1993-11-22 | Sanden Corp | Variable displacement swash plate type compressor |
JP3422186B2 (en) * | 1995-11-24 | 2003-06-30 | 株式会社豊田自動織機 | Variable capacity compressor |
JP4007637B2 (en) * | 1997-03-31 | 2007-11-14 | サンデン株式会社 | Variable capacity compressor |
JPH11264371A (en) * | 1998-03-18 | 1999-09-28 | Toyota Autom Loom Works Ltd | Variable displacement compressor |
JPH11336657A (en) * | 1998-05-27 | 1999-12-07 | Nippon Soken Inc | Swash plate type variable displacement compressor |
US6470761B1 (en) * | 1999-11-09 | 2002-10-29 | Sanden Corporation | Connecting link between the rotor and the CAM plate of a variable displacement swash plate compressor |
KR100318772B1 (en) * | 1999-12-16 | 2001-12-28 | 신영주 | Variable capacity swash plate type compressor |
JP2002303261A (en) * | 2001-04-06 | 2002-10-18 | Sanden Corp | Variable displacement swash plate compressor |
JP2004068756A (en) | 2002-08-08 | 2004-03-04 | Toyota Industries Corp | Variable displacement compressor |
-
2006
- 2006-09-08 JP JP2006244691A patent/JP2008064057A/en active Pending
-
2007
- 2007-09-07 CN CN2007800331591A patent/CN101512151B/en not_active Expired - Fee Related
- 2007-09-07 EP EP07806954A patent/EP2063121A1/en not_active Withdrawn
- 2007-09-07 US US12/440,353 patent/US20110041682A1/en not_active Abandoned
- 2007-09-07 WO PCT/JP2007/067522 patent/WO2008029919A1/en active Application Filing
- 2007-09-07 KR KR1020097005025A patent/KR20090052867A/en not_active Application Discontinuation
Non-Patent Citations (1)
Title |
---|
See references of WO2008029919A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN101512151B (en) | 2011-08-17 |
US20110041682A1 (en) | 2011-02-24 |
WO2008029919A1 (en) | 2008-03-13 |
KR20090052867A (en) | 2009-05-26 |
CN101512151A (en) | 2009-08-19 |
JP2008064057A (en) | 2008-03-21 |
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