EP3026265A1 - Variable displacement swash-plate compressor - Google Patents
Variable displacement swash-plate compressor Download PDFInfo
- Publication number
- EP3026265A1 EP3026265A1 EP15195805.5A EP15195805A EP3026265A1 EP 3026265 A1 EP3026265 A1 EP 3026265A1 EP 15195805 A EP15195805 A EP 15195805A EP 3026265 A1 EP3026265 A1 EP 3026265A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- swash plate
- drive shaft
- acting
- dead center
- inclination angle
- 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.)
- Granted
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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
- F04B27/0804—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
- F04B27/086—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 swash plate
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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
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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
- F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
- F04B27/0878—Pistons
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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
- 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
Definitions
- the valve base plate 40, the discharge valve plate 43, and the retainer plate 45 include suction ports 40a, the number of which is equal to that of the cylinder bores 21a. Furthermore, the valve base plate 40 and the suction valve plate 41 include discharge ports 40b, the number of which is equal to that of the cylinder bores 21a.
- the cylinder bores 21a communicate with the suction chamber 33 through the suction ports 40a and communicate with the discharge chamber 35 through the discharge ports 40b.
- the valve base plate 40, the suction valve plate 41, the discharge valve plate 43, and the retainer plate 45 include a first communication hole 40c and a second communication hole 40d.
- the first communication hole 40c connects the suction chamber 33 to the suction passage 39. This causes the swash plate chamber 25 to communicate with the suction chamber 33.
- the swash plate main portion 50 is shaped as a flat annular plate and has a front surface 5a and a rear surface 5b.
- a top dead center associated part T for positioning each piston 9 at the top dead center and a bottom dead center associated part U for positioning each piston 9 at the bottom dead center are defined on the swash plate main portion 50.
- an imaginary bottom dead center plane D is defined in this compressor.
- the bottom dead center plane D includes the top dead center associated part T, the bottom dead center associated part U, and the drive shaft axis O.
- the first protrusion 5g and the second protrusion 5h are provided on the swash plate weight 5c at positions on opposite sides of the bottom dead center plane D, and project forward from the swash plate 5, that is, toward the actuator 13.
- the first and second protrusions 5g, 5h each have an arcuate shape with a generatrix extending in a direction perpendicular to the bottom dead center plane D.
- the movable body weight 134 is located closer to the bottom dead center associate part U of the swash plate main portion 50 than the drive shaft axis O. That is, the movable body weight 134 is located between the drive shaft axis O and the bottom dead center associated part U.
- the movable body weight 134 has a semi-columnar shape. As shown in Fig. 1 , the movable body weight 134 extends from the second cylindrical portion 132 toward the swash plate 5. The movable body weight 134 displaces the center of gravity of the movable body 13a to a position closer to the bottom dead center associated part U than the drive shaft axis O.
- the first vertical surface 134c is connected to an end of the first inclined surface 134a that faces the swash plate 5 and vertically extends toward the bottom dead center associated part U.
- the second vertical surface 134d is connected to an end of the second inclined surface 134b that faces the swash plate 5 and vertically extends toward the bottom dead center associated part U.
- the first vertical surface 134c and the second vertical surface 134d are continuous with each other and located on opposite sides of the bottom dead center plane D.
- the first inclined surface 134a and the first vertical surface 134c that is, the first acting portion 14a contacts the first protrusion 5g shown in Fig. 3 at a first acting position F1 shown in Fig. 7 . Since the first protrusion 5g has a cylindrical shape as described above, the first acting portion 14a and the first protrusion 5g make line contact at the first acting position F1. Likewise, the second acting portion 14b and the second protrusion 5h shown in Fig. 3 make line contact at a second acting position F2 shown in Fig. 7 .
- Fig. 7 shows a state in which the first acting position F1 is located on the first inclined surface 134a, and the second acting position F2 is located on the second inclined surface 134b.
- the first acting position F1 and the second acting position F2 are moved. That is, as shown in Figs. 8 to 10 , when the swash plate 5 is moved from the minimum inclination angle to the maximum inclination angle, the first acting position F1 is moved from the first vertical surface 134c to a position on the first inclined surface 134a that is close to the second cylindrical portion 132.
- the second acting position F2 is moved from the second vertical surface 134d to a position on the second inclined surface 134b that is close to the second cylindrical portion 132.
- the first and second acting positions F1, F2 are located at positions shifted closer to the bottom dead center associated part U than the drive shaft axis O. That is, the first and second acting positions F1, F2 are located between the drive shaft axis O and the bottom dead center associated part U. Movement of the first and second acting positions F1, F2 will be described below.
- the drive shaft 3 has an axial passage 3a and a radial passage 3b.
- the axial passage 3a extends from the rear end of the drive shaft 3 toward the front end along the drive shaft axis O.
- the radial passage 3b extends in a radial direction from the front end of the axial passage 3a and opens in the outer circumferential surface of the drive shaft 3.
- the rear end of the axial passage 3a communicates with the pressure regulation chamber 31.
- the radial passage 3b communicates with control pressure chamber 13b as shown in Fig. 5 .
- the axial passage 3a and the radial passage 3b connect the pressure regulation chamber 31 to the control pressure chamber 13b.
- a pipe connected to the evaporator is connected to the inlet 250 shown in Fig. 1
- a pipe connected to the condenser is connected to the outlet.
- the condenser is connected to the evaporator via a pipe and an expansion valve.
- the drive shaft 3 rotates to rotate the swash plate 5, thus reciprocating each piston 9 in the corresponding cylinder bore 21a.
- This varies the volume of each compression chamber 57 in accordance with the piston stroke.
- the refrigerant that has been drawn from the evaporator into the swash plate chamber 25 through the inlet 250 flows through the suction passage 39 and the suction chamber 33 and is compressed in the compression chambers 57.
- the refrigerant that is compressed in the compression chambers 57 is discharged to the discharge chamber 35 and is discharged to the condenser through the outlet.
- the actuator 13 changes the inclination angle of the swash plate 5 to increase or decrease the stroke of the pistons 9, thereby varying the displacement of the compressor.
- the first acting position F1 of the compressor the first acting portion 14a shown in Fig. 7 pushes the first protrusion 5g shown in Fig. 3 toward the rear of the swash plate chamber 25.
- the second acting portion 14b shown in Fig. 7 pushes the second protrusion 5h shown in Fig. 3 toward the rear of the swash plate chamber 25.
- the first and second acting positions F1, F2 are located at positions shifted closer to the bottom dead center associated part U than the drive shaft axis O. That is, the first and second acting positions F1, F2 are located between the drive shaft axis O and the bottom dead center associated part U.
- the movable body 13a pushes the swash plate 5 at a position shifted closer to the bottom dead center associated part U than the drive shaft axis O via the first and second acting portions 14a, 14b and the first and second protrusions 5g, 5h. Therefore, the first and second swash plate arms 5e, 5f slide on the first and second guide surfaces 57a, 57b, respectively, toward the drive shaft axis O as shown in Fig. 8 .
- the swash plate 5 reduces the angle relative to the direction perpendicular to the drive shaft axis O, or the inclination angle, while substantially maintaining the position of the top dead center associated part T. This reduces the stroke of the pistons 9 and the displacement of the compressor per rotation of the drive shaft 3. The reduction in the inclination angle causes the swash plate 5 contact the restoration spring 37.
- the inclination angle of the swash plate 5 shown in Figs. 1 and 8 corresponds to the minimum inclination angle in the compressor.
- the reaction force acting on the swash plate 5 and the urging force of the restoration spring 37 cause the first and second swash plate arms 5e, 5f to slide on the first and second guide surfaces 57a, 57b, respectively, to move away from the drive shaft axis O.
- Fig. 9 illustrates a state in which the inclination angle of the swash plate 5 is slightly increased.
- the inclination angle of the swash plate 5 shown in Fig. 10 corresponds to the maximum inclination angle in the compressor.
- the compressor of the comparative example includes partially modified versions of the swash plate 5 and the movable body 13a of the compressor according to the first embodiment. Specifically, the swash plate weight 5c does not have the first and second protrusions 5g, 5h, and the movable body 13a does not have the movable body weight 134. In this configuration of the comparative example, the rear end of the first cylindrical portion 131 of the movable body 13a contacts the front surface 5a of the swash plate main portion 50 at a position around the through hole 5d. Thus, in the comparative example, the movable body 13a and the swash plate 5 contact each other at a position substantially on the drive shaft axis O, and the acting position is located about the drive shaft 3.
- the acting position in which the acting position is located about the drive shaft 3, the acting position is located close to the top dead center associated part T, and the movable body 13a is easily influenced by the reaction force. Therefore, as indicated by the graph of Fig. 11 , in the compressor of the comparative example, the variable pressure difference needs to be increased to move the movable body 13a with a greater thrust as the inclination angle of the swash plate 5 is reduced.
- the compressor of the comparison example has a small displacement per rotation of the drive shaft 3 and the pressure in the control pressure chamber 13b cannot be increased, the variable pressure difference cannot be increased.
- the size of the movable body 13a may be increased to enlarge the pressure receiving area. However, this would increase the size of the compressor.
- the first and second acting positions F1, F2 are located at positions shifted closer to the bottom dead center associated part U than the drive shaft axis O.
- the first and second acting positions F1, F2 are separated away from the top dead center associated part T, which makes the movable body 13a less prone to influence of the reaction force. That is, the load on the movable body 13a when decreasing the inclination angle is reduced, so that the movable body 13a is moved without increasing the variable pressure difference.
- the variable pressure difference is reduced over the entire range and made substantially constant as indicated by the graph of Fig. 11 when the inclination angle is changed.
- the first and second acting positions F1, F2 are shifted closer to the bottom dead center associated part U than the drive shaft axis O.
- the acting position is close to the top dead center associated part T, the stroke of the movable body 13a when the inclination angle of the swash plate 5 is changed is increased.
- the first and second acting positions F1, F2 are moved in a direction from the bottom dead center associated part U toward the drive shaft axis O by moving the swash plate 5 from the minimum inclination angle to the maximum inclination angle as shown in Figs. 8 to 10 .
- the fist acting position F1 will be described.
- the first acting portion 14a pushes the first protrusion 5g toward the rear of the swash plate chamber 25 at the first acting position F1.
- the first acting position F1 moves from the first inclined surface 134a toward the first vertical surface 134c.
- the first acting position F1 is located on the first vertical surface 134c. That is, when the swash plate 5 is at the minimum inclination angle, the first vertical surface 134c and the first protrusion 5g make line contact at the first acting position F1.
- the position of the first acting position F1 at this time is defined as an initial position A.
- the inclination angle of the swash plate 5 is slightly increased.
- the first inclined surface 134a and the first protrusion 5g make line contact at the first acting position F1. More specifically, a part of the first inclined surface 134a that is close to the first vertical surface 134c and the first protrusion 5g make line contact.
- the first acting position F1 is moved from the initial position A toward the lug plate 51 along the drive shaft axis O by a distance X1.
- the first acting position F1 is also moved in a direction from the bottom dead center associated part U toward the drive shaft axis O by a distance Y1.
- the first acting position F1 is moved from the initial position A by the distance Y1 in a direction from the bottom dead center associated part U toward the drive shaft axis O.
- the initial position A is illustrated as a circle of a dashed line in Figs. 9 and 10 .
- the first protrusion 5g slides on the first inclined surface 134a toward the second cylindrical portion 132.
- the inclination angle of the swash plate 5 is maximized as shown in Fig. 10 , a part of the first inclined surface 134a that is close to the second cylindrical portion 132 and the first protrusion 5g make line contact at the first acting position F1. That is, the first acting position F1 is moved from the initial position A toward the lug plate 51 along the drive shaft axis O by a distance X2, which is greater than the distance X1.
- the compressor according to the first embodiment has a high controllability and an improved mountability.
- the guide surfaces 52a, 52b allow the swash plate 5 to easily contact the outer circumferential surface 30 of the drive shaft 3 at two points on opposite sides of the drive shaft axis O. Therefore, the compressor reliably prevents the swash plate 5 from being warped by the moment. Since the compressor has no sleeve, the number of components is reduced, and the manufacturing costs are reduced, accordingly.
- the swash plate main portion 50 has the swash plate weight 5c on the front surface 5a
- the movable body 13a has the movable body weight 134.
- the swash plate weight 5c and the movable body weight 134 are located at positions closer to the bottom dead center associated part U than the drive shaft axis O.
- the swash plate arms 5e, 5f are closer to the top dead center associated part T than the drive shaft axis O on the front surface 5a
- the swash plate weight 5c and the movable body weight 134 reliably maintain the weight balance between the top dead center associated part T and the bottom dead center associated part U with the drive shaft axis O in between. Therefore, rotation of the drive shaft 3 reliably rotates the link mechanism 7, the actuator 13, and the swash plate 5, and vibration during operation is suppressed.
- the acting position F3 is located on the inclined surface 136a. That is, when the swash plate 5 is at the maximum inclination angle, the inclined surface 136a and the protrusion 5i make point contact at the acting position F3.
- the acting position F3 of this compressor is defined on the swash plate main portion 50 in an area between the opposite position P2 and the bottom dead center associated part U.
- the other components of the compressor of the second embodiment are configured identically with the corresponding components of the compressor of the first embodiment. Accordingly, these components are identified by the same reference numbers, and detailed description thereof is omitted herein.
- the acting position F3 is defined on the swash plate main portion 50 in an area between the opposite position P2 and the bottom dead center associated part U.
- the reaction force from components such as the pistons 9 is maximized at the maximum load position P1.
- the reaction force acting on the swash plate 5 is small between the opposite position P2 and the bottom dead center associated part U.
- the load on the movable body 13a is reliably reduced when the inclination angle of the swash plate 5 is reduced. Accordingly, even though the movable body 13a has the single acting position F3, the movable body 13a reliably pushes the swash plate 5 along the drive shaft axis O via the acting position F3.
- the other operations of the compressor are the same as the corresponding operations of the compressor of the first embodiment.
- control valve 15c may be provided in the high-pressure passage 15b, and the orifice 15d may be provided in the low-pressure passage 15a.
- the control valve 15c is allowed to adjust the flow rate of high-pressure refrigerant flowing through the high-pressure passage 15b. This allows the high-pressure in the discharge chamber 35 to promptly increase the pressure in the control pressure chamber 13b and to promptly reduce the displacement.
- the control valve 15c may be replaced by a three-way valve connected to the low-pressure passage 15a and the high-pressure passage 15b. In this case, the opening degree of the three-way valve is adjusted to regulate the flow rate of refrigerant flowing through the low-pressure passage 15a and the high-pressure passage 15b.
Abstract
Description
- The present invention relates to a variable displacement swash-plate compressor.
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Japanese Laid-Open Patent Publication No. 52-131204 - The link mechanism includes a lug member, a hinge ball, and a link. The lug member is located in the swash plate chamber and is fixed to the drive shaft. The hinge ball is fitted about the drive shaft to be arranged between the swash plate and the drive shaft. The hinge ball includes a spherical portion, which slidably contacts the swash plate, and a receiving portion, which faces the actuator. The receiving portion has a flat shape that is perpendicular to the drive shaft axis. The link is provided between the lug member and the swash plate. The link connects the swash plate to the lug member, so that the swash plate is permitted to pivot.
- The actuator includes the lug member, a movable body, and a control pressure chamber. The movable body has a cylindrical shape that is coaxial with the drive shaft axis. The movable body is fitted about the drive shaft and changes the inclination angle of the swash plate by moving along the axis of the drive shaft. The movable body has an acting portion at a position facing the hinge ball. The acting portion has a flat shape perpendicular to the drive shaft axis and contacts the receiving portion at an acting position. Since the hinge ball and the movable body are both fitted about the drive shaft and the acting portion and the receiving portion both have a flat shape, the acting position is located about the drive shaft. When the acting portion and the receiving contact each other, the movable body is engaged with the swash plate via the hinge ball. The control pressure chamber, which is defined by the lug member and the movable body, uses its internal pressure to move the movable body.
- In this compressor, when the control mechanism connects the discharge chamber and the control pressure chamber with each other using the pressure regulation valve, the pressure in the control pressure chamber is increased. This moves the movable body along the axis of the drive shaft and causes the acting portion to press the receiving portion along the axis of the drive shaft. Accordingly, the hinge ball is moved along the axis of the drive shaft, and the swash plate slides on the hinge ball in the direction reducing the inclination angle. This allows the displacement of the compressor per rotation of the drive shaft to be reduced.
- In this type of compressor, the swash plate receives reaction force from members such as pistons during operation. The reaction force is great at the top dead center associated part of the swash plate. However, in the compressor of the above described document, the acting position is located about the drive shaft and is close to the top dead center associated part. Thus, the movable body is easily influenced by the reaction force, which increases the load when reducing the inclination angle. Therefore, when reducing the inclination angle, the pressure difference between the swash plate chamber and the control pressure chamber (hereinafter, referred to as a variable pressure difference) needs to be increased to move the movable body with a greater thrust. In this case, the inclination angle cannot be quickly changed in response to changes in the driving state of machinery on which the compressor is mounted, such as a vehicle, and high controllability cannot be achieved.
- Further, if the compressor has a small displacement per rotation of the drive shaft and the pressure in the control pressure chamber cannot be increased, the variable pressure difference cannot be increased. Thus, to move the movable body with a great thrust, the size of the movable body may be increased to enlarge the pressure receiving area. In this case, however, the size of the actuator and thus the size of the compressor would be increased, reducing the mountability of the compressor to the vehicle and the like.
- An objective of the present invention is to provide a variable displacement swash-plate compressor that has a high controllability and an improved mountability.
- To achieve the foregoing objective and in accordance with one aspect of the present invention, a variable displacement swash-plate compressor is provided that includes a housing having a swash plate chamber and a cylinder bore, a drive shaft that is rotationally supported by the housing, a swash plate that is supported in the swash plate chamber and is rotational by rotation of the drive shaft, a link mechanism, a piston, a conversion mechanism, an actuator, and a control mechanism. The link mechanism is arranged between the drive shaft and the swash plate and allows an inclination angle of the swash plate to be changed with respect to a direction perpendicular to a drive shaft axis of the drive shaft. The piston is reciprocally received in the cylinder bore. The conversion mechanism causes the piston to reciprocate in the cylinder bore by a stroke corresponding to the inclination angle of the swash plate through rotation of the swash plate. The actuator is configured to change the inclination angle. The control mechanism controls the actuator. The link mechanism includes a lug member that is located in the swash plate chamber and is fixed to the drive shaft and a transmitting member that transmits rotation of the lug member to the swash plate. The actuator includes the lug member, a movable body that is configured to rotate integrally with the swash plate and to move along the drive shaft axis, thereby changing the inclination angle, and a control pressure chamber that is defined by the lug member and the movable body and is configured such that pressure in the control pressure chamber is changed by the control mechanism to move the movable body. The movable body includes an acting portion that is configured to push the swash plate with the pressure in the control pressure chamber. The swash plate includes a receiving portion that contacts and is pushed by the acting portion. The acting portion and the receiving portion contact each other at an acting position. A bottom dead center associated part for positioning the piston at a bottom dead center is defined on the swash plate. When the inclination angle is minimized, the acting position is located at a position shifted closer to the bottom dead center associated part than the drive shaft axis.
- Other aspects and advantages of the present invention will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the invention.
- The invention, together with objects and advantages thereof, may best be understood by reference to the following description of the presently preferred embodiments together with the accompanying drawings in which:
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Fig. 1 is a cross-sectional view of a compressor according to a first embodiment at the minimum displacement; -
Fig. 2 is a schematic diagram showing the control mechanism of the compressor according to the first embodiment; -
Fig. 3 is a schematic front view of the swash plate of the compressor according to the first embodiment; -
Fig. 4 is a rear view of the lug plate of the compressor according to the first embodiment; -
Fig. 5 is an enlarged partial cross-sectional view showing the lug plate and the movable body of the compressor according to the first embodiment; -
Fig. 6 is a side view of the movable body of the compressor according to the first embodiment; -
Fig. 7 is a rear view of the movable body of the compressor according to the first embodiment; -
Fig. 8 is an enlarged partial cross-sectional view of an acting position when the displacement is minimized in the compressor according to the first embodiment; -
Fig. 9 is an enlarged partial cross-sectional view of the acting position when the displacement is increased from the minimum displacement in the compressor according to the first embodiment; -
Fig. 10 is an enlarged partial cross-sectional view of an acting position when the displacement is maximized in the compressor according to the first embodiment; -
Fig. 11 is a graph showing the relationship between the inclination angle and the variable pressure difference; -
Fig. 12 is an enlarged partial cross-sectional view of a compressor according to a second embodiment when the displacement is minimized; -
Fig. 13 is a schematic front view of a swash plate of the compressor according to the second embodiment; and -
Fig. 14 is an enlarged partial cross-sectional view of the compressor according to the second embodiment when the displacement is maximized. - First and second embodiments will now be described with reference to the drawings. Compressors according to the first and second embodiments are variable displacement swash-plate compressors with single-headed pistons. These compressors are installed in vehicles and are each included in the refrigeration circuit in the air conditioner for the vehicle.
- As shown in
Fig. 1 , the compressor according to the first embodiment includes ahousing 1, adrive shaft 3, aswash plate 5, alink mechanism 7,pistons 9, pairs ofshoes actuator 13, and acontrol mechanism 15, which is illustrated inFig. 2 . - As shown in
Fig. 1 , thehousing 1 has afront housing member 17 at a front position in the compressor, arear housing member 19 at a rear position in the compressor, and acylinder block 21 and avalve assembly plate 23, which are arranged between thefront housing member 17 and therear housing member 19. - The
front housing member 17 includes afront wall 17a, which extends in the vertical direction of the compressor on the front side, and acircumferential wall 17b, which is integrated with thefront wall 17a and extends rearward from the front of the compressor. Thefront housing member 17 has a substantially cylindrical cup shape with thefront wall 17a and thecircumferential wall 17b. Furthermore, thefront wall 17a and thecircumferential wall 17b define aswash plate chamber 25 in thefront housing member 17. - The
front wall 17a has a boss 17c, which projects forward. The boss 17c accommodates ashaft sealing device 27. The boss 17c has afirst shaft hole 17d, which extends in the front-rear direction of the compressor. Thefirst shaft hole 17d accommodates afirst slide bearing 29a. - The
circumferential wall 17b has aninlet 250, which communicates with theswash plate chamber 25. Theswash plate chamber 25 is connected to a non-illustrated evaporator through theinlet 250. Since low-pressure refrigerant gas that has passed through the evaporator flows into theswash plate chamber 25 via theinlet 250, the pressures in theswash plate chamber 25 is lower than the pressure in adischarge chamber 35, which will be discussed below. - A part of the
control mechanism 15 is received in therear housing member 19. Therear housing member 19 includes a firstpressure regulation chamber 31a, asuction chamber 33, and thedischarge chamber 35. The firstpressure regulation chamber 31a is located in the central part of therear housing member 19. Thedischarge chamber 35 has an annular shape and is located in a radially outer part of therear housing member 19. Also, thesuction chamber 33 has an annular shape between the firstpressure regulation chamber 31a and thedischarge chamber 35 in therear housing member 19. Thedischarge chamber 35 is connected to a non-illustrated outlet. - The
cylinder block 21 includes cylinder bores 21a, the number of which is the same as that of thepistons 9. The cylinder bores 21a are arranged at equal angular intervals in the circumferential direction. The front end of the eachcylinder bore 21a communicates with theswash plate chamber 25. Thecylinder block 21 also includesretainer grooves 21 b, which limit the lift ofsuction reed valves 41a, which will be discussed below. - The
cylinder block 21 further includes asecond shaft hole 21c, which communicates with theswash plate chamber 25 and extends in the front-rear direction of the compressor. Thesecond shaft hole 21c accommodates a second slide bearing 29b. The first slide bearing 29a and the second slide bearing 29b may be replaced by rolling-element bearings. - The
cylinder block 21 further has aspring chamber 21d. Thespring chamber 21d is located between theswash plate chamber 25 and thesecond shaft hole 21c. Thespring chamber 21d accommodates arestoration spring 37. Therestoration spring 37 urges theswash plate 5 forward of theswash plate chamber 25 when the inclination angle is minimized. Thecylinder block 21 also includes asuction passage 39, which communicates with theswash plate chamber 25. - The
valve assembly plate 23 is located between therear housing member 19 and thecylinder block 21. Thevalve assembly plate 23 includes avalve base plate 40, asuction valve plate 41, adischarge valve plate 43, and aretainer plate 45. - The
valve base plate 40, thedischarge valve plate 43, and theretainer plate 45 includesuction ports 40a, the number of which is equal to that of the cylinder bores 21a. Furthermore, thevalve base plate 40 and thesuction valve plate 41 includedischarge ports 40b, the number of which is equal to that of the cylinder bores 21a. The cylinder bores 21a communicate with thesuction chamber 33 through thesuction ports 40a and communicate with thedischarge chamber 35 through thedischarge ports 40b. Furthermore, thevalve base plate 40, thesuction valve plate 41, thedischarge valve plate 43, and theretainer plate 45 include afirst communication hole 40c and asecond communication hole 40d. Thefirst communication hole 40c connects thesuction chamber 33 to thesuction passage 39. This causes theswash plate chamber 25 to communicate with thesuction chamber 33. - The
suction valve plate 41 is provided on the front surface of thevalve base plate 40. Thesuction valve plate 41 includessuction reed valves 41a, which are allowed to selectively open and close thesuction ports 40a by elastic deformation. Thedischarge valve plate 43 is located on the rear surface of thevalve base plate 40. Thedischarge valve plate 43 includesdischarge reed valves 43a, which are allowed to selectively open and close thedischarge ports 40b by elastic deformation. Theretainer plate 45 is provided on the rear surface of thedischarge valve plate 43. Theretainer plate 45 limits the maximum opening degree of thedischarge reed valves 43a. - The
drive shaft 3 has a cylindrical outercircumferential surface 30. Thedrive shaft 3 is inserted in the boss 17c toward the rear of thehousing 1. The front portion of thedrive shaft 3 is supported by theshaft sealing device 27 in the boss 17c and is supported by the first slide bearing 29a in thefirst shaft hole 17d. The rear portion of thedrive shaft 3 is supported by the second slide bearing 29b in thesecond shaft hole 21c. In this manner, thedrive shaft 3 is supported by thehousing 1 to be rotational about the drive shaft axis O. Thesecond shaft hole 21c and the rear end of thedrive shaft 3 define a secondpressure regulation chamber 31 b. The secondpressure regulation chamber 31b communicates with the firstpressure regulation chamber 31a through thesecond communication hole 40d. The first and secondpressure regulation chambers pressure regulation chamber 31. - O-
rings drive shaft 3. The O-rings drive shaft 3 and thesecond shaft hole 21c to seal off theswash plate chamber 25 and thepressure regulation chamber 31 from each other. - The
link mechanism 7, theswash plate 5, and theactuator 13 are mounted on thedrive shaft 3. Thelink mechanism 7 includes first and secondswash plate arms swash plate 5 shown inFig. 3 , alug plate 51 shown inFig. 4 , and first andsecond lug arms lug plate 51. The first and secondswash plate arms lug plate 51 corresponds to a lug member. For illustrative purposes, part of the firstswash plate arm 5e is omitted by using a break line inFig. 1 . The same applies toFigs. 8 to 10 , which will be discussed below. - As shown in
Fig. 3 , theswash plate 5 has a swash platemain portion 50, aswash plate weight 5c, and the first and secondswash plate arms - The swash plate
main portion 50 is shaped as a flat annular plate and has afront surface 5a and arear surface 5b. A top dead center associated part T for positioning eachpiston 9 at the top dead center and a bottom dead center associated part U for positioning eachpiston 9 at the bottom dead center are defined on the swash platemain portion 50. Also, as shown inFig. 3 , an imaginary bottom dead center plane D is defined in this compressor. The bottom dead center plane D includes the top dead center associated part T, the bottom dead center associated part U, and the drive shaft axis O. - The swash plate
main portion 50 includes a throughhole 5d. Thedrive shaft 3 is inserted in the throughhole 5d. Twoflat guide surfaces hole 5d. When thedrive shaft 3 is inserted in the throughhole 5d, the guide surfaces 52a, 52b contact the outercircumferential surface 30 of thedrive shaft 3. - The
swash plate weight 5c is provided on thefront surface 5a at a position closer to the bottom dead center associated part U than the drive shaft axis O. That is, theswash plate weight 5c is located between the drive shaft axis O and the bottom dead center associated part U. Theswash plate weight 5c has a substantially semi-circular cylindrical shape and extends from thefront surface 5a toward thelug plate 51 as shown inFig. 1 . Theswash plate weight 5c has, at its distal end, first andsecond protrusions Fig. 3 . The first andsecond protrusions - The
first protrusion 5g and thesecond protrusion 5h are provided on theswash plate weight 5c at positions on opposite sides of the bottom dead center plane D, and project forward from theswash plate 5, that is, toward theactuator 13. The first andsecond protrusions - The first and second
swash plate arms front surface 5a at positions closer to the top dead center associated part T than the drive shaft axis O, that is, at positions on the opposite side of the drive shaft axis O to the bottom dead center associated part U. In other words, the first and secondswash plate arms swash plate arm 5e and the secondswash plate arm 5f are arranged on thefront surface 5a at positions on opposite sides of the bottom dead center plane D. As shown inFig. 1 , the first and secondswash plate arms front surface 5a toward thelug plate 51. For illustrative purposes, the shapes of theswash plate weight 5c and the first and secondswash plate arms Fig. 3 . - As shown in
Fig. 4 , thelug plate 51 has a substantially annular shape with a throughhole 510. Thedrive shaft 3 is press-fitted in the throughhole 510, so that thelug plate 51 rotates integrally with thedrive shaft 3. As shown inFig. 1 , athrust bearing 55 is located between thelug plate 51 and thefront wall 17a. - As shown in
Fig. 5 , thelug plate 51 has a recessedcylinder chamber 51a, which has a cylindrical shape coaxial with and extending along the drive shaft axis O. Thecylinder chamber 51a communicates with theswash plate chamber 25 at the rear. - As shown in
Fig. 4 , thefirst lug arm 53a and thesecond lug arm 53b are provided on thelug plate 51 at positions on opposite sides of the bottom dead center plane D. On thelug plate 51, the first andsecond lug arms main portion 50 than the drive shaft axis O and extend from thelug plate 51 toward theswash plate 5. That is, the first andsecond lug arms lug plate 51. - The
lug plate 51 has first andsecond guide surfaces 57a, 57b between the first andsecond lug arms second guide surface 57b are also located on opposite sides of the bottom dead center plane D. As shown inFig. 1 , thesecond guide surface 57b is inclined such that the distance from theswash plate 5 gradually decreases from the outer circumference of thelug plate 51 toward thecylinder chamber 51a. The first guide surface 57a has the same shape as thesecond guide surface 57b. - In this compressor, the first and second
swash plate arms second lug arms swash plate 5 to thedrive shaft 3. Thelug plate 51 and theswash plate 5 are thus coupled to each other with the first and secondswash plate arms second lug arms lug plate 51 is transmitted from the first andsecond lug arms swash plate arms swash plate 5 rotates with thelug plate 51 in theswash plate chamber 25. - Since the first and second
swash plate arms second lug arms swash plate arm 5e contacts the first guide surface 57a, and the distal end of the secondswash plate arm 5f contacts thesecond guide surface 57b. The first and secondswash plate arms second guide surfaces 57a, 57b, respectively. Accordingly, theswash plate 5 is allowed to change its inclination angle relative to the direction perpendicular to the drive shaft axis O between the minimum inclination angle shown inFig. 1 and the maximum inclination angle shown inFig. 10 , while substantially maintaining the position of the top dead center associated part T. - As shown in
Fig. 5 , theactuator 13 includes thelug plate 51, amovable body 13a, and acontrol pressure chamber 13b. - As shown in
Fig. 6 , themovable body 13a is fitted about thedrive shaft 3 and located between thelug plate 51 and theswash plate 5 to move along the drive shaft axis O while sliding on thedrive shaft 3. Themovable body 13a has a substantially cylindrical shape coaxial with thedrive shaft 3. Specifically, themovable body 13a includes a firstcylindrical portion 131, a secondcylindrical portion 132, acoupling portion 133, amovable body weight 134, and arotation stopper 135. - The first
cylindrical portion 131 is located at a position facing theswash plate 5 in themovable body 13a and extends along the drive shaft axis O. The firstcylindrical portion 131 has the smallest outer diameter in themovable body 13a. As shown inFig. 5 , aring groove 131a is provided in the inner circumferential surface of the firstcylindrical portion 131. An O-ring 49c is fitted in thering groove 131a. The secondcylindrical portion 132 is located at a position on themovable body 13a that faces thelug plate 51. The secondcylindrical portion 132 has a diameter larger than that of the firstcylindrical portion 131 and has the largest outer diameter in themovable body 13a. The secondcylindrical portion 132 has aring groove 132a in the outer circumferential surface. An O-ring 49d is fitted in thering groove 132a. Thecoupling portion 133 has an outer diameter that gradually increases from the firstcylindrical portion 131 toward the secondcylindrical portion 132 and couples the firstcylindrical portion 131 and the secondcylindrical portion 132 to each other. - As shown in
Fig. 7 , themovable body weight 134 is located closer to the bottom dead center associate part U of the swash platemain portion 50 than the drive shaft axis O. That is, themovable body weight 134 is located between the drive shaft axis O and the bottom dead center associated part U. Themovable body weight 134 has a semi-columnar shape. As shown inFig. 1 , themovable body weight 134 extends from the secondcylindrical portion 132 toward theswash plate 5. Themovable body weight 134 displaces the center of gravity of themovable body 13a to a position closer to the bottom dead center associated part U than the drive shaft axis O. - As shown in
Fig. 7 , themovable body weight 134 has a symmetrical shape with respect to the bottom dead center plane D and has first and secondinclined surfaces vertical surfaces inclined surface 134a and the firstvertical surface 134c constitute afirst acting portion 14a. The secondinclined surface 134b and the secondvertical surface 134d constitute asecond acting portion 14b. Thus, in addition to achieving weight balance of themovable body 13a, themovable body weight 134 has functions of thefirst acting portion 14a and thesecond acting portion 14b, which are located on opposite sides of the bottom dead center plane D. - As shown in
Fig. 1 , the firstinclined surface 134a is inclined such that the distance from the drive shaft axis O gradually decreases from theswash plate 5 toward the secondcylindrical portion 132. The secondinclined surface 134b, which is shown inFig. 7 , has the same structure as the firstinclined surface 134a. - The first
vertical surface 134c is connected to an end of the firstinclined surface 134a that faces theswash plate 5 and vertically extends toward the bottom dead center associated part U. The secondvertical surface 134d is connected to an end of the secondinclined surface 134b that faces theswash plate 5 and vertically extends toward the bottom dead center associated part U. The firstvertical surface 134c and the secondvertical surface 134d are continuous with each other and located on opposite sides of the bottom dead center plane D. - In this compressor, the first
inclined surface 134a and the firstvertical surface 134c, that is, thefirst acting portion 14a contacts thefirst protrusion 5g shown inFig. 3 at a first acting position F1 shown inFig. 7 . Since thefirst protrusion 5g has a cylindrical shape as described above, thefirst acting portion 14a and thefirst protrusion 5g make line contact at the first acting position F1. Likewise, thesecond acting portion 14b and thesecond protrusion 5h shown inFig. 3 make line contact at a second acting position F2 shown inFig. 7 . -
Fig. 7 shows a state in which the first acting position F1 is located on the firstinclined surface 134a, and the second acting position F2 is located on the secondinclined surface 134b. However, when the inclination angle of theswash plate 5 of this compressor changes, the first acting position F1 and the second acting position F2 are moved. That is, as shown inFigs. 8 to 10 , when theswash plate 5 is moved from the minimum inclination angle to the maximum inclination angle, the first acting position F1 is moved from the firstvertical surface 134c to a position on the firstinclined surface 134a that is close to the secondcylindrical portion 132. Likewise, the second acting position F2 is moved from the secondvertical surface 134d to a position on the secondinclined surface 134b that is close to the secondcylindrical portion 132. In this compressor, not only when theswash plate 5 is at the minimum inclination angle, but also when at the maximum inclination angle, the first and second acting positions F1, F2 are located at positions shifted closer to the bottom dead center associated part U than the drive shaft axis O. That is, the first and second acting positions F1, F2 are located between the drive shaft axis O and the bottom dead center associated part U. Movement of the first and second acting positions F1, F2 will be described below. - As shown in
Fig. 6 , therotation stopper 135 is located at a position on the firstcylindrical portion 131 that faces theswash plate 5. Therotation stopper 135 has a rectangular shape as shown inFig. 7 and extends from the outer circumferential surface of the firstcylindrical portion 131 toward the top dead center associated part T of the swash platemain portion 50. Therotation stopper 135 is located between the firstswash plate arm 5e and the secondswash plate arm 5f, which are shown inFig. 3 . As theswash plate 5 rotates, therotation stopper 135 contacts the firstswash plate arm 5e or the secondswash plate arm 5f to restrict themovable body 13a from rotating about the drive shaft axis O. This allows themovable body 13a to be rotated integrally with thelug plate 51 and theswash plate 5 by rotation of thedrive shaft 3. - As shown in
Fig. 5 , thecontrol pressure chamber 13b is defined by the secondcylindrical portion 132, thecoupling portion 133, thecylinder chamber 51a, and thedrive shaft 3. Thecontrol pressure chamber 13b and theswash plate chamber 25 are sealed off from each other by the O-rings - The
drive shaft 3 has anaxial passage 3a and aradial passage 3b. Theaxial passage 3a extends from the rear end of thedrive shaft 3 toward the front end along the drive shaft axis O. Theradial passage 3b extends in a radial direction from the front end of theaxial passage 3a and opens in the outer circumferential surface of thedrive shaft 3. As shown inFig. 1 , the rear end of theaxial passage 3a communicates with thepressure regulation chamber 31. Theradial passage 3b communicates withcontrol pressure chamber 13b as shown inFig. 5 . Theaxial passage 3a and theradial passage 3b connect thepressure regulation chamber 31 to thecontrol pressure chamber 13b. - As shown in
Fig. 1 , thedrive shaft 3 has, at the front end, a threadedportion 3c. Thedrive shaft 3 is connected to a non-illustrated pulley or a non-illustrated electromagnetic clutch through the threadedportion 3c. - Each
piston 9 is accommodated in the corresponding one of the cylinder bores 21a and is allowed to reciprocate in thecylinder bore 21a. Eachpiston 9 and thevalve assembly plate 23 define acompression chamber 57 in thecorresponding cylinder bore 21a. - Each
piston 9 has an engagingportion 9a. Each engagingportion 9a accommodates a pair ofhemispherical shoes shoes swash plate 5 into reciprocation of thepistons 9. Theshoes piston 9 thus reciprocates in the corresponding cylinder bore 21a by the stroke corresponding to the inclination angle of theswash plate 5. Instead of providing theshoes rear surface 5b of the swash platemain portion 50 via a thrust bearing, and the wobble plate and thepistons 9 are connected to each other with connecting rods. - As shown in
Fig. 2 , thecontrol mechanism 15 includes a low-pressure passage 15a, a high-pressure passage 15b, acontrol valve 15c, anorifice 15d, theaxial passage 3a, and theradial passage 3b. - The low-
pressure passage 15a is connected to thepressure regulation chamber 31 and thesuction chamber 33. The low-pressure passage 15a, theaxial passage 3a, and theradial passage 3b connect thecontrol pressure chamber 13b, thepressure regulation chamber 31, and thesuction chamber 33 to one another. The high-pressure passage 15b is connected to thepressure regulation chamber 31 and thedischarge chamber 35. The high-pressure passage 15b, theaxial passage 3a, and theradial passage 3b connect thecontrol pressure chamber 13b, thepressure regulation chamber 31, and thedischarge chamber 35 to one another. - The
control valve 15c is arranged in the low-pressure passage 15a. The low-pressure control valve 15c is allowed to adjust the opening degree of the low-pressure passage 15a based on the pressure in thesuction chamber 33. The high-pressure passage 15b also has theorifice 15d. - In this compressor, a pipe connected to the evaporator is connected to the
inlet 250 shown inFig. 1 , and a pipe connected to the condenser is connected to the outlet. The condenser is connected to the evaporator via a pipe and an expansion valve. These components, which include the compressor, the evaporator, the expansion valve, and the condenser, constitute the refrigeration circuit in the air conditioner for a vehicle. The illustration of the evaporator, the expansion valve, the condenser, and the pipes is omitted. - In the compressor having the above-described configuration, the
drive shaft 3 rotates to rotate theswash plate 5, thus reciprocating eachpiston 9 in thecorresponding cylinder bore 21a. This varies the volume of eachcompression chamber 57 in accordance with the piston stroke. Thus, the refrigerant that has been drawn from the evaporator into theswash plate chamber 25 through theinlet 250 flows through thesuction passage 39 and thesuction chamber 33 and is compressed in thecompression chambers 57. The refrigerant that is compressed in thecompression chambers 57 is discharged to thedischarge chamber 35 and is discharged to the condenser through the outlet. - The actuator 13 changes the inclination angle of the
swash plate 5 to increase or decrease the stroke of thepistons 9, thereby varying the displacement of the compressor. - Specifically, when the
control valve 15c of thecontrol mechanism 15 shown inFig. 2 reduces the opening degree of the low-pressure passage 15a, the pressure in thepressure regulation chamber 31 is increased, and the pressure in thecontrol pressure chamber 13b is increased. This causes themovable body 13a to move along the drive shaft axis O toward theswash plate 5 as shown inFig. 8 , while moving away from thelug plate 51. - Accordingly, at the first acting position F1 of the compressor, the
first acting portion 14a shown inFig. 7 pushes thefirst protrusion 5g shown inFig. 3 toward the rear of theswash plate chamber 25. Likewise, at the second acting position F2, thesecond acting portion 14b shown inFig. 7 pushes thesecond protrusion 5h shown inFig. 3 toward the rear of theswash plate chamber 25. As described above, the first and second acting positions F1, F2 are located at positions shifted closer to the bottom dead center associated part U than the drive shaft axis O. That is, the first and second acting positions F1, F2 are located between the drive shaft axis O and the bottom dead center associated part U. Thus, themovable body 13a pushes theswash plate 5 at a position shifted closer to the bottom dead center associated part U than the drive shaft axis O via the first andsecond acting portions second protrusions swash plate arms second guide surfaces 57a, 57b, respectively, toward the drive shaft axis O as shown inFig. 8 . - Accordingly, the
swash plate 5 reduces the angle relative to the direction perpendicular to the drive shaft axis O, or the inclination angle, while substantially maintaining the position of the top dead center associated part T. This reduces the stroke of thepistons 9 and the displacement of the compressor per rotation of thedrive shaft 3. The reduction in the inclination angle causes theswash plate 5 contact therestoration spring 37. The inclination angle of theswash plate 5 shown inFigs. 1 and8 corresponds to the minimum inclination angle in the compressor. - In contrast, when the
control valve 15c of thecontrol mechanism 15 shown inFig. 2 increases the opening degree of the low-pressure passage 15a, the pressure in thepressure regulation chamber 31 and thus the pressure in thecontrol pressure chamber 13b become substantially equal to the pressure in thesuction chamber 33. Thus, reaction force that acts on theswash plate 5 from components such as thepistons 9 causes themovable body 13a to move along the drive shaft axis O from theswash plate 5 toward thelug plate 51 as shown inFigs. 9 and10 . This causes themovable body 13a to move deeply into thecylinder chamber 51a. - The reaction force acting on the
swash plate 5 and the urging force of therestoration spring 37 cause the first and secondswash plate arms second guide surfaces 57a, 57b, respectively, to move away from the drive shaft axis O. - The
swash plate 5 thus increases the inclination angle while substantially maintaining the position of the top dead center associated part T. This increases the stroke of thepistons 9 and thus increases the displacement of the compressor per rotation of thedrive shaft 3.Fig. 9 illustrates a state in which the inclination angle of theswash plate 5 is slightly increased. The inclination angle of theswash plate 5 shown inFig. 10 corresponds to the maximum inclination angle in the compressor. - As described above, in this compressor, the first and
second acting portions second protrusions first acting portion 14a and thefirst protrusion 5g make line contact, and the second acting position F2, where thesecond acting portion 14b and thesecond protrusion 5h make line contact, are located at positions shifted closer to the bottom dead center associated part U than the drive shaft axis O not only when theswash plate 5 is at the minimum inclination angle, but also when theswash plate 5 is at the maximum inclination angle. When decreasing the inclination angle of theswash plate 5, themovable body 13a pushes theswash plate 5 along the drive shaft axis O via the first and second acting positions F1, F2. - Since the reaction force acting on the
swash plate 5 is small at a position between the drive shaft axis O and the bottom dead center associated part U, particularly at a position close to the bottom dead center associated part U, themovable body 13a is unlikely to be influenced by the reaction force. That is, the compressor reduces the load on themovable body 13a when minimizing the inclination angle. Thus, when reducing the inclination angle in the compressor, themovable body 13a is moved without increasing the variable pressure difference to obtain a large thrust. This allows the compressor to quickly change the inclination angle in response to changes in the driving state of the vehicle. Also, the configuration allows the size of the compressor to be reduced. These operations will be described based on comparison with examples. - The compressor of the comparative example includes partially modified versions of the
swash plate 5 and themovable body 13a of the compressor according to the first embodiment. Specifically, theswash plate weight 5c does not have the first andsecond protrusions movable body 13a does not have themovable body weight 134. In this configuration of the comparative example, the rear end of the firstcylindrical portion 131 of themovable body 13a contacts thefront surface 5a of the swash platemain portion 50 at a position around the throughhole 5d. Thus, in the comparative example, themovable body 13a and theswash plate 5 contact each other at a position substantially on the drive shaft axis O, and the acting position is located about thedrive shaft 3. - The reaction force that acts on the
swash plate 5 from components such as thepistons 9 increases on the swash platemain portion 50 as the distance from the top dead center associated part T decreases. More specifically, when theswash plate 5 rotates in the direction of the solid arrow inFig. 13 , a position slightly before the top dead center associated part T in the rotation direction is a maximum load position P1, where the reaction force from components such as thepistons 9 is maximized. - Thus, in the compressor of the comparison example, in which the acting position is located about the
drive shaft 3, the acting position is located close to the top dead center associated part T, and themovable body 13a is easily influenced by the reaction force. Therefore, as indicated by the graph ofFig. 11 , in the compressor of the comparative example, the variable pressure difference needs to be increased to move themovable body 13a with a greater thrust as the inclination angle of theswash plate 5 is reduced. - Further, if the compressor of the comparison example has a small displacement per rotation of the
drive shaft 3 and the pressure in thecontrol pressure chamber 13b cannot be increased, the variable pressure difference cannot be increased. Thus, to move themovable body 13a with a great thrust, the size of themovable body 13a may be increased to enlarge the pressure receiving area. However, this would increase the size of the compressor. - In contrast, in the compressor according to the first embodiment, not only when the
swash plate 5 is at the minimum inclination angle, but also at the maximum inclination angle, the first and second acting positions F1, F2 are located at positions shifted closer to the bottom dead center associated part U than the drive shaft axis O. Thus, the first and second acting positions F1, F2 are separated away from the top dead center associated part T, which makes themovable body 13a less prone to influence of the reaction force. That is, the load on themovable body 13a when decreasing the inclination angle is reduced, so that themovable body 13a is moved without increasing the variable pressure difference. Accordingly, in the compressor according to the first embodiment, the variable pressure difference is reduced over the entire range and made substantially constant as indicated by the graph ofFig. 11 when the inclination angle is changed. - As described above, in the compressor according to the first embodiment, the
movable body 13a is moved without increasing the variable pressure difference. Thus, even if the displacement per rotation of the drive shaft is small, themovable body 13a is moved reliably. Therefore, themovable body 13a of the compressor does need to be enlarged to increase the pressure receiving area, and the compressor is reduced in size. - In the compressor according to the first embodiment, the first and second acting positions F1, F2 are shifted closer to the bottom dead center associated part U than the drive shaft axis O. Thus, compared to the compressor of the comparison example, in which the acting position is close to the top dead center associated part T, the stroke of the
movable body 13a when the inclination angle of theswash plate 5 is changed is increased. - In the compressor of the comparative example, since the acting position is located about the drive shaft axis O, the distance between the acting position and the drive shaft axis O is constant even if the inclination angle of the
swash plate 5 is changed. In contrast, in the compressor according to the first embodiment, the first and second acting positions F1, F2 are moved in a direction from the bottom dead center associated part U toward the drive shaft axis O by moving theswash plate 5 from the minimum inclination angle to the maximum inclination angle as shown inFigs. 8 to 10 . Hereinafter, the fist acting position F1 will be described. - As described above, when the inclination angle of the
swash plate 5 is reduced, thefirst acting portion 14a pushes thefirst protrusion 5g toward the rear of theswash plate chamber 25 at the first acting position F1. Thus, as the inclination angle of theswash plate 5 decreases, the first acting position F1 moves from the firstinclined surface 134a toward the firstvertical surface 134c. When the inclination angle of theswash plate 5 is minimized, the first acting position F1 is located on the firstvertical surface 134c. That is, when theswash plate 5 is at the minimum inclination angle, the firstvertical surface 134c and thefirst protrusion 5g make line contact at the first acting position F1. The position of the first acting position F1 at this time is defined as an initial position A. - When the pressure in the
pressure regulation chamber 31 is lowered and themovable body 13a is slightly moved from theswash plate 5 toward thelug plate 51 along the drive shaft axis O as shown inFig. 9 , the inclination angle of theswash plate 5 is slightly increased. At this time, the firstinclined surface 134a and thefirst protrusion 5g make line contact at the first acting position F1. More specifically, a part of the firstinclined surface 134a that is close to the firstvertical surface 134c and thefirst protrusion 5g make line contact. That is, when the inclination angle of theswash plate 5 is increased slightly from the minimum inclination angle, the first acting position F1 is moved from the initial position A toward thelug plate 51 along the drive shaft axis O by a distance X1. The first acting position F1 is also moved in a direction from the bottom dead center associated part U toward the drive shaft axis O by a distance Y1. In other words, due to a slight increase in the inclination angle of theswash plate 5, the first acting position F1 is moved from the initial position A by the distance Y1 in a direction from the bottom dead center associated part U toward the drive shaft axis O. For illustrative purposes, the initial position A is illustrated as a circle of a dashed line inFigs. 9 and10 . - Further, when the inclination angle of the
swash plate 5 is increased, thefirst protrusion 5g slides on the firstinclined surface 134a toward the secondcylindrical portion 132. When the inclination angle of theswash plate 5 is maximized as shown inFig. 10 , a part of the firstinclined surface 134a that is close to the secondcylindrical portion 132 and thefirst protrusion 5g make line contact at the first acting position F1. That is, the first acting position F1 is moved from the initial position A toward thelug plate 51 along the drive shaft axis O by a distance X2, which is greater than the distance X1. The first acting position F1 is also moved in a direction from the bottom dead center associated part U toward the drive shaft axis O by a distance Y2, which is greater than the distance Y1. Accordingly, due to the change of the inclination angle of theswash plate 5 from the minimum inclination angle to the maximum inclination angle, the first acting position F1 is moved from the initial position A by the distance Y2 in a direction from the bottom dead center associated part U toward the drive shaft axis O. The same applies to the second acting position F2. - Thus, in the compressor according to the first embodiment, if the range of the inclination angle of the
swash plate 5 is the same, when the inclination angle is increased, the stroke of themovable body 13a along the drive shaft axis O is small compared to a case in which the distance between the acting position and the drive shaft axis O is constant even if the inclination angle is changed. Thus, in the compressor according to the first embodiment, although themovable body 13a pushes theswash plate 5 along the drive shaft axis O at a position relatively close to the bottom dead center associated part U via the first and second acting positions F1, F2, the stroke of themovable body 13a is minimized. The compressor according to the first embodiment thus prevents the shaft length from being increased. - Therefore, the compressor according to the first embodiment has a high controllability and an improved mountability.
- Further, the reaction force that acts from the
pistons 9 to theswash plate 5 during operation of the compressor generates moment that acts to rotate theswash plate 5 in a direction other than the direction in which the inclination angle is changed. This creates a warp in theswash plate 5. In this respect, the guide surfaces 52a, 52b in the throughhole 5d of the compressor slide on the outercircumferential surface 30 of thedrive shaft 3 in response to changes in the inclination angle of theswash plate 5. Then, theswash plate 5 is guided by thelink mechanism 7 and thedrive shaft 3 along the drive shaft axis O and in the direction of the inclination angle, so that the inclination angle is changed as described above. At this time, the guide surfaces 52a, 52b allow theswash plate 5 to easily contact the outercircumferential surface 30 of thedrive shaft 3 at two points on opposite sides of the drive shaft axis O. Therefore, the compressor reliably prevents theswash plate 5 from being warped by the moment. Since the compressor has no sleeve, the number of components is reduced, and the manufacturing costs are reduced, accordingly. - Further, when the inclination angle of the
swash plate 5 is reduced, thefirst acting portion 14a pushes thefirst protrusion 5g at the first acting position F1, and thesecond acting portion 14b pushes thesecond protrusion 5h at the second acting position F2. In this manner, themovable body 13a pushes theswash plate 5 along the drive shaft axis O and at two positions, which are the first acting position F1 and the second acting position F2 with reference to the bottom dead center plane D. This allows themovable body 13a of the compressor to decrease the inclination angle of theswash plate 5 rapidly. - Further, the swash plate
main portion 50 has theswash plate weight 5c on thefront surface 5a, and themovable body 13a has themovable body weight 134. Theswash plate weight 5c and themovable body weight 134 are located at positions closer to the bottom dead center associated part U than the drive shaft axis O. Thus, even though theswash plate arms front surface 5a, theswash plate weight 5c and themovable body weight 134 reliably maintain the weight balance between the top dead center associated part T and the bottom dead center associated part U with the drive shaft axis O in between. Therefore, rotation of thedrive shaft 3 reliably rotates thelink mechanism 7, theactuator 13, and theswash plate 5, and vibration during operation is suppressed. - Also, the
swash plate weight 5c and themovable body weight 134 eliminate the necessity for providing a weight for reliably maintaining the weight balance to thelug plate 51. This prevents the size of thelug plate 51 from being increased. Thus, thelug plate 51 is reliably prevented from agitating lubricant in theswash plate chamber 25. Therefore, the lubricity of the lubricant does not deteriorate because of heating of the lubricant that would be caused by such agitation. Accordingly, sliding parts in the compressor are prevented from being unduly worn. - Further, since the
swash plate weight 5c has the first andsecond protrusions swash plate 5 is easy to produce. Likewise, since themovable body weight 134 also functions as the first andsecond acting portions movable body 13a is easy to produce. - In the compressor according to the second embodiment, the first and
second protrusions single protrusion 5i on theswash plate weight 5c as shown inFig. 12 . Theprotrusion 5i also functions as a receiving portion. Also, themovable body weight 134 of the compressor according to the first embodiment is replaced by amovable body weight 136 on themovable body 13a. - The
protrusion 5i is located on the front side of theswash plate weight 5c, that is, on the side of theswash plate weight 5c that faces themovable body 13a. Specifically, as shown inFig. 13 , theprotrusion 5i is located at the distal end of theswash plate weight 5c and in an area between the bottom dead center associated part U and a position on the opposite side of the drive shaft axis O from the maximum load position P1 (hereinafter, referred to as an opposite position P2). The area is indicated by the arrow of a broken line. Theprotrusion 5i has a semispherical shape. As inFig. 3 , for illustrative purposes, the shapes of theswash plate weight 5c and theprotrusion 5i are simplified inFig. 10 . - Like the above described
movable body weight 134, themovable body weight 136 is arranged on themovable body 13a at a position that is closer to the bottom dead center associated part U of the swash platemain portion 50 than the drive shaft axis O as shown inFig. 12 . Themovable body weight 136 extends from the secondcylindrical portion 132 toward theswash plate 5. Themovable body weight 136 has aninclined surface 136a and avertical surface 136b. Theinclined surface 136a is inclined such that the distance from the drive shaft axis O gradually decreases from theswash plate 5 toward the secondcylindrical portion 132. Thevertical surface 136b is connected to an end of theinclined surface 136a that faces theswash plate 5 and extends vertically toward the bottom dead center associated part U. Theinclined surface 136a and thevertical surface 136b constitute an actingportion 16. Thus, themovable body weight 136 has a function of the actingportion 16 in addition to the function for creating weight balance in themovable body 13a. - The acting
portion 16, which is constituted by theinclined surface 136a and thevertical surface 136b, and theprotrusion 5i of theswash plate 5 make point contact at an acting position F3. When the inclination angle of theswash plate 5 is changed from the minimum inclination angle shown inFig. 12 to the maximum inclination angle shown inFig. 14 , the acting position F3 is moved. Specifically, as shown in the drawings, when theswash plate 5 is at the minimum inclination angle, the acting position F3 is located on thevertical surface 136b. That is, when theswash plate 5 is at the minimum inclination angle, thevertical surface 136b and theprotrusion 5i make point contact at the acting position F3. In contrast, when theswash plate 5 is at the maximum inclination angle as shown inFig. 14 , the acting position F3 is located on theinclined surface 136a. That is, when theswash plate 5 is at the maximum inclination angle, theinclined surface 136a and theprotrusion 5i make point contact at the acting position F3. - As described above, due to the change of the inclination angle of the
swash plate 5 from the minimum inclination angle to the maximum inclination angle, the third acting position F3 is moved in a direction from the bottom dead center associated part U toward the drive shaft axis O in this compressor. In this compressor also, not only when theswash plate 5 is at the minimum inclination angle, but also at the maximum inclination angle, the third acting position F3 is located at a position shifted closer to the bottom dead center associated part U than the drive shaft axis O. Since theprotrusion 5i is located at a position between the opposite position P2 and the bottom dead center associated part U as shown inFig. 13 , the acting position F3 of this compressor is defined on the swash platemain portion 50 in an area between the opposite position P2 and the bottom dead center associated part U. The other components of the compressor of the second embodiment are configured identically with the corresponding components of the compressor of the first embodiment. Accordingly, these components are identified by the same reference numbers, and detailed description thereof is omitted herein. - In the compressor of the second embodiment, the
inclined surface 136a and thevertical surface 136b of themovable body weight 136, that is, the actingportion 16 and theprotrusion 5i make point contact at the single acting position F3. Therefore, the actingportion 16 and theprotrusion 5i, and thus, themovable body 13a and theswash plate 5 are easy to produce. - The acting position F3 is defined on the swash plate
main portion 50 in an area between the opposite position P2 and the bottom dead center associated part U. In the swash platemain portion 50, the reaction force from components such as thepistons 9 is maximized at the maximum load position P1. In contrast, the reaction force acting on theswash plate 5 is small between the opposite position P2 and the bottom dead center associated part U. Thus, the load on themovable body 13a is reliably reduced when the inclination angle of theswash plate 5 is reduced. Accordingly, even though themovable body 13a has the single acting position F3, themovable body 13a reliably pushes theswash plate 5 along the drive shaft axis O via the acting position F3. The other operations of the compressor are the same as the corresponding operations of the compressor of the first embodiment. - Although only the first and second embodiments of the present invention have been described so far, the present invention is not limited to the first and second embodiments, but may be modified as necessary without departing from the scope of the invention.
- For example, in the compressor according to the first embodiment, the shapes of the first and
second acting portions swash plate 5 is at the maximum inclination angle, the first and second acting positions F1, F2 are shifted beyond the drive shaft axis O and reach positions on the swash platemain portion 50 that are close to the top dead center associated part T. The same modification may be applied to the compressor according to the second embodiment. - The compressor according to the first embodiment may be configured such that, while the inclination angle of the
swash plate 5 is increased from the minimum inclination angle to a predetermined inclination angle, the first and second acting positions F1, F2 are moved in a direction from the bottom dead center associated part U toward the drive shaft axis O, and while the inclination angle of theswash plate 5 is increased from the predetermined inclination angle to the maximum inclination angle, the first and second acting positions F1, F2 do not move. The same modification may be applied to the compressor according to the second embodiment. - Further, in the compressor according to the first embodiment, the
movable body 13a may include dedicated first andsecond acting portions movable body weight 134. The same modification may be applied to the compressor according to the second embodiment. - In the compressor according to the first embodiment, the first and
second acting portions second protrusions portion 16 and theprotrusion 5i may be configured to make line contact. - Further, regarding the
control mechanism 15 of the compressor according to the first and second embodiments, thecontrol valve 15c may be provided in the high-pressure passage 15b, and theorifice 15d may be provided in the low-pressure passage 15a. In this case, thecontrol valve 15c is allowed to adjust the flow rate of high-pressure refrigerant flowing through the high-pressure passage 15b. This allows the high-pressure in thedischarge chamber 35 to promptly increase the pressure in thecontrol pressure chamber 13b and to promptly reduce the displacement. Also, thecontrol valve 15c may be replaced by a three-way valve connected to the low-pressure passage 15a and the high-pressure passage 15b. In this case, the opening degree of the three-way valve is adjusted to regulate the flow rate of refrigerant flowing through the low-pressure passage 15a and the high-pressure passage 15b. - Therefore, the present examples and embodiments are to be considered as illustrative and not restrictive and the invention is not to be limited to the details given herein, but may be modified within the scope and equivalence of the appended claims.
Claims (8)
- A variable displacement swash-plate compressor comprising:a housing (1) having a swash plate chamber (25) and a cylinder bore (21a);a drive shaft (3) that is rotationally supported by the housing (1);a swash plate (5) that is supported in the swash plate chamber (25) and is rotational by rotation of the drive shaft (3);a link mechanism (7) arranged between the drive shaft (3) and the swash plate (5),
wherein the link mechanism (7) allows an inclination angle of the swash plate (5) to be changed with respect to a direction perpendicular to a drive shaft axis (O) of the drive shaft (3);a piston (9) reciprocally received in the cylinder bore (21a);a conversion mechanism (11a, 11b) that causes the piston (9) to reciprocate in the cylinder bore (21a) by a stroke corresponding to the inclination angle of the swash plate (5) through rotation of the swash plate (5);an actuator (13) configured to change the inclination angle; anda control mechanism (15) that controls the actuator (13), whereinthe link mechanism (7) includesa lug member (51) that is located in the swash plate chamber (25) and is fixed to the drive shaft (3), anda transmitting member (5e, 5f) that transmits rotation of the lug member (51) to the swash plate (5),the actuator (13) includesthe lug member (51),a movable body (13a) that is configured to rotate integrally with the swash plate (5) and to move along the drive shaft axis (O), thereby changing the inclination angle, anda control pressure chamber (13b) that is defined by the lug member (51) and the movable body (13a) and is configured such that pressure in the control pressure chamber (13b) is changed by the control mechanism (15) to move the movable body (13a),the variable displacement swash-plate compressor being characterized in thatthe movable body (13a) includes an acting portion (14a, 14b; 16) that is configured to push the swash plate (5) with the pressure in the control pressure chamber (13b),the swash plate (5) includes a receiving portion (5g, 5h; 5i) that contacts and is pushed by the acting portion (14a, 14b; 16),the acting portion (14a, 14b; 16) and the receiving portion (5g, 5h; 5i) contact each other at an acting position (F1, F2; F3),a bottom dead center associated part (U) for positioning the piston (9) at a bottom dead center is defined on the swash plate (5), andwhen the inclination angle is minimized, the acting position (F1, F2; F3) is located at a position shifted closer to the bottom dead center associated part (U) than the drive shaft axis (O). - The variable displacement swash-plate compressor according to claim 1, wherein the transmitting member (5e, 5f) is located on the swash plate (5) and is positioned on an opposite side of the drive shaft axis (O) from the bottom dead center associated part (U),
the swash plate (5) has a swash plate weight (5c) that is located at a position closer to the bottom dead center associated part (U) than the drive shaft axis (O) and protrudes toward the acting portion (14a, 14b; 16), and
the receiving portion (5g, 5h; 5i) is located on the swash plate weight (5c). - The variable displacement swash-plate compressor according to claim 2, wherein
the movable body (13a) has a movable body weight (134; 136) that is located a position closer to the bottom dead center associated part (U) than the drive shaft axis (O), and
the movable body weight functions as the acting portion (14a, 14b; 16). - The variable displacement swash-plate compressor according to any one of claims 1 to 3, wherein
the acting position is a first acting position (F1),
a second acting position (F2) is defined that constitutes a pair with the first acting position (F1), wherein the first acting position (F1) and the second acting position (F1) are located on opposite sides of a bottom dead center plane (D), which includes the bottom dead center associated part (U) and the drive shaft axis (O),
the acting portion is a first acting portion (14a) that contacts the receiving portion (5g) at the first acting position (F1), and
a second acting portion (14b) is provided that contacts the receiving portion (5h) at the second acting position (F2). - The variable displacement swash-plate compressor according to claim 1 or 2,
wherein the acting position (F3) is a single position. - The variable displacement swash-plate compressor according to claim 5, wherein, in relation to a maximum load position (P1), where reaction force acting from the piston (9) is maximized on the swash plate (5), the acting position (F3) is located in an area between the bottom dead center associated part (U) and a position on an opposite side of the drive shaft axis (O) from the bottom dead center associated part (U).
- The variable displacement swash-plate compressor according to any one of claims 1 to 6, wherein, when the inclination angle is increased, the acting position (F1, F2; F3) is moved in a direction from the bottom dead center associated part (U) toward the drive shaft axis (O).
- The variable displacement swash-plate compressor according to any one of claims 1 to 7, wherein
the swash plate (5) has a through hole (5d), which slides on an outer circumference of the drive shaft (3) in response to changes in the inclination angle, and
the swash plate (5) is guided by the link mechanism (7) and the through hole (5d) along the drive shaft axis (O) and in a direction of the inclination angle, thereby changing the inclination angle.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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JP2014239917A JP2016102417A (en) | 2014-11-27 | 2014-11-27 | Variable displacement type swash plate compressor |
Publications (2)
Publication Number | Publication Date |
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EP3026265A1 true EP3026265A1 (en) | 2016-06-01 |
EP3026265B1 EP3026265B1 (en) | 2017-06-28 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP15195805.5A Active EP3026265B1 (en) | 2014-11-27 | 2015-11-23 | Variable displacement swash-plate compressor |
Country Status (5)
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US (1) | US20160153435A1 (en) |
EP (1) | EP3026265B1 (en) |
JP (1) | JP2016102417A (en) |
KR (1) | KR101788935B1 (en) |
CN (1) | CN105649921B (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JP6146263B2 (en) * | 2013-11-06 | 2017-06-14 | 株式会社豊田自動織機 | Variable capacity swash plate compressor |
US10273051B2 (en) | 2016-07-15 | 2019-04-30 | Ring Container Technologies | Container and handle system |
JP2018031364A (en) * | 2016-08-26 | 2018-03-01 | サンデン・オートモーティブコンポーネント株式会社 | Variable displacement compressor |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS52131204A (en) | 1976-04-23 | 1977-11-04 | Borg Warner | Controllers for variable discharge compressors |
US20140127045A1 (en) * | 2012-11-05 | 2014-05-08 | Kabushiki Kaisha Toyota Jidoshokki | Swash plate type variable displacement compressor |
WO2014157311A1 (en) * | 2013-03-29 | 2014-10-02 | 株式会社 豊田自動織機 | Variable displacement swash-plate compressor |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62225782A (en) * | 1986-03-27 | 1987-10-03 | Nippon Denso Co Ltd | Variable displacement oscillating plate type compressor |
JPH05312144A (en) * | 1992-05-08 | 1993-11-22 | Sanden Corp | Variable displacement swash plate type compressor |
JP4976731B2 (en) * | 2006-04-07 | 2012-07-18 | カルソニックカンセイ株式会社 | Variable capacity compressor |
JP5519193B2 (en) * | 2009-06-05 | 2014-06-11 | サンデン株式会社 | Variable capacity compressor |
-
2014
- 2014-11-27 JP JP2014239917A patent/JP2016102417A/en not_active Withdrawn
-
2015
- 2015-11-20 US US14/947,143 patent/US20160153435A1/en not_active Abandoned
- 2015-11-23 EP EP15195805.5A patent/EP3026265B1/en active Active
- 2015-11-23 CN CN201510821377.8A patent/CN105649921B/en active Active
- 2015-11-25 KR KR1020150165475A patent/KR101788935B1/en active IP Right Grant
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS52131204A (en) | 1976-04-23 | 1977-11-04 | Borg Warner | Controllers for variable discharge compressors |
US20140127045A1 (en) * | 2012-11-05 | 2014-05-08 | Kabushiki Kaisha Toyota Jidoshokki | Swash plate type variable displacement compressor |
WO2014157311A1 (en) * | 2013-03-29 | 2014-10-02 | 株式会社 豊田自動織機 | Variable displacement swash-plate compressor |
Also Published As
Publication number | Publication date |
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EP3026265B1 (en) | 2017-06-28 |
KR101788935B1 (en) | 2017-10-20 |
JP2016102417A (en) | 2016-06-02 |
US20160153435A1 (en) | 2016-06-02 |
KR20160064007A (en) | 2016-06-07 |
CN105649921A (en) | 2016-06-08 |
CN105649921B (en) | 2018-04-03 |
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