Swash plate type compressor of variable capacity type

This application is based on Japanese Patent Application No. 2000-183159 filed Jun. 19, 2000, the contents of which are incorporated hereinto by reference.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates in general to a swash plate type compressor of variable capacity type, and more particularly to a technique for assuring stable behavior of the swash plate which is rotated during operation of the compressor.

2. Discussion of the Related Art

One example of a swash plate type compressor of variable capacity type is disclosed in JP-A-7-91366. The compressor disclosed in the publication comprises (a) a housing having a plurality of cylinder bores formed therein such that the cylinder bores are equiangularly arranged along a circle whose center lies on a centerline of the housing; (b) a rotary drive shaft which is rotatably supported by the housing such that an axis of rotation of the rotary drive shaft is aligned with the centerline of the housing; (c) a swash plate which is carried by the rotary drive shaft such that an angle of inclination of the swash plate with respect to a plane perpendicular to the axis of rotation of the rotary drive shaft is variable, and such that the swash plate is rotated together with the rotary drive shaft; (d) a plurality of pistons which are slidably fitted in the respective cylinder bores and which engage a radially outer portion of the swash plate, each piston being reciprocated between a compression stroke end and a suction stroke end during rotation of the swash plate; and (e) a swash plate angle adjusting device for adjusting the angle of inclination of the swash plate between a maximum inclination angle and a minimum inclination angle.

The compressor further comprises an engaging protrusion which extends from a body portion of the swash plate at an angle with respect to the centerline of the body portion. The engaging protrusion has at its free end a spherical portion which is held in engagement with an engaging hole formed in a rotary member fixed to the rotary drive shaft. The swash plate has a central through-hole formed through the thickness at its central portion. The rotary drive shaft extends through the through-hole for supporting the swash plate. The configuration of the through-hole permits a tilting motion of the swash plate between a perpendicular posture in which the swash plate is perpendicular to the rotation axis of the rotary drive shaft and an inclined posture in which the swash plate is inclined by a predetermined angle with respect to the rotation axis, namely, a rotary motion of the swash plate for changing its inclination angle.

While the swash plate which is inclined with respect to the rotation axis of the rotary drive shaft is rotated, the plurality of pistons which engage the radially outer portion of the swash plate are reciprocated within the respective cylinder bores, for thereby changing the volume of the pressurizing chamber which is defined by the end face of each piston and the inner surface of the cylinder bore. Described more specifically, the volume of the pressurizing chamber is increased during a suction stroke of the piston in which a gas is sucked into the pressurizing chamber, while the volume of the pressurizing chamber is decreased during a compression stroke of the piston in which the gas is compressed. The volume of the pressurizing chamber is minimum when the piston is at its compression stroke end, and the volume of the pressurizing chamber is maximum when the piston is at its suction stroke end. The radially outer portion of the swash plate includes a compression-end circumferential part which engages each piston when each piston is at its compression stroke end, and a suction-end circumferential part which engages each piston when each piston is at its suction stroke end. Since the body portion of the swash plate generally has a circular shape, the compression-end circumferential part and the suction-end circumferential part of the swash plate are opposite to each other diametrically of the rotary drive shaft. While the swash plate which is inclined by a predetermined angle is rotated for reciprocating each piston, the swash plate receives at one of its opposite inclined surfaces the reaction force from the piston which is at its compression stroke. In this case, owing to the effect of the inclined surface, a force acts on the swash plate in a direction from its suction-end circumferential part toward the compression-end circumferential part. Accordingly, the swash plate is rotated together with the rotary drive shaft while a circumferential portion of the inner circumferential surface of the central through-hole of the swash plate, which circumferential portion is on the side of the suction-end circumferential part of the swash plate, is held in pressing contact with the corresponding circumferential portion of the outer circumferential surface of the rotary drive shaft. The above-indicated circumferential portion of the inner circumferential surface of the thorough-hole on the side of the suction-end circumferential part of the swash plate is hereinafter referred to as “suction-end-side inner circumferential surface” of the through-hole.

Where the swash plate is rotated while it is placed in the substantially perpendicular posture relative to the rotation axis of the rotary drive shaft, the positions of the piston at its compression stroke end and suction stroke end in the axial direction of the rotary drive shaft are substantially identical with each other, causing substantially no change in the volume of the pressurizing chamber. Since the compression of the gas is not substantially effected in this state, the reaction force acting on the swash plate from the piston is substantially zero. In addition, the opposite surfaces of the swash plate which receive the reaction force of the piston are perpendicular to the rotation axis, in the substantially perpendicular posture of the swash plate. Accordingly, the above-indicated force acting on the swash plate owing to the effect of the inclined surface in the direction from the suction-end circumferential part toward the compression-end circumferential part of the swash plate is substantially zero or considerably small. It is, however, desirable that the suction-end-side inner circumferential surface of the through-hole of the swash plate is kept in pressing contact with the outer circumferential surface of the drive shaft by the force acting on the swash plate in the direction from its suction-end circumferential part toward the compression-end circumferential part. If the circumferential portion of the inner circumferential surface of the through-hole of the swash plate on the side of its compression-end circumferential part (hereinafter referred to as a “compression-end-side inner circumferential surface” of the through-hole) were held in pressing contact with the outer circumferential surface of the rotary drive shaft, the swash plate would be moved in its radial direction from its suction-end circumferential part toward the compression-end circumferential part during its tilting motion to increase the inclination angle. This movement causes undesirable butting noise due to a butting contact of the suction-end-side inner circumferential surface of the through-hole of the swash plate with the rotary drive shaft. Further, since the volume of the pressurizing chamber is abruptly changed due to the above-described movement of the swash plate, the discharge capacity of the compressor is also abruptly changed. To avoid these undesirable phenomena, it is preferable that the suction-end-side inner circumferential surface of the through-hole of the swash plate is always kept in pressing contact with the outer circumferential surface of the rotary drive shaft, irrespective of the inclination angle of the swash plate.

SUMMARY OF THE INVENTION

For permitting the swash plate to receive the force acting thereon in the direction from its suction-end circumferential part toward the compression-end circumferential part even while the swash plate is placed in the substantially perpendicular posture relative to the rotation axis, it is effective to design the swash plate such that the center of gravity of the swash plate is located on one side of the rotation axis of the rotary drive shaft, which one side corresponds to the compression-end circumferential part of the swash plate. The thus designed swash plate is subjected to the force acting thereon in the direction from the suction-end circumferential part toward the compression-end circumferential part, based on a centrifugal force. It is, however, desirable to minimize the magnitude of the centrifugal force because the centrifugal force deteriorates a dynamic balance of the rotating unit of the compressor.

It is an object of the present invention to provide a swash plate type compressor of variable capacity type, wherein the swash plate is rotated with the suction-end-side inner circumferential surface of the through-hole formed therein being kept in pressing contact with the outer circumferential surface of the rotary drive shaft, without deteriorating the dynamic balance of the rotating unit of the compressor.

The object indicated above may be achieved according to any one of the following forms or modes of the present invention, each of which is numbered like the appended claims and depend from the other form or forms, where appropriate, to indicate and clarify possible combinations of technical features of the present invention, for easier understanding of the invention. It is to be understood that the present invention is not limited to the technical features and their combinations described below. It is also to be understood that any technical feature described below in combination with other technical features may be a subject matter of the present invention, independently of those other technical features.

(1) A swash plate type compressor of variable capacity type comprising: a housing having a plurality of cylinder bores formed therein such that the cylinder bores are arranged along a circle whose center lies on a centerline of the housing; a rotary drive shaft which is rotatably supported by the housing such that an axis of rotation of the rotary drive shaft is aligned with the centerline of the housing; a swash plate which is carried by the rotary drive shaft such that an angle of inclination of the swash plate with respect to a plane perpendicular to the axis of rotation of the rotary drive shaft is variable, and such that the swash plate is rotated together with the rotary drive shaft; a plurality of pistons which are slidably fitted in the respective cylinder bores and which engage a radially outer portion of the swash plate, each of the pistons being reciprocated between a compression stroke end and a suction stroke end by rotation of the swash plate, the radially outer portion of the swash plate including a compression-end circumferential part which engages each piston when each piston is located at the compression stroke end; a swash plate angle adjusting device for adjusting the angle of inclination of the swash plate between a minimum inclination angle and a maximum inclination angle, and wherein the swash plate has a first center point at the maximum inclination angle and a second center point at the minimum inclination angle, each of the first and second center points being an intersection between an intermediate plane of the swash plate which is intermediate in a direction of thickness thereof and a centerline of the swash plate, (a) the first center point and the second center point being located on the axis of rotation of the rotary drive shaft, or (b) the first center point being located on the axis of rotation or offset from the axis of rotation on one side of the axis of rotation, which one side corresponds to the compression-end circumferential part of the swash plate, while the second center point is offset a larger distance from the axis of rotation than the first center point.

In the conventional swash plate type compressor of variable capacity type, the first center point of the swash plate at its maximum inclination angle is located substantially on the rotation axis of the rotary drive shaft. As the inclination angle of the swash plate gradually decreases, the center point of the swash plate is initially moved to one side of the rotation axis corresponding to the compression-end circumferential part, and then moved to the other side of the rotation axis corresponding to the suction-end circumferential part. Thus, the second center point of the swash plate at its minimum inclination angle is located on the other side of the rotation axis corresponding to the suction-end circumferential part. In the conventional compressor, the center point of the swash plate is moved so as not to offset a large distance from the rotation axis. The center of gravity of the swash plate is located on one of opposite sides of its intermediate plane, which one side is remote from the cylinder bore of the housing. Accordingly, in the conventional compressor, the second center of gravity of the swash plate at its minimum inclination angle is offset from the first center of gravity at the maximum inclination angle on the side of the suction-end circumferential part of the swash plate.

As described above, for assuring the optimum operating condition of the compressor, it is desirable to locate the center of gravity of the swash plate on one side of the rotation axis corresponding to the compression-end circumferential part, so as to cause the centrifugal force acting on the swash plate in the direction from the suction-end circumferential part toward the compression-end circumferential part while minimizing the magnitude of the centrifugal force. Further, it is desirable that the centrifugal force acting on the swash plate at the minimum inclination angle is larger than that acting on the swash plate at the maximum inclination angle. The swash plate at the maximum inclination angle receives at one of its opposite inclined surfaces the reaction force of the piston when the piston is at the compression stroke, so that the swash plate receives the force acting thereon in the direction from the suction-end circumferential part toward the compression-end circumferential part owing to the effect of the inclined surface. In contrast, the above-indicated force is substantially zero or considerably small while the swash plate is at the minimum inclination angle.

In the conventional swash plate type compressor, however, the second center of gravity of the swash plate at the minimum inclination angle is offset from the first center of gravity at the maximum inclination angle on the side of the suction-end circumferential part of the swash plate. This positional relationship between the first and second centers of gravity of the swash plate at the maximum and minimum inclination angles is contrary to the desired one. In the compressor constructed according to the present invention wherein the first and second center points of the swash plate at the maximum and minimum inclination angles are located on the rotation axis, or the first center point at the maximum inclination angle is located on the rotation axis or offset from the rotation axis on one side of the rotation axis corresponding to the compression-end circumferential part of the swash plate, while the second center point at the minimum inclination angle is offset a larger distance from the rotation axis than the first center point at the maximum inclination angle, the positional relationship between the first and second centers of gravity at the maximum and minimum inclination angles is more desirable than that of the conventional compressor described above. Accordingly, it is easier in the present arrangement than in the conventional arrangement to lower the maximum value of the centrifugal force while permitting the swash plate to receive the centrifugal force acting thereon in the direction from the suction-end circumferential part toward the compression-end circumferential part at both of the maximum and minimum inclination angles. In case where the second center of gravity at the minimum inclination angle is located on the other side of the rotation axis corresponding to the suction-end circumferential surface of the swash plate, the swash plate is subjected to a centrifugal force acting thereon in the reverse direction from the compression-end circumferential part toward the suction-end circumferential part. Even in this case, since the distance between the second center of gravity which is located on the other side of the rotation axis corresponding to the suction-end circumferential part of the swash plate and the rotation axis is smaller in the present arrangement than that in the conventional arrangement, the magnitude of the centrifugal force acting on the swash plate at the minimum inclination angle in the above-indicated reverse direction is accordingly small. Accordingly, even in this arrangement, it is easier than in the conventional arrangement to permit the suction-end-side inner circumferential surface of the through-hole of the swash plate to be kept in pressing contact with the outer circumferential surface of the rotation axis. Where the inclination angle of the swash plate at the minimum inclination is a positive value rather than zero, for instance, the swash plate receives the force acting thereon in the direction from the suction-end circumferential part toward the compression-end circumferential part, based on the reaction force of the piston at its compression stroke. If this force acting on the swash plate in the direction from the suction end side toward the compression end side is made larger than the centrifugal force acting on the swash plate in the reverse direction from the compression end side toward the suction end side; it is possible that the suction-end-side inner circumferential surface of the through-hole of the swash plate is kept in pressing contact with the outer circumferential surface of the rotary drive shaft while the swash plate is at the minimum inclination angle. Even where the inclination angle of the swash plate at the minimum inclination is zero, the suction-end-side inner circumferential surface of the through-hole of the swash plate can be kept in a pressing contact with the outer circumferential surface of the rotary drive shaft, by providing suitable biasing means such as a spring between the rotary drive shaft and the swash plate, for biasing the swash plate in the direction from the suction-end circumferential part toward the compression-end circumferential part. Thus, if the inclination angle of the swash plate at the minimum inclination is a positive value (larger than zero) or the biasing means is provided for biasing the swash plate as described above, the suction-end-side inner circumferential surface of the through-hole of the swash plate can be kept in pressing contact with the outer circumferential surface of the rotary drive shaft without employing the arrangement of the present invention. It is noted, however, that the inclination angle of the swash plate at the minimum inclination and the biasing force for biasing the swash plate in the direction from the suction-end side toward the compression-end side can be made smaller in the present arrangement.

(2) A swash plate type compressor of variable capacity type comprising: a housing having a plurality of cylinder bores formed therein such that the cylinder bores are arranged along a circle whose center lies on a centerline of the housing; a rotary drive shaft which is rotatably supported by the housing such that an axis of rotation of the rotary drive shaft is aligned with the centerline of the housing; a swash plate which is carried by the rotary drive shaft such that an angle of inclination of the swash plate with respect to a plane perpendicular to the axis of rotation of the rotary drive shaft is variable, and such that the swash plate is rotated together with the rotary drive shaft; a plurality of pistons which are slidably fitted in the respective cylinder bores and which engage a radially outer portion of the swash plate, each of the pistons being reciprocated between a compression stroke end and a suction stroke end by rotation of the swash plate, the radially outer portion of the swash plate including a compression-end circumferential part which engages each piston when each piston is located at the compression stroke end; a swash plate angle adjusting device for adjusting the angle of inclination of the swash plate between a minimum inclination angle and a maximum inclination angle, and wherein the swash plate has a first center of gravity at the maximum inclination angle and a second center of gravity at the minimum inclination angle, the first center of gravity and the second center of gravity being located on the axis of rotation of the rotary shaft or offset a substantially equal distance from the axis of rotation on one side of the axis of rotation, which one side corresponds to the compression-end circumferential part of the swash plate.

In the above mode (2) of the invention, the second center of gravity of the swash plate at the minimum inclination angle and the first center of gravity at the maximum inclination angle are offset a substantially equal distance from the axis of rotation of the rotary drive shaft. Namely, the distance between the second center of gravity at the minimum inclination angle and the rotation axis may be just equal to, slightly larger or smaller than, the distance between the first center of gravity at the maximum inclination angle and the rotation axis. The present arrangement permits the swash plate at both of the minimum inclination angle and maximum inclination angle to receive the centrifugal force acting thereon in the direction from the suction-end circumferential part toward the compression-end circumferential part while minimizing the maximum value of the centrifugal force to a required level.

(3) A swash plate type compressor of variable capacity type comprising: a housing having a plurality of cylinder bores formed therein such that the cylinder bores are arranged along a circle whose center lies on a centerline of the housing; a rotary drive shaft which is rotatably supported by the housing such that an axis of rotation of the rotary drive shaft is aligned with the centerline of the housing; a swash plate which is carried by the rotary drive shaft such that an angle of inclination of the swash plate with respect to a plane perpendicular to the axis of rotation of the rotary drive shaft is variable, and such that the swash plate is rotated together with the rotary drive shaft; a plurality of pistons which are slidably fitted in the respective cylinder bores and which engage a radially outer portion of the swash plate, each of the pistons being reciprocated between a compression stroke end and a suction stroke end by rotation of the swash plate, the radially outer portion of the swash plate including a compression-end circumferential part which engages each piston when each piston is located at the compression stroke end; a swash plate angle adjusting device for adjusting the angle of inclination of the swash plate between a minimum inclination angle and a maximum inclination angle, and wherein the swash plate has a first center of gravity at the maximum inclination angle and a second center of gravity at the minimum inclination angle, the second center of gravity being offset from the first center of gravity on the side of the compression-end circumferential part of the swash plate.

In the arrangement according to the above mode (3), the maximum value of the centrifugal force acting on the swash plate can be easily made smaller than that in the conventional arrangement while biasing the swash plate in the direction from the suction-end circumferential part toward the compression-end circumferential part at both of the minimum inclination angle and maximum inclination angle of the swash plate.

(4) A swash plate type compressor according to the above mode (3), wherein the second center of gravity is located on the axis of rotation of the rotary drive shaft or offset from the axis of rotation on one side of the axis of rotation, which one side corresponds to the compression-end circumferential part of the swash plate.

In one example according to the above mode (4), the second center of gravity of the swash plate at the minimum inclination angle is located on one side of the rotation axis of the rotary drive shaft corresponding to the compression-end circumferential part of the swash plate, while the first center of gravity at the maximum inclination angle is located on the other side of the rotation axis corresponding to the suction-end circumferential part of the swash plate.

In this arrangement, the centrifugal force acts on the swash plate in the direction from the suction-end circumferential part toward the compression-end circumferential part when the swash plate is at the minimum inclination angle where the force acting on the swash plate in the same direction owing to the effect of the inclined surface is not expected or insufficient. This arrangement is effective to stabilize the behavior of the swash plate.

In another example according to the above mode (4), the first center of gravity of the swash plate at the maximum inclination angle and the second center of gravity at the minimum inclination angle are both located on one side of the rotation axis corresponding to the compression-end circumferential part of the swash plate, and the second center of gravity is offset a larger distance from the rotation axis than the first center of gravity.

In this arrangement, the centrifugal force acts on the swash plate in the direction from the suction-end circumferential part toward the compression-end circumferential part both when the swash plate is at the minimum inclination angle and when the swash plate is at the maximum inclination angle. Further, the centrifugal force acting on the swash plate at the minimum inclination angle is larger than that at the maximum inclination angle. Accordingly, the swash plate type compressor of variable capacity type according to the present arrangement can be operated in a condition which is optimum or almost optimum from the viewpoint of the behavior of the swash plate. It is particularly desirable that the second center of gravity of the swash plate at the minimum inclination angle is offset a larger distance from the rotation axis than any other centers of gravity of the swash plate at any other inclination angles.

(5) A swash plate type compressor according to any one of the above modes (1)-(4), further comprising: a first engaging portion which is offset from the axis of rotation of the rotary drive shaft and which is rotatable together with the rotary drive shaft; and a second engaging portion which is fixed to the swash plate and which engages the first engaging portion such that the swash plate is tiltable relative to the axis of rotation of the rotary drive shaft so as to change the angle of inclination thereof, and such that the swash plate is inhibited from rotating relative to the rotary drive shaft.

The rotation of the rotary drive shaft can be effectively transmitted to the swash plate owing to the engagement of the first and second engaging portions described above.

(6) A swash plate type compressor according to the above mode (5), wherein the first engaging portion is provided on a rotary member which is fixed to the rotary drive shaft.

The first engaging portion may be provided on the rotary drive shaft. The present arrangement wherein the first engaging portion is provided on the rotary member fixed to the rotary drive shaft facilitates the installation of the first engaging portion.

(7) A swash plate type compressor according to the above mode (6), wherein the radially outer portion of the swash plate further includes a suction-end circumferential part which engages each piston when each piston is located at the suction stroke end, the suction-end circumferential part being opposite to the compression-end circumferential part diametrically of the rotary drive shaft, and wherein the rotary member has a center of gravity which is located on the axis of rotation of the rotary drive shaft or offset from the axis of rotation on the other side of the axis of rotation corresponding to the suction-end circumferential part of the swash plate.

For stable behavior of the swash plate, it is effective to locate the center of gravity of the swash plate on one side of the rotation axis of the rotary drive shaft corresponding to the compression-end circumferential part. In this case, however, the dynamic balance of the swash plate itself deteriorates to some extent. In view of this, if the center of gravity of the rotary member is located on the other side of the rotation axis corresponding to the suction-end circumferential part of the swash plate, the centrifugal force acting on the swash plate is offset or reduced by the centrifugal force acting on the rotary member. In particular, in the swash plate type compressor of variable capacity type constructed according to the above mode (2) of the invention wherein the first center of gravity and the second center of gravity are both located on one side of the rotation axis corresponding to the compression-end circumferential part of the swash plate, and the first and second centers of gravity are offset from the rotation axis by a substantially equal distance, the centrifugal force acting on the swash plate is substantially constant irrespective of the inclination angle of the swash plate. Accordingly, if the compressor is designed such that the center of gravity of the rotary member is located on the other side of the rotation axis corresponding to the suction-end circumferential part of the swash plate, and such that the magnitude of the centrifugal force acting on the rotary member is substantially equal to that acting on the swash plate, the dynamic balance of the rotating unit of the compressor including the rotary drive shaft, swash plate and rotary member can be maintained in an optimum condition irrespective of the inclination angle of the swash plate. As a result, the swash plate type compressor of variable capacity type does not suffer from undesirable vibration which would be otherwise caused by deteriorated dynamic balance of its rotation unit, regardless of its discharge capacity.

(8) A swash plate type compressor according to any one of the above modes (5)-(7), wherein the first engaging portion comprises an engaging hole having a circular shape in transverse cross section, and the second engaging portion is a protruding member which protrudes from a body portion of the swash plate such that the protruding member is inclined with respect to the intermediate plane of the swash plate, the protruding member having at a distal end thereof a spherical portion which is slidably fitted into the engaging hole of the first engaging portion.

(9) A swash plate type compressor according to any one of the above modes (1)-(8), further comprising a stopper for limiting a movement of the swash plate relative to the rotary drive shaft in a direction from the suction-end circumferential part of the swash plate toward the compression-end circumferential part of the swash plate, the stopper being formed at a portion of an inner circumferential surface of a through-hole formed through a central part of the swash plate, which portion is located on the side of the suction-end circumferential part of the swash plate, the stopper limiting the movement of the swash plate by a contact thereof with a corresponding portion of an outer circumferential surface of the rotary drive shaft.

(10) A swash plate type compressor according to the above mode (9), wherein the stopper has a curved shape in cross section in a plane which passes the compression-end circumferential part of the swash plate and the suction-end circumferential part of the swash plate and which includes the rotation axis of the rotary drive shaft.

In the swash plate type compressor of variable capacity type constructed according to any one of the above modes (1)-(4), the curved cross sectional shape and the position of the stopper are determined to satisfy the condition described in any one of the above modes (1)-(4). The curved cross sectional shape comprises an arcuate shape as defined in the following mode (11). Where the curved cross sectional shape is other than the arcuate shape, it is possible to change the position of the swash plate in a direction perpendicular to the rotary drive shaft while the stopper formed on the swash plate is held in contact with the rotary drive shaft, by appropriately changing the curved cross sectional shape of the stopper.

(11) A swash plate type compressor according to the above mode (10), wherein the curved cross sectional shape of the stopper is arcuate.

In the swash plate type compressor of variable capacity type constructed according to any one of the above modes (1)-(4), the position of the center of the arcuate shape of the stopper relative to the center point or the center of gravity of the swash plate is determined to satisfy the condition described in any one of the above modes (1)-(4).

BRIEF DESCRIPTION OF THE DRAWINGS

The above and optional objects, features, advantages and technical and industrial significance of the present invention will be better understood and appreciated by reading the following detailed description of the presently preferred embodiments of the invention, when considered in connection with the accompanying drawings, in which:

FIG. 1

is a front elevational view in cross section of a swash plate type compressor of variable capacity type constructed according to one embodiment of the present invention, wherein the swash plate is at its minimum inclination angle;

FIG. 2

is a front elevational view in cross section of the compressor of

FIG. 1

, wherein the swash plate is at its maximum inclination angle;

FIG. 3

is a schematic view showing a relative positional relationship of the center point of the swash plate at the maximum inclination angle, rotation axis of the rotary drive shaft, and center of the arc of stopper;

FIG. 4

is a schematic view showing a relative positional relationship of the center point of the swash plate at the minimum inclination angle, rotation axis of the rotary drive shaft, and center of the arc of the stopper;

FIG. 5

is a schematic view showing a relative positional relationship of the center points and centers of gravity of the swash plate at the maximum and minimum inclination angles, and the center of the arc of the stopper;

FIG. 6

is a schematic view showing a relative positional relationship of the center points and centers of gravity of the swash plate at the maximum and minimum inclination angles, and the center of the arc of the stopper in a conventional swash plate type compressor; and

FIG. 7

is a schematic view showing a relative positional relationship of the center points and centers of gravity of the swash plate at the maximum and minimum inclination angles, and the center of the arc of the stopper in a swash plate type compressor constructed according to another embodiment of the invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Referring to the accompanying drawings, there will be described presently preferred embodiments of the present invention as applied to a swash plate type compressor of variable capacity type used for an air conditioning system of an automotive vehicle.

Referring first to

FIG. 1

, there is shown a swash plate type compressor of variable capacity type. In

FIG. 1

, reference numeral

10

denotes a cylinder block having a plurality of cylinder bores

12

formed so as to extend in its axial direction such that the cylinder bores

12

are equiangularly arranged along a circle whose center lies on a centerline of the cylinder block

10

. A plurality of single-headed pistons

14

(hereinafter referred to simply as “pistons

14

”) are reciprocably received in the respective cylinder bores

12

. To one of the axially opposite end faces of the cylinder block

10

, (the left end face as seen in

FIG. 1

, which will be referred to as “front end face”), there is attached a front housing

16

. To the other end face (the right end face as seen in

FIG. 1

, which will be referred to as “rear end face”), there is attached a rear housing

18

through a valve plate

20

. The front housing

16

, rear housing

18

and cylinder block

10

cooperate to constitute a housing assembly of the swash plate type compressor. The rear housing

18

and the valve plate

20

cooperate to define a suction chamber

22

and a discharge chamber

24

, which are connected to a refrigerating circuit (not shown) through an inlet

26

and an outlet

28

, respectively. The valve plate

20

has suction ports

32

, suction valves

34

, discharge ports

36

and discharge valves

38

.

A rotary drive shaft

50

is disposed in the cylinder block

10

and the front housing

16

such that the axis of rotation M of the rotary drive shaft

50

is aligned with the centerline of the cylinder block

10

. The rotary drive shaft

50

is supported at its opposite end portions by the front housing

16

and the cylinder block

10

, respectively, via respective bearings. The cylinder block

10

has a central bearing hole

56

formed in a central portion thereof, and the bearing is disposed in this central bearing hole

56

, for supporting the drive shaft

50

at its rear end portion. The front end portion of the drive shaft

50

is connected, through a clutch mechanism such as an electromagnetic clutch, to an external drive source (not shown) in the form of an engine of an automotive vehicle. In operation of the compressor, the drive shaft

50

is connected through the clutch mechanism to the vehicle engine in operation so that the drive shaft

50

is rotated about its axis M.

The rotary drive shaft

50

carries a swash plate

60

such that the swash plate

60

is axially movable and tiltable relative to the drive shaft

50

. The swash plate

60

has a body portion

62

. A central through-hole

64

is formed through a central portion of the swash plate

60

such that the through-hole

64

includes a centerline N of the body portion

62

of the swash plate

60

. The rotary drive shaft

50

extends through the through-hole

64

for supporting the swash plate

60

. To the rotary drive shaft

50

, there is fixed a rotary member

66

as a torque transmitting member, which is held in engagement with the front housing

16

through a thrust bearing

68

. The swash plate

60

is rotated with the rotary drive shaft

50

by a hinge mechanism

74

during rotation of the rotary drive shaft

50

. The hinge mechanism

74

guides the swash plate

60

for its axial and tilting motions. The hinge mechanism

74

includes: a pair of support arms

76

fixed to the rotary member

66

at respective two circumferential portions thereof which are offset from the rotation axis M of the rotary drive shaft

50

and which are opposite to each other in the diametric direction of the rotary member

66

; engaging protrusions

80

which are formed on the body portion

62

of the swash plate

60

and which slidably engage engaging holes

78

formed in the support arms

76

, the through-hole

64

of the swash plate

60

, and an outer circumferential surface

82

of the rotary drive shaft

50

. Each of the engaging protrusions

80

protrudes from one of the opposite major surfaces of the body portion

62

of the swash plate

60

on the side of the rotary member

66

, so as to extend in a direction which is inclined with respect to the centerline N of the swash plate

60

(i.e., in a radially outward direction of the compressor). Each engaging protrusion

80

has, at its distal end, a spherical portion

84

which is slidably fitted into the corresponding engaging hole

78

having a circular shape in transverse cross section. In the present embodiment, the swash plate

60

, rotary drive shaft

50

, and hinge mechanism

74

constitute a major portion of a reciprocating drive device for reciprocating the pistons

14

. The engaging hole

78

formed in each support arm

76

functions as a first engaging portion, while each engaging protrusion

80

functions as a second engaging portion.

The piston

14

indicated above includes an engaging portion

90

engaging the swash plate

60

, and a hollow cylindrical head portion

92

formed integrally with the engaging portion

90

and fitted in the corresponding cylinder bore

12

. The engaging portion

90

has a generally U-shape in cross section, and includes a base section

98

which defines the bottom of the U-shape, and a pair of substantially parallel arm sections

94

,

96

which extend from the base section

98

in a direction perpendicular to the axis of the piston

14

. The two opposed lateral walls of the arm sections

94

,

96

have respective recesses

100

which are opposed to each other. Each of the recesses

100

is defined by a part-spherical inner surface of the lateral wall. The two part-spherical inner surfaces are of a single spherical surface. The engaging portion

90

engages the swash plate

60

through a pair of hemi-spherical shoes

104

. The hemi-spherical shoes

104

are slidably received at their hemispherical surfaces in the respective recesses

100

and engage the radially outer portions of the opposite surfaces of the swash plate

60

at their flat surfaces. The head portion

92

of the piston

14

includes a cylindrical body portion

106

having an open end and a closed end, and a cap

108

as a closure member which is fixed to the cylindrical body portion

106

for closing its open end. The cylindrical body portion

106

is formed integrally at its bottom with the engaging portion

90

on the side of its arm section

96

.

The cylinder block

10

and the piston

14

are formed of a metallic material in the form of an aluminum alloy. The piston

14

is coated at its outer circumferential surface with a coating film of a fluoro resin. The fluoro resin coating prevents a direct contact of the aluminum alloy of the piston

14

with the aluminum alloy of the cylinder block

10

so as to prevent seizure therebetween, and makes it possible to minimize the amount of clearance between the piston

14

and the cylinder bore

12

. It is noted that the cylinder block

10

and the piston

14

may be formed of an aluminum silicon alloy. Other materials may be used for the cylinder block

10

, the piston

14

, and the coating film.

A rotary motion of the swash plate

60

is converted into a reciprocating linear motion of the piston

14

through the shoes

104

. A refrigerant gas in the suction chamber

22

is sucked into the pressurizing chamber

79

through the suction port

32

and the suction valve

34

when the piston

14

is moved from its upper dead point to its lower dead point, that is, when the piston

14

is in the suction stroke. The refrigerant gas in the pressurizing chamber

79

is pressurized by the piston

14

when the piston

14

is moved from its lower dead point to its upper dead point, that is, when the piston

14

is in the compression stroke. The pressurized refrigerant gas is discharged into the discharge chamber

24

through the discharge port

36

and the discharge valve

38

. The swash plate

60

includes a compression-end circumferential part

110

which engages each of the plurality of pistons

14

when each piston is located at its compression stroke end, and a suction-end circumferential part

112

which engages each piston,

14

when each piston

14

is located at its suction stroke end. The compression-end circumferential part

110

and the suction-end circumferential part

112

are opposite to each other diametrically of :the rotary drive shaft

50

. The compression-end and suction-end circumferential parts

110

,

112

move in the rotating direction of the drive shaft

50

during a rotary movement of a rotary unit including the drive shaft

50

, swash plate

60

, and rotary member

66

. In

FIGS. 1 and 2

, the compression-end circumferential part

110

of the swash plate

60

is located at the highest position as seen in the vertical direction of

FIGS. 1 and 2

, while the suction-end circumferential part

112

is located at the lowest position. A reaction force acts on the piston

14

in the axial direction as a result of compression of the refrigerant gas in the pressurizing chamber

79

. This compression reaction force is received by the housing assembly constituted by the cylinder block

10

and the front and rear housings

16

,

18

through the piston

14

, swash plate

60

, rotary member

66

and thrust bearing

68

. The engaging portion

90

of the piston

14

has an integrally formed rotation preventive part (not shown), which is arranged to contact the inner circumferential surface of the front housing

16

, for thereby preventing a rotary motion of the piston

14

about its centerline to prevent an interference between the piston

14

and the swash plate

60

.

The cylinder block

10

has a supply passage

120

formed therethrough for communication between the discharge chamber

24

and a crank chamber

122

which is defined between the front housing

16

and the cylinder block

10

. The supply passage

120

is connected to a solenoid-operated control valve

124

provided to control the pressure in the crank chamber

122

. The solenoid-operated control valve

124

has a solenoid coil

126

which is selectively energized and de-energized by a control device (not shown) constituted principally by a computer. During energization of the solenoid coil

126

, the amount of electric current applied to the solenoid coil

126

is controlled depending upon the air conditioner load, so that the amount of opening of the control valve

124

is controlled according to the air conditioner load.

The rotary drive shaft

50

has a bleeding passage

130

formed therethrough. The bleeding passage

130

is open at one of its opposite ends to the central bearing hole

56

, and is open to the crank chamber

122

at the other end. The central bearing hole

56

communicates at its bottom with the suction chamber

22

through a communication port

134

.

The present swash plate type compressor is a variable capacity type. By controlling the pressure in the crank chamber

122

by utilizing a difference between the pressure in the discharge chamber

24

as a high-pressure source and the pressure in the suction chamber

22

as a low pressure source, a difference between the pressure in the crank chamber

122

which acts on the front side of the piston

14

and the pressure in the pressurizing chamber

79

is regulated to change the angle of inclination of the swash plate

60

with respect to a plane perpendicular to the axis M of rotation of the drive shaft

50

, for thereby changing the reciprocating stroke (suction and compression strokes) of the piston

14

, whereby the discharge capacity of the compressor can be adjusted. Described in detail, the pressure in the crank chamber

122

is controlled by controlling the solenoid-operated control valve

124

to selectively connect and disconnect the crank chamber

122

to and from the discharge chamber

24

.

Described more specifically, while the solenoid coil

126

is in the de-energized state, the solenoid-operated control valve

124

is held in its fully open state, and the supply passage

120

is opened for permitting the pressurized refrigerant gas to be delivered from the discharge chamber

24

into the crank chamber

122

, resulting in an increase in the pressure in the crank chamber

122

, and the angle of inclination of the swash plate

60

is minimized. Namely, the swash plate

60

is placed in a substantially perpendicular posture relative to the axis M of rotation of the rotary drive shaft, as shown in FIG.

1

. The reciprocating stroke of the piston

14

which is reciprocated by rotation of the swash plate

60

decreases with a decrease of the angle of inclination of the swash plate

60

, so as to reduce an amount of change of the volume of the pressurizing chamber

79

, whereby the discharge capacity of the compressor is minimized. While the solenoid coil

126

is in the energized state, the amount of the pressurized refrigerant gas in the discharge chamber

24

to be delivered into the crank chamber

122

is reduced, by increasing an amount of electric current applied to the solenoid coil

126

to reduce (or zero) the amount of opening of the solenoid-operated control valve

124

. In this condition, the refrigerant gas in the crank chamber

122

flows into the suction chamber

22

through the bleeding passage

130

and the communication port

134

, so that the pressure in the crank chamber

122

is lowered, to thereby increase the angle of inclination of the swash plate

60

. Accordingly, the amount of change of the volume of the pressurizing chamber

79

is increased, whereby the discharge capacity of the compressor is increased. When the supply passage

120

is closed upon energization of the solenoid coil

126

, the pressurized refrigerant gas in the discharge chamber

24

is not delivered into the crank chamber

122

, whereby the angle of inclination of the swash plate

60

is maximized to maximize the discharge capacity of the compressor.

The minimum angle of inclination of the swash plate

60

is limited by abutting contact of the swash plate

60

with a stop

136

in the form of a ring fixedly fitted on the drive shaft

50

, while the maximum angle of inclination of the swash plate

60

is limited by abutting contact of a part-cylindrical stop

138

formed on the swash plate

60

, with the rotary member

66

. In the present embodiment, the supply passage

120

, the crank chamber

122

, the solenoid-operated control valve

124

, the bleeding passage

130

, the communication port

134

, and the control device for controlling the solenoid-operated control valve

124

cooperate to constitute a major portion of an angle adjusting device for controlling the angle of inclination of the swash plate

60

.

Between the rotary member

66

and one of the opposite major surfaces of the swash plate

60

which is remote from the rear housing

18

, an elastic member in the form of a compression coil spring

140

is disposed to function as biasing means. This compression coil spring

140

is received at one of its opposite ends by the rotary member

66

, and at the other end by the body portion

62

of the swash plate

60

on the side of the engaging protrusion

80

, namely, on the side which is nearer to the rotary member

66

, so that the compression coil spring

140

biases the swash plate

60

at its minimum inclination angle.

At one of axially opposite ends of the through-hole

64

of the swash plate

60

, which end is nearer to the rotary member

66

, a circumferential groove

150

is formed. While the swash plate

60

is at its maximum inclination position, the compression coil spring

140

is received at one end thereof which is remote from the rotary member

66

by a bearing surface

154

which partially defines the circumferential groove

150

and which is perpendicular to the centerline of the housing assembly of the compressor when the inclination angle of the swash plate

60

is maximum. While the swash plate

60

is at its minimum inclination position, the compression coil spring

140

is received at the above-indicated one end thereof by a bearing surface

152

which partially defines the circumferential groove

150

and which is perpendicular to the centerline of the housing assembly when the inclination angle of the swash plate

60

is minimum. When the compressor is turned off, the swash plate is moved to the minimum inclination position by a biasing force of the compression coil spring

140

and is kept at the position until the compressor is re-started.

A stopper

160

having a curved surface is formed at a portion of the inner circumferential surface of the through-hole

64

of the swash plate

60

, which portion is located on the side of the suction-end circumferential part

112

of the swash plate

60

. The stopper

160

limits a movement of the swash plate

60

in a direction from its suction-end circumferential part

112

toward its compression-end circumferential part

110

. The stopper

160

has an arcuate shape in cross section in a plane which passes the compression-end and suction-end circumferential parts

110

,

112

of the swash plate

60

and which includes the rotation axis M of the rotary drive shaft

50

. In the present embodiment, the stopper

160

is formed adjacent to the bearing surface

154

described above and has a part-circular cross sectional shape. As shown in

FIG. 3

, the stopper

160

is formed such that the center a of the arc of its part-circular shape is located on one of opposite sides of an intermediate plane

1

, which side is nearer to the engaging protrusion

80

. The intermediate plane

1

is intermediate in a direction of thickness of the body portion

62

of the swash plate

60

, i.e., in a direction parallel to the centerline N of the swash plate

60

. The configuration of the through-hole

64

of the swash plate

60

is designed so as to permit the tilting motion of the swash plate

60

while limiting the movement of the swash plate

60

relative to the rotary drive shaft

50

in the direction toward its compression-end circumferential part

110

, by contact of the stopper

160

with the outer circumferential surface

82

of the rotary drive shaft

50

.

The positional relationship of the center a of the arc of the stopper

160

relative to the center point b of the body portion

62

of the swash plate

60

, i.e., the intersection between the centerline N of the swash plate

60

and the intermediate plane

1

, is determined based on the following formulas. Initially, the following formula is established when the swash plate

60

is at its maximum inclination position, as schematically shown in FIG.

3

:

D/

2

+R=H

cos θ

100

−A

sin θ

100

−B

100

wherein,

D/2: a radius of the rotary drive shaft

50

,

R: a radius of the arc of the stopper

160

,

H: a distance between the center a of the arc of the stopper

160

and the centerline N of the swash plate

60

,

θ

100

: the inclination angle of the swash plate

60

at its maximum inclination position where the discharge capacity of the compressor is maximum (100%),

A: a distance between the center a of the arc of the stopper

160

and the intermediate plane

1

of the swash plate

60

, and

B: a distance between the center point b of the swash plate

60

and the rotation axis M of the rotary drive shaft

50

.

By transposing the term “B

100

” in the right-hand side of the above formula to the left-hand side of the formula and transposing the term “D/2+R” in the left-hand side to the right-hand side, the following formula (1) is established:

B

100

=H

cos θ

100

−A

sin θ

100

−D/

2

−R

(1)

The positional relationship of the center a of the arc of the stopper

160

relative to the center point b of the swash plate

60

when the swash plate

60

is at its minimum inclination position is schematically shown in FIG.

4

. This positional relationship shown in

FIG. 4

is determined to satisfy the following formula (2):

B

min

=H

cos θ

min

−A

sin θ

min

−D/

2

−R

(2)

wherein, θ

min

represents the minimum inclination angle of the swash plate

60

. The above-described values A, H, and R are determined such that the values B

100

and B

min

satisfy the following formula (3):

B

min

−B

100

>0 (3)

Since the values A, H, and R are determined to satisfy the above formula (3), the center point b

min

of the swash plate

60

at the minimum inclination angle is offset from the rotation axis M a larger distance corresponding to ΔH (=B

min

−B

110

) than the center point b

100

of the swash plate

60

at the maximum inclination angle. In other words, the center point b

100

of the swash plate

60

at the maximum inclination angle and the center point b

min

of the swash plate

60

at the minimum inclination angle are both located on the rotation axis M, or the center point b

100

at the maximum inclination angle is located on the rotation axis M or offset from the rotation axis M on one side of the rotation axis corresponding to the compression-end circumferential part

110

of the swash plate

60

, while the center point b

min

at the minimum inclination angle is offset a larger distance from the rotation axis M than the center point b

100

at the maximum inclination angle. In the present embodiment, the center point b

100

of the swash plate

60

at the maximum inclination angle is located on the rotation axis M, while the center point b

min

at the minimum inclination angle is located on one side of the rotation axis M corresponding to the compression-end circumferential part

110

.

FIG. 5

schematically shows a relative positional relationship of the center points b

min

and b

100

of the swash plate

60

at the minimum inclination angle and the maximum inclination angle, respectively, a center of gravity d

min

of the swash plate

60

at the minimum inclination angle and a center of gravity d

100

at the maximum inclination angle, the center a of the arc of the stopper

160

, and the rotation axis M of the rotary drive shaft. In actual operation of the compressor, the position of the stopper

160

is moved in opposite two axial directions of the rotary drive shaft

50

when the inclination angle of the swash plate

60

is changed. For easier understanding, the position of the stopper

160

is fixed in FIG.

5

.

FIG. 5

shows a difference between the distance of the center point b

min

from the rotation axis M and the distance of the center point b

100

from the rotation axis M, and a difference between the distance of the center of gravity b

min

from the rotation axis M and the distance of the center of gravity b

100

from the rotation axis M. As described above, the center point b

100

of the swash plate

60

at the maximum inclination angle and the center point b

min

at the minimum inclination angle are both located on the rotation axis M, or the center point b

100

is located on the rotation axis M or offset from the rotation axis M on one side of the axis M corresponding to the compression-end circumferential part of the swash plate

60

, while the center point b

min

is offset a larger distance from the rotation axis M than the center point b

100

. In the present embodiment shown in

FIG. 5

, the center of gravity of the swash plate

60

is offset a larger distance from the rotation axis M than the center point thereof, and located on one of opposite sides of the intermediate plane

1

, which side is nearer to the engaging protrusion

80

. Described in detail, the center of gravity d

min

of the swash plate

60

at the minimum inclination angle and the center of gravity d

100

at the maximum inclination angle are both located on one side of the rotation axis M corresponding to the compression-end circumferential part

110

of the swash plate

60

, and the centers of gravity d

min

and d

100

are offset an equal distance from the rotation axis M.

In contrast, in the conventional swash plate type compressor of variable capacity type, the center point of the swash plate

60

is changed as shown in

FIG. 6

, with a decrease of the inclination angle of the swash plate

60

. Described in detail, the center point b

100

of the swash plate

60

at the maximum inclination angle, which is located on the rotation axis M, is moved by a slight distance to one side of the rotation axis M corresponding to the compression-end circumferential part

110

of the swash plate

60

with a decrease of the inclination angle of the swash plate

60

, and then moved to the other side of the rotation axis M corresponding to the suction-end circumferential part

112

with a further decrease of the inclination angle of the swash plate

60

. As a result, the center point b

min

at the minimum inclination angle is located on the other side of the rotation axis M corresponding to the suction-end circumferential part

112

. The center of gravity of the swash plate

60

of the conventional compressor is located on one of opposite sides of its intermediate plane

1

, which side is nearer to the engaging protrusion

80

. Described in detail, the center of gravity d

100

is offset a larger distance from the rotation axis M on the side of the compression-end circumferential part

110

of the swash plate

60

than the center of gravity d

min

at the minimum inclination angle.

In the conventional compressor designed as described above, the swash plate

60

at the maximum inclination angle receives the centrifugal force acting thereon in a direction from the suction-end circumferential part

112

toward the compression-end circumferential part

110

, while the swash plate

60

at the minimum inclination angle receives the centrifugal force which acts thereon in the same direction but whose magnitude is smaller than that at the maximum inclination angle. Although the swash plate

60

at the maximum inclination angle receives the force acting thereon in the direction from the suction-end circumferential part

112

toward the compression-end circumferential part

110

owing to the effect of the inclined surface, the swash plate

60

at the maximum inclination angle also receives the centrifugal force in the same direction whose magnitude is larger than that at the minimum inclination angle. For assuring the stable behavior of the swash plate

60

, it is preferable that the stopper

160

formed on the suction-end side inner circumferential surface of the through-hole

64

of the swash plate

60

is kept in pressing contact with the outer circumferential surface

82

of the rotary drive shaft

50

during operation of the compressor. If the swash plate

60

at the maximum inclination angle, however, received the centrifugal force whose magnitude is larger than necessary, the dynamic balance of the rotating unit of the compressor including the swash plate

60

would undesirably deteriorate. In view of this, in the conventional compressor, the center of gravity of the rotary member

66

is located on the other side of the rotation axis M corresponding to the suction-end circumferential part

112

of the swash plate

60

by providing a counter weight (balancing weight) on the rotary member

66

, so as to offset the centrifugal force acting on the swash plate

60

by the centrifugal force acting on the rotary member

66

. Since the difference between the magnitude of the centrifugal force at the maximum inclination angle of the swash plate

60

and the magnitude of the centrifugal force at the minimum inclination angle is considerably large as described above, it is difficult to effectively reduce dynamic imbalance of the rotating unit of the compressor by the constant centrifugal force of the rotary member

66

, both when the swash plate

60

is at the maximum inclination angle and when the swash plate

60

is at the minimum inclination angle. In addition, the counter weight provided on the rotary member

66

undesirably increases the overall weight of the rotating unit of the compressor.

The swash plate type compressor constructed according to the present embodiment is free from the above-described problems as experienced in the conventional compressor. In the present swash plate type compressor wherein a distance B

min

between the center point b

min

of the swash plate

60

at the minimum inclination angle and the rotation axis M is made larger than a distance B

100

between the center point b

100

at the maximum inclination angle and the rotation axis M, the center of gravity d

min

of the swash plate

60

at the minimum inclination angle is not located on one side of the center of gravity d

100

at the maximum inclination angle corresponding to the suction-end circumferential part

112

of the swash plate

60

. Accordingly, the swash plate

60

at the minimum inclination angle receives the centrifugal force acting thereon in the direction from the suction-end circumferential part

112

toward the compression-end circumferential part

110

. Though the effect of the inclined surface described above is not substantially expected while the swash plate

60

is at the minimum inclination angle, the centrifugal force acting on the swash plate

60

in the direction described above permits the stopper

160

to be effectively kept in pressing contact with the outer circumferential surface

82

of the rotary drive shaft

50

. Therefore, the angle of inclination of the swash plate

60

can be changed with high stability while the radial movement of the swash plate

60

is limited.

In the present arrangement, the path of the center of gravity of the swash plate

60

between d

min

at the minimum inclination angle and d

100

at the maximum inclination angle is substantially parallel with the rotation axis M. Accordingly, the present arrangement permits the swash plate

60

to receive the centrifugal force acting thereon in the direction from the suction-end circumferential part

112

toward the compression-end circumferential part

110

with high stability while lowering the maximum value of the centrifugal force to a required level. In the present arrangement wherein the path of the center of gravity of the swash plate

60

between d

min

at the minimum inclination angle and d

100

at the maximum inclination angle is substantially parallel to the rotation axis M, the centrifugal force acting on the swash plate

60

is kept substantially constant irrespective of the inclination angle of the swash plate

60

. Accordingly, the dynamic imbalance of the rotating unit of the compressor can be substantially entirely eliminated by the constant centrifugal force acting on the rotary member

66

. In the present embodiment, since the maximum value of the centrifugal force acting on the swash plate

60

can be minimized to a required level, the dynamic imbalance of the rotating unit is relatively small even when the center of gravity of the rotary member

66

is located on the rotation axis M. Therefore, the present arrangement does not require any special means for locating the center of gravity of the rotary member

66

on the other side of the rotation axis M corresponding to the suction-end circumferential part

112

of the swash plate

60

. Even if it is required to locate the center of gravity of the rotary member

66

as described above, such locating means can be small in the present arrangement. For instance, where the counter weight is provided on the rotary member

66

for locating its center of gravity on the other side of the rotation axis M corresponding to the suction-end circumferential part

112

of the swash plate

60

, the mass of the counter weight can be made small in the present arrangement.

FIG. 7

shows a relative positional relationship of the center points b

min

, b

100

of the swash plate

60

at the minimum and maximum inclination angles, respectively, the centers of gravity d

min

, d

100

of the swash plate

60

at the maximum and minimum inclination angles, respectively, the rotation axis M of the rotary shaft

50

, and the center a of the arc of the stopper

160

in the compressor constructed according to another embodiment of the present invention. Described more specifically, the center point b

100

at the maximum inclination angle and the center point b

min

at the minimum inclination angle are both located on the rotation axis M, or the center point b

100

is located on the rotation axis M or offset from the rotation axis M on the side of the compression-end circumferential part

110

of the swash plate

60

while the center point b

min

is offset a larger distance from the rotation axis M than the center point b

100

. Further, the center of gravity d

100

at the minimum inclination angle and the center of gravity d

100

at the maximum inclination angle are both located on one side of the rotation axis M corresponding to the compression-end circumferential part

110

of the swash plate

60

, and the center of gravity d

min

is offset a larger distance from the rotation axis M than the center of gravity d

100

. According to this arrangement, the magnitude of the centrifugal force acting on the swash plate

60

at the minimum inclination angle can be made larger than that of the centrifugal force acting on the swash plate

60

at the maximum inclination angle, for thereby assuring optimum behavior of the swash plate

60

. In other words, the magnitude of the centrifugal force can be made small with an increase of the magnitude of the force acting on the swash plate

60

in the direction from the suction-end circumferential part

112

toward the compression-end circumferential part

110

owing to the effect of the inclined surface, which increase results from an increase of the inclination angle of the swash plate

60

. In the present arrangement, the magnitude of the centrifugal force acting on the swash plate

60

in the direction from the suction-end circumferential part

112

toward the compression-end circumferential part

110

is large at the minimum inclination of the swash plate

60

where the effect of the inclined surface is not expected, while the magnitude of the centrifugal force is small at the maximum inclination of the swash plate

60

where the force acting on the swash plate

60

in the direction from the suction-end circumferential part

112

toward the compression-end circumferential part

110

is assured owing to the effect of the inclined surface. If the compressor is designed such that the increase of the effect of the inclined surface and the decrease of the centrifugal force are offset relative to each other, the swash plate

60

is biased in the direction from the suction-end circumferential part

112

toward the compression-end circumferential part

110

with a force whose magnitude is constant irrespective of a change of the inclination angle. Further, if the magnitude of the centrifugal force acting on the swash plate

60

at the minimum inclination is minimized to a required level, the magnitude of the centrifugal force decreases with an increase of the inclination angle of the swash plate

60

. Accordingly, in the present embodiment, an average value of the magnitude of the centrifugal force acting on the swash plate

60

over the entire range of the inclination angle of the swash plate

60

is smaller than that in the embodiment of FIG.

5

. Therefore, the vibration in the compressor which does not employ any special means to remove the dynamic imbalance caused by locating the center of gravity of the rotary member

66

on the other side of the rotation axis M corresponding to the suction-end circumferential part

112

of the swash plate

60

, can be made smaller than the vibration in the compressor of the embodiment of

FIG. 5

, in any operating condition of the compressor, except the operating condition in which the discharge capacity of the compressor is minimum.

The construction of the swash plate type compressor according to the present invention is not limited to that of FIG.

1

. For instance, the solenoid-operated control valve

124

is not essential, and the compressor may use a shut-off valve which is mechanically opened and closed depending upon a difference between the pressures in the crank chamber

122

and the discharge chamber

24

. In place of or in addition to the control valve

124

, a solenoid-operated control valve similar to the control valve

124

may be provided in the bleeding passage

130

. Alternatively, a shut-off valve may be provided, which, is mechanically opened or closed depending upon a difference between the pressures in the crank chamber

122

and the suction chamber

22

.

While the presently preferred embodiments of this invention have been described above, for illustrative purpose only, it is to be understood that the present invention may be embodied with various changes and improvements such as those described in the SUMMARY OF THE INVENTION, which may occur to those skilled in the art.

Number	Name	Date	Kind
4846049	Terauchi et al.	Jul 1989	A
5063829	Takao et al.	Nov 1991	A
5706716	Unemura	Jan 1998	A
5836748	Kawaguchi et al.	Nov 1998	A
5950520	Kurosawa	Sep 1999	A
6044751	Kimura et al.	Apr 2000	A
6076449	Kawaguchi et al.	Jun 2000	A
20010049997	Ahn	Dec 2001	A1
20020073839	Tagami	Jun 2002	A1

Swash plate type compressor of variable capacity type

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