JP2003328934A - Swash plate type compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a swash plate type compressor excellent in volumeric efficiency of the compressor and control efficiency of a swash plate. <P>SOLUTION: A momentary rotation center O of the swash plate when the swash plate 10 is tilted is positioned on a predetermined position of the swash plate 10 in spite of a tilting angle of the swash plate. The momentary rotation center O is moved along a virtual circle (c). The virtual circle (c) passes all of center points of a virtual sphere (s) described by spherical surfaces 51a and 51b of a piston 7 when all of the pistons 7 are located in a dead end center. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable displacement type swash plate compressor whose discharge capacity increases and decreases in accordance with the inclination angle of a swash plate, and in particular, keeps the top clearance of a piston constant regardless of the inclination angle of the swash plate. The present invention relates to a swash plate compressor capable of increasing the volumetric efficiency of the compressor.

[0002]

2. Description of the Related Art As a conventional swash plate type compressor of this type, a swash plate type compressor described in Japanese Patent No. 3188716 is known.

FIG. 12 is a perspective view of a part of a swash plate type compressor disclosed in Japanese Patent No. 3188716, and FIG.
2 is a longitudinal sectional view of a portion shown in FIG. 2, and FIG. 14 is a sectional view taken along line XIV-XIV in FIG.

As shown in FIGS. 12 to 14, the conventional swash plate compressor has a shaft 905 and a driver (rotating member) 91.
3, annular disc (swash plate) 906, and sliding sleeve 921
And a plurality of pistons (not shown).

The shaft 905 is a casing (not shown).
It is rotatably supported by. The driver 913 has a substantially rod shape and is fixed to the shaft 905.
Rotates together with. A spherical head 915 is formed at the tip of the driver 913. The annular disc 906 has a radial hole 916 extending in its radial direction. The annular disc 906 is a support sleeve 9 of the sliding sleeve 921, which will be described later.
26 and 927 are rotatably attached. In the radial hole 916 of the annular disc 906, the head 9 of the driver 913 is inserted.
15 is inserted. The sliding sleeve 921 has a tubular shape,
It is attached to the shaft 905 so as to be movable in the central axis x direction, and rotates integrally with the shaft 905. Sliding sleeve 9
21 is a pair of support sleeves 926 extending in the radial direction.
An annular disc 906 having a support sleeve 926, 927 is rotatably mounted by a pair of pins 922, 923. The sliding sleeve 921 has a pin 9
22 and 923 rotatably support the annular disc 906, and the head 915 of the driver 913 is inserted into the radial hole 916 of the annular disc 906 so that the annular disc 906 can tilt with respect to the shaft 905. . Thus, the head portion 915 of the driver 913, the radial hole 916 of the annular disc 906, the support sleeve 926, and the radial hole 916.
The annular disk 906 is connected to the driver 913 by 927 and the pins 922 and 923 in such a manner that the tilt angle is variable.
A link mechanism that transmits the rotation of No. 3 to the annular disk 906 is configured. Each of the plurality of pistons is connected to the annular disc 906 through a pair of connecting pieces (shoe: not shown) and is inserted into a cylinder bore (not shown) formed in a rear side portion of the casing.

The tilt angle of the annular disc 906 (one end face in the thickness direction of the annular disc 906 and the central axis x of the shaft 905).
From the state where the angle formed by the virtual plane orthogonal to
When the pressure in the crank chamber (not shown) that houses the annular disc 906 or the like is lowered, the moment or the like generated in the annular disc 906 due to the differential pressure between the crank chamber side of the piston and the compression chamber side changes, and the annular disc 906 The inclination angle becomes large. On the contrary, when the pressure in the crank chamber is increased from the state where the inclination angle of the annular disc 906 is large, the inclination angle of the annular disc 906 becomes small.

When the inclination angle of the annular disc 906 changes in this way, the annular disc 906 moves around a certain point. This center is called the instantaneous rotation center O of the annular disk 906. In the conventional swash plate compressor shown in FIGS. 12 to 14, the instantaneous rotation center O of the annular disk 906 is obtained at the intersection of the virtual straight line L2 and the virtual straight line L4. Virtual straight line L
2 is a central point OS of the annular disk 906 and a driver 91.
It is a straight line which is orthogonal to the virtual straight line L1 passing through the center 917 of the head 915 of the third head 915 and is on the virtual plane f5 (see FIG. 14). The virtual plane f5 is parallel to the central axis x of the shaft 905, and the central axis x and the center 91 of the head 915 of the driver 913 are parallel to each other.
It is a plane that passes through 7. Virtual straight line L4 is pins 922, 9
It is a straight line orthogonal to the extension line L3 of the central axes a1 and a2 of 23 and the central axis x. As shown by the solid line in FIG. 13, when the inclination angle of the annular disc 906 is the minimum, the annular disc 90
The instantaneous rotation center O of 6 occurs on the center 917 of the head 915 of the driver 913. As shown by the chain double-dashed line in FIG.
When the inclination angle of the annular disc 906 is maximum, the instantaneous rotation center O of the annular disc 906 is the head 91 of the driver 913.
5 diagonally above the center 917 of 5. Therefore, the central axis x of the shaft 905 is the x-axis, the axis orthogonal to this x-axis and passing through the center 917 of the head 915 of the driver 913 is the y-axis, and the axis orthogonal to the x-axis and the y-axis is the z-axis. Then, the instantaneous rotation center O of the annular disc 906 is
It moves on the xy coordinate plane according to the change of the inclination angle of 6. The virtual straight line L1 overlaps the y-axis when the inclination angle of the annular disc 906 is the minimum, that is, the annular disc 9
The minimum angle of 06 is 0 °, but this is for convenience, and the actual minimum angle of the annular disk 906 is set to be slightly larger than 0 °.

The position of the center 917 of the head 915 of the driver 913 in the direction of the central axis x of the shaft 905 determines the top dead center position of the piston. Therefore, the shaft 90
5, the head 915 of the driver 913 in the direction of the central axis x
If the position of the center 917 of the piston is set to an appropriate position, the top clearance of the piston (between the end surface of the intake valve (not shown) on the cylinder block side and the top surface of the piston) will be irrespective of the inclination angle of the annular disc 906. (Clearance) can be kept constant, and the volumetric efficiency of the compressor can be improved.

[0009]

As described above, in the conventional swash plate compressor, the top clearance of the piston is constant regardless of the inclination angle of the annular disc 906, but the instantaneous rotation center O of the annular disc 906 is annular. Disk 906
It moves on the xy coordinate plane according to the change of the inclination angle of.

As shown in FIG. 15, the y-coordinate of the instantaneous rotation center O is plotted on the vertical axis, and the y-coordinate of the instantaneous rotation center O is plotted on the horizontal axis, as shown in FIG. 15, when the tilt angle of the annular disc 906 changes. If a graph with an inclination angle of 906 is taken (hereinafter referred to as a graph showing a change in the y coordinate of the instantaneous rotation center), the line segment of the graph becomes an upwardly rising graph.

There is a correlation between the graph showing the change in the y coordinate of the instantaneous rotation center and the graph showing the tilting characteristic of the link mechanism. The tilt characteristics of the link mechanism are purely possessed by the link mechanism except for the moment generated in the annular disk when the annular disk (swash plate) rotates with the shaft and the inertial force generated when the piston reciprocates. The characteristic is the relationship between the inclination angle of the annular disc and the crank chamber pressure when the inclination angle of the annular disc is maintained at a certain value. Further, as shown in FIG. 16, the horizontal axis of the graph showing the tilting characteristics of the link mechanism indicates the inclination angle of the annular disc, and the vertical axis indicates the pressure in the crank chamber required to maintain the inclination angle of the annular disc at a certain value. Represent each.

For example, if a graph showing the change in the y-coordinate of the instantaneous rotation center of a swash plate type compressor shows a line segment that rises to the right, a graph indicating the tilting characteristics of the link mechanism of the swash plate type compressor. Also, a rising line segment appears. on the other hand,
There is also a correlation between the tilting characteristic of the link mechanism and the controllability of the link mechanism, and if a graph showing the tilting characteristic of the link mechanism shows an upward rising line segment, the controllability of the link mechanism is If the line segment that descends to the right appears on the contrary, the controllability of the link mechanism is excellent.

In the conventional swash plate compressor, as described above, a graph showing the change in the y-coordinate of the instantaneous rotation center shows a line segment that rises to the right, and a graph showing the tilting characteristic of the link mechanism also rises to the right. Since the line segment of appears, the controllability of the link mechanism was poor. In this way, the conventional swash plate compressor was able to increase the volumetric efficiency of the compressor by keeping the top clearance of the piston constant, but the controllability of the link mechanism was poor, and the effect of this was the controllability of the swash plate. Was bad. Therefore, in the conventional swash plate compressor, in order to improve the controllability of the swash plate, the mass of the annular disc and the piston, the strength of the spring for urging the annular disc, and the like must be adjusted.

The present invention has been made in view of such circumstances, and an object thereof is to provide a swash plate type compressor excellent in volumetric efficiency of the compressor and excellent in controllability of the swash plate.

[0015]

In order to solve the above-mentioned problems, the invention according to claim 1 is directed to a shaft rotatably supported by a casing, and a rotating member fixed to the shaft and rotating integrally with the shaft. A swash plate that is tiltably attached to the shaft, a link mechanism that connects the rotating member and the swash plate, and that transmits the rotation of the rotating member to the swash plate, and a plurality of links provided in the casing. In a swash plate compressor including a plurality of pistons slidably inserted in the cylinder bores and a plurality of connecting members that connect the swash plate and the plurality of pistons to each other, when the swash plate tilts, The position of the instantaneous rotation center of the swash plate is on a fixed point on the coordinate system that rotates with the shaft regardless of the tilt angle of the swash plate, and all the pistons are located at the top dead center. Characterized in that located on the imaginary circle passing through the center point of the rotation of all of said coupling member when allowed.

As described above, when the swash plate is tilted, the position of the instantaneous rotation center of the swash plate is on a fixed point on the coordinate system that always rotates with the shaft regardless of the tilt angle of the swash plate. Y of the instantaneous rotation center of the swash plate even if the tilt angle of the plate changes
The coordinates do not change.

Further, the position of the instantaneous center of rotation of the swash plate when the swash plate is tilted is on a virtual circle passing through the center of rotation of all the connecting members when all the pistons are located at the top dead center. Since it is located, the top clearance of the piston can be set to the minimum.

According to a second aspect of the present invention, a shaft rotatably supported by the casing, a rotary member fixed to the shaft and rotating integrally with the shaft, and a swash plate tiltably attached to the shaft. A link mechanism that connects the rotating member and the swash plate and transmits the rotation of the rotating member to the swash plate; a swing plate that is rotatably attached to the swash plate; In a swash plate compressor including a plurality of pistons slidably inserted in a plurality of cylinder bores and a plurality of connecting members connecting the swing plate and the plurality of pistons, the swash plate is inclined. At that time, the position of the instantaneous rotation center of the swash plate is on a fixed point on the coordinate system that rotates with the shaft regardless of the inclination angle of the swash plate, and all the pistons are moved upward. Characterized in that located on the imaginary circle passing through the center point of the rotation of all of said coupling member when brought into position to a point.

As described above, when the swash plate is tilted, the position of the instantaneous rotation center of the swash plate is on a fixed point of the coordinate system that always rotates with the shaft regardless of the tilt angle of the swash plate. Y of the instantaneous rotation center of the swash plate even if the inclination angle of changes
The coordinates do not change.

Further, the position of the instantaneous rotation center of the swash plate when the swash plate is tilted is on a virtual circle passing through the rotation center points of all the connecting members when all the pistons are located at the top dead center. Since it is located, the top clearance of the piston can be set to the minimum.

According to the third aspect of the present invention, the casing is rotated.
A shaft that can be supported and fixed to this shaft.
The rotating member that rotates together with the shaft and the shaft
A swash plate tiltably attached to the shaft, and the rotating unit.
Material and the swash plate to connect the rotary member
Positioned so as to sandwich the swash plate with the link mechanism that transmits to the plate
A plurality of shoes each connected to the swash plate through a pair of shoes
And a swash plate type compressor provided with
The position of the instantaneous center of rotation of the swash plate when the
A seat that rotates with the shaft regardless of the inclination angle of the plate
It is on a fixed point on the frame and all of the above
All the pair of shoes when the
Is located on a virtual circle passing through the center of the virtual sphere
It is characterized by

As described above, when the swash plate is tilted, the position of the instantaneous rotation center of the swash plate is on a fixed point on the coordinate system that always rotates with the shaft regardless of the tilt angle of the swash plate. Y of the instantaneous rotation center of the swash plate even if the tilt angle of the plate changes
The coordinates do not change.

Further, the position of the instantaneous center of rotation of the swash plate when the swash plate is tilted is the center point of a virtual sphere drawn by the spherical surfaces of all the pairs of shoes when all the pistons are located at the top dead center. Since it is located on a virtual circle that passes through, the top clearance of the piston can be set to the minimum.

According to a fourth aspect of the present invention, a shaft rotatably supported by the casing, a rotary member fixed to the shaft and rotating integrally with the shaft, and a swash plate tiltably attached to the shaft. A link mechanism that connects the rotating member and the swash plate to transmit the rotation of the rotating member to the swash plate, a swing plate that is rotatably attached to the swash plate, and the swinging member via a rod. A plurality of pistons each connected to a moving plate, one end of the rod having a spherical shape is supported by the rocking plate so as to be relatively rollable, and the other end of the rod is fixed to the piston. In the plate compressor, the position of the instantaneous rotation center of the swash plate when the swash plate tilts is on a fixed point on the coordinate system that rotates together with the shaft regardless of the tilt angle of the swash plate, and all Before Characterized in that located on the imaginary circle passing through the center point of the one end portion of the spherical all the rods when is located at the top dead center of the piston.

As described above, when the swash plate is tilted, the position of the instantaneous rotation center of the swash plate is located on one fixed point of the coordinate system that always rotates with the shaft regardless of the tilt angle of the swash plate. Y of the instantaneous rotation center of the swash plate even if the inclination angle of changes
The coordinates do not change.

Further, the position of the instantaneous center of rotation of the swash plate when the swash plate is inclined passes through a virtual circle passing through the center points of the spherical ends of all the rods when all the pistons are located at the top dead center. Since it is located above, the top clearance of the piston can be set to the minimum.

According to a fifth aspect of the present invention, in the swash plate compressor according to any one of the first to fourth aspects, the link mechanism has an arc shape provided on one of the rotating member and the swash plate. A first elongated hole and a first pin that is provided on the other of the rotating member and the swash plate and that engages with the first elongated hole, and has an arc shape on one of the swash plate and the shaft. Second
Slot is provided, a second pin that engages with the second slot is provided on the other side of the swash plate and the shaft, and an arc of the arc drawn by the center lines of the first and second slots is provided. All of the centers of curvature coincide with the instantaneous center of rotation.

Since the link mechanism has the first and second pins and the first and second elongated holes as described above, it reliably guides the swash plate when the inclination angle of the swash plate changes. The link mechanism can be easily configured.

According to a sixth aspect of the present invention, in the swash plate compressor according to any one of the first to fourth aspects, the link mechanism has an arc shape provided on one of the rotating member and the swash plate. A support for supporting the swash plate rollably, having a first long hole and a first pin that is provided on the other of the rotating member and the swash plate and that engages with the first long hole. A sleeve is fixed to the shaft, one of the swash plate and the supporting sleeve is provided with an arc-shaped second long hole, and the other of the swash plate and the supporting sleeve is provided with the second long hole. A second pin to be engaged is provided, and both the centers of curvature of the arcs drawn by the center lines of the first and second elongated holes coincide with the instantaneous rotation center.

Since the second long hole or the second pin may be provided in the supporting sleeve as described above, the second long hole is easily formed as compared with the second long hole or the second pin provided in the shaft. A hole or a second pin can be provided.

The invention according to claim 7 is the swash plate compressor according to claim 5 or 6, characterized in that the center line of the second elongated hole straddles the center axis of the shaft.

As described above, since the center line of the second elongated hole straddles the center axis of the shaft, the fluctuation of the rotation balance of the swash plate can be reduced.

According to an eighth aspect of the present invention, in the swash plate compressor according to any one of the fifth to seventh aspects, when the inclination angle of the swash plate is the minimum, the position of the second pin is the It is characterized in that it is displaced along the thickness direction of the swash plate with respect to the middle point in the thickness direction of the swash plate.

As described above, when the inclination angle of the swash plate is the minimum, the position of the second pin deviates to one side along the thickness direction of the swash plate with respect to the middle point in the thickness direction of the swash plate. Therefore, the second pin can be attached to the swash plate without being disturbed by the disc portion of the swash plate.

According to a ninth aspect of the present invention, in the swash plate compressor according to any one of the first to fourth aspects, the link mechanism has an arc shape provided on one of the rotating member and the swash plate. A first elongated hole and a first pin that is provided on the other of the rotating member and the swash plate and that engages with the first elongated hole, the rear side end of the shaft to the front side end of the shaft. Is formed in the shaft, the swash plate is provided with an arc-shaped second elongated hole, the shaft is engaged with the second elongated hole, and the lubricating oil introduction path is formed. A second pin that traverses is provided, and the centers of curvature of the arcs drawn by the center lines of the first and second elongated holes are both coincident with the instantaneous rotation center, and the lubricating oil introduction path is formed by the second pin. A passage is provided in the second pin so as not to be blocked. To.

Since the passage is provided in the second pin as described above, the lubricating oil can be supplied to the seal member through this passage.

[0037]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a longitudinal sectional view showing a variable capacity type swash plate compressor according to a first embodiment of the present invention, showing a state where the inclination of the swash plate is minimum, and FIG. 2 is a variable capacity type swash plate type compressor of FIG. FIG. 3 is a vertical cross-sectional view showing a state in which the swash plate is the maximum inclination of the compressor, FIG. 3 shows the swash plate of the variable capacity type swash plate compressor of FIG. 1, and FIG. (B) is a cross-sectional view taken along the line III-III in FIG. 1, FIG. 4 shows the instantaneous center of rotation of the swash plate of the variable displacement type swash plate compressor in FIG. 1, and FIG. FIG. 3B is a conceptual diagram showing that the position is on a circle, and FIG. 3B is a conceptual diagram showing the relationship between the instantaneous rotation center and the x-axis, y-axis, and z-axis.

This variable capacity type swash plate compressor is used as one component of a refrigeration system using CO 2 as a refrigerant.

A rear head 3 is fixed to one end surface of a cylinder block 1 of this variable displacement type swash plate compressor via a valve plate 2, and a front head 4 is fixed to the other end surface thereof. Front head 4, cylinder block 1,
The valve plate 2 and the rear head 3 are integrally connected to each other in the central axis x direction of the shaft 5 by a through bolt 31 and a nut 32. Cylinder block 1 and valve plate 2
And casing 14 with rear head 3 and front head 4
Is configured.

The cylinder block 1 has a plurality of cylinder bores 6 around the shaft 5 at predetermined intervals in the circumferential direction.
Is provided. A piston 7 is slidably accommodated in each of the cylinder bores 6.

At one end of the piston 7, a spherical surface 51a for supporting a pair of shoes (coupling members) 60, 61 in a rollable manner,
Supporting recesses 51c and 51d having 51b are formed.

A crank chamber 8 for accommodating the swash plate 10 and the thrust flange (rotating member) 40 is formed in the front head 4.

The rear head 3 has a suction chamber 13 and a discharge chamber 12
And are formed. The suction chamber 13 is located around the discharge chamber 12. The suction chamber 13 contains the low-pressure refrigerant gas supplied to the compression chamber 22. The discharge chamber 12 has a compression chamber 2
The high-pressure refrigerant gas discharged from No. 2 is stored.

One end of the shaft 5 is the thrust flange 4
0 is rotatably supported by the front head 4 via a boss 40a and a radial bearing 26, and the other end of the shaft 5 is rotatably supported by the cylinder block 1 via a radial bearing 25 and a thrust bearing 24. . Shaft 5
Outer peripheral surface of one end (front end) of the casing and the casing 14
Sealing members 34 and 35 are disposed between the inner peripheral surface of one end portion (front end portion) of the. Sealing member 34,
Reference numeral 35 blocks the inside and outside of the casing 14.

The thrust flange 40 is fixed to the shaft 5 and rotates integrally with the shaft 5.

The swash plate 10 is attached to the shaft 5.
The swash plate 10 includes a drive unit 101 and a swash plate unit 102. The drive unit 101, as shown in FIG.
The substantially disk-shaped flange portion 101a and this flange portion 1
A pair of brackets 10 connected to the front side of 01a
1b and a boss portion 101c continuously provided on the rear side of the flange portion 101a. A first pin insertion hole 101d is formed in each of the pair of brackets 101b.
A second pin insertion hole 101e is formed in the boss portion 101c. First and second pin insertion holes 101d, 101
The center point of e is on an arc ar having a radius r centered on an instantaneous rotation center O of the swash plate 10 described later. The center point of the second pin insertion hole 101e is offset by Δy and Δx from the x-axis and y-axis, which will be described later. Swash plate part 102
Is a substantially disc shape, and the boss portion 101 of the drive portion 101
It is fixed to c. The swash plate 10 is connected to the thrust flange 40 via the link mechanism 41 with a variable inclination angle, and rotates integrally with the rotation of the thrust flange 40. Further, the swash plate 10 is biased toward the rear head 3 by the spring 23.

The instantaneous center of rotation O of the swash plate 10 is shown in FIG.
As shown in FIG. 5, it occurs on the intersection of a virtual circle (a locus of points equidistant from a fixed point on one plane) c and a virtual plane f.

The virtual circle c is a circle that passes through all the center points of rotation of the shoes 60 and 61 of each pair when all the pistons 7 are positioned at the top dead center. The center point of rotation of the shoes 60, 61 is the center point of the movement of the shoes 60, 61 when the movement of the swash plate 10 is transmitted to the piston 7 via the shoes 60, 61 and the piston 7 makes a reciprocating linear movement. Say. The center point of rotation of the shoes 60, 61 is the spherical surface portion 60 described later.
It coincides with the center point of the virtual sphere s drawn by a and 61a.

The imaginary plane f is parallel to the central axis x of the shaft 5, passes through the central axis x and the midpoint m in the longitudinal direction of the first pin 11, which will be described later, and intersects the imaginary circle c. .

The central axis x of the shaft 5 is defined as the x axis, and the axis on the imaginary plane f that intersects the imaginary circle c and is orthogonal to the x axis is the y axis. The axis orthogonal to the x axis and the y axis is the axis. Looking at the position of the instantaneous rotation center O of the swash plate 10 as the z-axis in the xyz coordinate system, the position of the instantaneous rotation center O does not change even if the tilt angle of the swash plate 10 changes. That is, the instantaneous rotation center O of the swash plate 10
The position of is on a fixed point on the xyz coordinate system that rotates together with the shaft 5 regardless of the inclination angle of the swash plate 10. The actual movement of the instantaneous rotation center O always moves on the virtual circle c regardless of the change in the inclination angle of the swash plate 10.

The center axis a of the swash plate 10 is parallel to the center axis x of the shaft 5 as shown in FIG. 4 (a) when the tilt angle of the swash plate 10 is minimum. Are eccentric. Further, as shown in FIG. 4B, the inclination angle α of the swash plate 10 changes around the instantaneous rotation center O.

The periphery of the swash plate 10 and one end of the piston 7 are connected via shoes 60, 61. Shoe 6
0 and 61 are spherical surfaces 60a and 61a and flat surfaces 60b and 61.
b. The spherical surfaces 60a and 61a are the piston 7
Of the flat surfaces 60b and 61b
Are in contact with the sliding surfaces 102a and 102b of the swash plate 10.

The shoes 60 and 61 relatively rotate on the sliding surfaces 102a and 102b of the swash plate 10 as the shaft 5 rotates. The rotation of the swash plate 10 causes the piston 7 to reciprocate in the cylinder bore 6.

The valve plate 2 is provided with a discharge port 16 for connecting the compression chamber 22 and the discharge chamber 12 and a suction port 15 for connecting the compression chamber 22 and the suction chamber 13 at predetermined intervals in the circumferential direction. It is provided.

The discharge port 16 is opened and closed by a discharge valve 17, and the discharge valve 17 is fixed to a rear head side end surface of the valve plate 2 together with a valve retainer 18 by a bolt 19.

The suction port 15 is opened and closed by a suction valve 21, which is arranged between the valve plate 2 and the cylinder block 1.

The thrust flange 40 fixed to the front end of the shaft 5 is rotatably supported on the inner wall surface of the front head 4 via a thrust bearing 33. A protrusion 46 is provided on the rear side of the thrust flange 40. The protrusions 46 are the pair of brackets 10 of the swash plate 10.
It is inserted between 1b. As mentioned above, thrust flange 4
0 and the swash plate 10 are connected via a link mechanism 41, and the swash plate 10 can be tilted with respect to a plane perpendicular to the shaft 5.

The link mechanism 41 includes the first pin 11 and the first pin 11.
The long hole 44, the second pin 9 and the second long hole 5a. The first pin 11 is the bracket 10 of the swash plate 10.
It is inserted into the first pin insertion hole 101d of 1b. The first elongated hole 44 has an arc shape and is formed in the protruding piece portion 46 of the thrust flange 40. The first slot 44 movably receives the first pin 11. The second pin 9 is inserted into the second pin insertion hole 101e of the boss portion 101c of the swash plate 10. The second elongated hole 5 a has an arc shape and is formed on the shaft 5. First and second elongated holes 44, 5a
The centers of curvature of the arcs drawn by the center lines s1 and s2 of both coincide with the instantaneous rotation center O of the swash plate 10. In other words, the intersection point of two virtual straight lines respectively orthogonal to the two tangents of the arc drawn by the center lines s1 and s2 of the first and second elongated holes 44 and 5a becomes the instantaneous rotation center O of the swash plate 10. .

Next, the operation of this variable displacement type swash plate compressor will be described.

When the rotational force of the vehicle-mounted engine (not shown) is transmitted to the shaft 5, the rotational force of the shaft 5 is transmitted from the thrust flange 40 to the swash plate 10 via the link mechanism 41, and the swash plate 10 is centered on the shaft 5. To rotate as. By the rotation of the swash plate 10, the shoes 60, 61 relatively rotate on the sliding surfaces 10a, 10b of the swash plate 10, and the rotational force from the swash plate 10 is converted into a linear reciprocating motion of the piston 7.

The piston 7 reciprocates in the cylinder bore 6, as a result of which the volume of the compression chamber 22 in the cylinder bore 6 changes, and due to this volume change, the suction, compression and discharge of the refrigerant gas are sequentially performed, and the swash plate 10 moves. A high-pressure refrigerant gas having a volume corresponding to the tilt angle is discharged.

At the time of suction, the suction valve 21 is opened, low-pressure refrigerant gas is sucked from the suction chamber 13 to the compression chamber 22 in the cylinder bore 6, and at the time of discharge, the discharge valve 17 is opened and the high pressure is supplied from the compression chamber 22 to the discharge chamber 12. The refrigerant gas is discharged.

When the pressure in the crank chamber 8 increases, the swash plate 10 moves in the destroke direction (direction in which the tilt angle of the swash plate 10 decreases), and as a result, the stroke amount of the piston 7 decreases and the discharge capacity increases. Decrease. Swash plate 1 at this time
The instantaneous rotation center O of 0 occurs on the virtual circle c shown in FIG. 4A, moves on the virtual circle c, and does not deviate from the virtual circle c. At this time, the first and second pins 11 and 9 of the link mechanism 41 slide in the first and second elongated holes 44 and 5a, respectively, and are attached to one ends of the first and second elongated holes 44 and 5a. (See Figure 1).

On the other hand, when the pressure in the crank chamber 8 decreases, the swash plate 10 moves in the stroke direction (direction in which the tilt angle increases), and as a result, the stroke amount of the piston 7 increases and the discharge capacity increases. . Also at this time, the instantaneous rotation center O of the swash plate 10 occurs on the virtual circle c shown in FIG. 4A, moves on the virtual circle c, and does not deviate from the virtual circle c. At this time, the first and second pins 11 of the link mechanism 41,
9 slides in the first and second elongated holes 44 and 5a,
The other ends of the first and second elongated holes 44, 5a are reached (see FIG. 2).

According to the variable displacement type swash plate compressor of this embodiment, the instantaneous center of rotation O of the swash plate 10 is always on the above-mentioned virtual circle c regardless of the inclination angle of the swash plate 10, so that the top clearance is It can be kept constant and high volume efficiency is obtained. Moreover, when a graph showing changes in the y coordinate of the instantaneous rotation center O in the xyz coordinate system is created, the line segments of the graph are parallel to the x axis. Therefore, the link mechanism 41
Also in the graph showing the tilting characteristic, the line segment is almost parallel to the x-axis, and the controllability is better than that of the conventional link mechanism.

Since the second pin insertion hole 101e is offset from the y-axis by Δx to the rear side, the second pin 9
When inserting into the second insertion hole 101e, the swash plate 102 does not get in the way, and the second pin 9 can be easily inserted into the second insertion hole 101e.

FIG. 5 is a vertical cross-sectional view showing a modified example of the variable capacity type swash plate compressor according to the first embodiment of the present invention, showing a state where the inclination of the swash plate is minimum. The same parts as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted.

In the modified example of the first embodiment, the radius of curvature r'of the arc drawn by the center lines s1 ', s2' of the first and second elongated holes 44 ', 5a' is the same as that of the first embodiment. And the radius of curvature r of the arc drawn by the center lines s1 and s2 of the second elongated holes 44 and 5a. Therefore, the second long hole 5
The center line s2 ′ of a ′ straddles the center axis x of the shaft 5 and intersects the center axis x at two points.

According to this modification, the same effect as that of the first embodiment is obtained, and the center line s2 'of the second elongated hole 5a' straddles the center axis x of the shaft 5, so that the swash plate is used. The central axis a of the swash plate 10 can be brought close to the central axis x of the shaft 5, whereby the rotational vibration of the swash plate 10 can be reduced.

FIG. 6 is a vertical sectional view showing a variable capacity type swash plate compressor according to a second embodiment of the present invention, showing a state where the inclination of the swash plate is minimum, and FIG. 7 is a variable capacity type swash plate type compressor of FIG. The swash plate of a compressor is shown, the figure (a) is a longitudinal cross-sectional view, and the figure (b) is FIG.
FIG. 7 is a sectional view taken along line VII-VII of FIG.

The variable capacity swash plate compressor of the second embodiment has the same configuration as the variable capacity swash plate compressor of the first embodiment except for a part, and therefore the description of the same parts will be omitted. Hereinafter, only a part having a configuration different from that of the first embodiment will be described.

The shaft 205 is formed with a lubricating oil introduction passage 205b communicating from the rear end to the front end. The second long hole is not formed in the shaft 205 in order to prevent the lubricating oil introduction path 205b from being divided in the middle. A sleeve mounting portion 205c is formed on the rear side portion of the shaft 205.

A sleeve 247 is attached to the shaft mounting portion 205c. The sleeve 247 has a cylindrical boss portion 247a extending in the radial direction. The internal space of the boss portion 247a is the second elongated hole 247b.

2 formed on the boss portion 101c of the swash plate 10
Short second pins 209 are inserted into the two second pin insertion holes 101e. These second pins 209
Is inserted into the second elongated hole 247b so as to sandwich the shaft 205.

According to the second embodiment, the same operational effect as that of the first embodiment is obtained, and since the lubricating oil introducing passage 205b communicating from the rear side to the front side is formed in the shaft 205, the lubricating oil introducing passage 205b is formed. Lubricating oil is supplied to the seal members 34, 35 through the seal members 34, 3
5 can be lubricated.

The second long hole 247 is formed in the sleeve 247.
Since b is provided, it is not necessary to form the second elongated hole 5a in the shaft 5, and thus the strength of the shaft 5 can be kept high.

FIG. 8 is a vertical sectional view showing a variable capacity type swash plate compressor according to a third embodiment of the present invention, showing a state where the inclination of the swash plate is minimum, and FIG. 9 is a variable capacity type swash plate type compressor of FIG. The swash plate of a compressor is shown, the figure (a) is a longitudinal cross-sectional view, and the figure (b) is FIG.
FIG. 9 is a sectional view taken along line IX-IX in FIG.

The variable capacity type swash plate compressor of the third embodiment has the same structure as the variable capacity type swash plate type compressor of the first embodiment except for a part, and therefore the description of the same parts will be omitted. Hereinafter, only a part having a configuration different from that of the first embodiment will be described.

In the third embodiment, the first and second pins 31
1, 309 and the first and second elongated holes 301f and 301g have the same relationship as the first and second pins 1 of the first embodiment.
The relationship between 1, 9 and the first and second elongated holes 44, 5a is opposite.

That is, in the third embodiment, a pair of brackets 346 is provided on the rear side portion of the thrust flange 340, and a first pin insertion hole 346a is formed in the pair of brackets 346. Pin insertion hole 346
The first pin 311 is inserted through a. Also, the swash plate 3
The front side portion of 10 is provided with a projecting piece 301e that is inserted between a pair of brackets 346.
The first elongated hole 301f is formed in e. A second pin insertion hole 305d is formed in the shaft 305, and a second pin 309 is inserted in the second pin insertion hole 305d. The lubricating oil passage 305 is provided in the second pin 309.
passage 30 that connects the rear side portion and the front side portion of b
9a is formed. Furthermore, the boss portion 30 of the swash plate 310
Two 1st long holes 301g are formed in 1c.

According to the third embodiment, the same operational effect as that of the first embodiment is obtained, and since the second pin 309 is fixed to the shaft 305, the lubricating oil passage 305b can be formed in the shaft 305. . Therefore, the seal members 34 and 35 can be lubricated by the lubricating oil passage 305b.

FIG. 10 shows a swash plate of a modified example of the variable capacity type swash plate compressor according to the third embodiment of the present invention.
-It is sectional drawing which follows the same line as the IX line. The same parts as those in the third embodiment are designated by the same reference numerals and the description thereof will be omitted.

In this modification, instead of forming the passage 309a in the second pin 309, two second pins 309 are used.
′ Is used to open the second pin 309 ′ so that the lubricating passage 305b is not blocked.

According to this modification, the same operational effects as those of the third embodiment are obtained.

FIG. 11 is a vertical cross-sectional view showing a variable displacement type swash plate compressor according to a fourth embodiment of the present invention in a state where the swash plate has a maximum inclination.

The variable capacity swash plate compressor of the fourth embodiment has the same structure as the variable capacity swash plate compressor of the first embodiment except for a part, and therefore the description of the same parts will be omitted. Hereinafter, only a part having a configuration different from that of the first embodiment will be described.

In the swash plate compressor of the first embodiment, the movements of the swash plate 10 are converted into reciprocating linear movements by the shoes 60 and 61 and transmitted to the piston 7, but in the fourth embodiment. In the swash plate type compressor, the movement of the swash plate 10 is changed to the swing plate 20.
Is converted into a reciprocating linear motion, and this reciprocating linear motion is transmitted to the piston 7 via a rod (connecting member) 27.

The swing plate 20 is attached to the swash plate 10 so as to be relatively rotatable. One end 27a of the rod 27 having a spherical shape is supported by the rocking plate 20 so as to be capable of relative rolling, and the other end 27b of the rod 27 is fixed to the piston 7.

As described above, in this embodiment, the rocking plate 20 and the piston 7 are connected by the rod 27. When the piston 7 reciprocates, the rod 27 moves the piston 7
Although it does not rotate with respect to the oscillating plate 20, the oscillating plate 20 rotates relatively to the one end portion 27a. Therefore,
In this embodiment, the center point of the one end portion 27a of the rod 27 is the center point of rotation of the rod 27.

The position of the instantaneous rotation center O of the swash plate 10 is on a fixed point on the xyz coordinate system that rotates with the shaft 5 regardless of the inclination angle of the swash plate 10, as in the other embodiments. It is on a virtual circle c passing through the center point s of the one ends 27a of all the rods 27 when all the pistons 7 are positioned at the top dead center.

According to the fourth embodiment, the same operational effects as the first embodiment can be obtained.

In the second embodiment, the second pin 209 may be fixed to the sleeve 247 and the boss 101c of the swash plate 10 may be provided with the second elongated hole. Further, the first pin 11 may be attached to the thrust flange 40 and the first elongated hole may be formed in the swash plate 10.

The present invention can also be applied to a retainer type swash plate compressor. In the retainer type swash plate compressor, a disc-shaped retainer is attached to the swash plate such that it can rotate relative to the swash plate like a rocking plate, and a shoe is slidably arranged on the retainer side end surface of the swash plate and the rod The spherical portion at one end is sandwiched between the shoe and the retainer, and the other end of the rod is connected to the piston. As described above, in the retainer type swash plate compressor, the swash plate and the retainer are connected to the piston by the rod. When the piston reciprocates, the rod rotates about the spherical portion relative to the swash plate. Therefore, in the retainer type swash plate compressor, the center point of the spherical portion of the rod is the center point of rotation of the rod. Then, as in the fourth embodiment,
The position of the instantaneous rotation center of the swash plate is on a fixed point on the coordinate system that rotates with the shaft regardless of the tilt angle of the swash plate, and all rods when all pistons are located at top dead center It lies on an imaginary circle that passes through the center point of the spherical part of.

[0095]

As described above, according to the swash plate type compressor of the invention described in claim 1, the y-coordinate of the instantaneous rotation center of the swash plate does not change even if the tilt angle of the swash plate changes. The graph showing the change in the y coordinate of the rotation center is a graph in which the line segment showing the y coordinate is parallel to the x axis. Therefore, the graph showing the tilting characteristic of the link mechanism is also a graph in which the line segment showing the tilting characteristic is approximately parallel to the x-axis, which is superior to the conventional tilting characteristic of rising. Therefore, the swash plate has excellent controllability without special tuning.

Moreover, since the top clearance of the piston can be set to the minimum, the volume efficiency of the compressor is excellent.

According to the swash plate compressor of the second aspect of the invention, y of the instantaneous rotation center of the swash plate is changed even if the inclination angle of the swash plate changes.
Since the coordinates do not change, the controllability of the oscillating plate is excellent without special tuning of the swash plate or the like.

Further, since the top clearance of the piston can be set to the minimum, the volume efficiency of the compressor is excellent.

According to the swash plate compressor of the third aspect of the present invention, like the swash plate type compressor of the first aspect of the present invention, the controllability of the swash plate is improved without special tuning of the swash plate or the like. And the volume efficiency of the compressor is excellent.

According to the swash plate compressor of the fourth aspect of the present invention, like the swash plate type compressor of the second aspect of the present invention, the swash plate controllability can be achieved without special tuning of the swash plate. And the volume efficiency of the compressor is excellent.

According to the swash plate compressor of the fifth aspect of the present invention, when the inclination angle of the swash plate changes, the swash plate can be reliably guided, and the link mechanism can be simply constructed. The controllability of the plate can be higher and the cost can be lower.

According to the swash plate type compressor of the sixth aspect of the present invention, the second elongated hole or the second pin can be provided more easily than the second elongated hole or the second pin provided on the shaft. Therefore, the manufacturing is easy.

According to the swash plate type compressor of the seventh aspect of the present invention, the fluctuation of the rotational balance of the swash plate can be reduced, so that the controllability of the swash plate can be further improved.

According to the swash plate compressor of the eighth aspect of the invention, the second pin can be attached to the swash plate without being disturbed by the disc portion of the swash plate. It can be attached easily.

According to the swash plate compressor of the ninth aspect of the present invention, since the lubricating oil can be supplied to the seal member through the passage of the second pin, the seal member can be lubricated and the life of the seal member is extended. be able to.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view showing a variable displacement swash plate compressor according to a first embodiment of the present invention in a state where the swash plate has a minimum inclination.

FIG. 2 is a vertical cross-sectional view showing the variable displacement swash plate compressor of FIG. 1 in a state where the swash plate has a maximum inclination.

3 shows a swash plate of the variable displacement type swash plate compressor of FIG. 1, FIG. 3 (a) is a longitudinal sectional view, and FIG. 3 (b) is III- of FIG.
It is sectional drawing which follows the III line.

4 shows an instantaneous center of rotation of a swash plate of the variable displacement swash plate compressor shown in FIG. 1, and FIG. 4 (a) is a conceptual diagram showing that the instantaneous center of rotation is located on a virtual circle; FIG. 6B is a conceptual diagram showing the relationship between the instantaneous rotation center and the x-axis, y-axis, and z-axis.

FIG. 5 is a vertical cross-sectional view showing a modified example of the variable displacement swash plate compressor according to the first embodiment of the present invention, showing a state where the inclination of the swash plate is minimum.

FIG. 6 is a vertical cross-sectional view showing a variable capacity type swash plate compressor according to a second embodiment of the present invention in a state where the swash plate has a minimum inclination.

7 shows a swash plate of the variable capacity type swash plate compressor of FIG. 6, FIG. 7 (a) is a vertical sectional view, and FIG. 7 (b) is VII- of FIG.
FIG. 7 is a sectional view taken along line VII.

FIG. 8 is a vertical cross-sectional view showing a variable displacement swash plate compressor according to a third embodiment of the present invention in a state where the swash plate has a minimum inclination.

9 shows a swash plate of the variable capacity type swash plate compressor of FIG. 8, FIG. 9 (a) is a vertical sectional view, and FIG. 9 (b) is IX-I of FIG.
It is a sectional view taken along the X-ray.

10 shows a swash plate of a modified example of the variable capacity type swash plate compressor according to the third embodiment of the present invention, and is a IX-I of FIG.
It is a sectional view taken along the same line as the X-ray.

FIG. 11 is a vertical cross-sectional view showing a variable displacement swash plate compressor according to a fourth embodiment of the present invention in a state where the swash plate has a maximum inclination.

FIG. 12 is a perspective view of a part of the swash plate compressor disclosed in Japanese Patent No. 3188716.

13 is a vertical cross-sectional view of the portion shown in FIG.

14 is a sectional view taken along line XIV-XIV in FIG.

FIG. 15 is a graph in which the vertical axis represents the y coordinate of the instantaneous rotation center O, and the horizontal axis represents the inclination angle of the annular disk.

FIG. 16 is a graph showing tilting characteristics of the link mechanism.

[Explanation of symbols]

5,205,305 shaft 5a, 247b, 301g Second long hole 7 pistons 9,209,309 Second pin 10,310 Swash plate (tilt rotary plate) 11,311 the first pin 13 Link pin (pin) 14 casing 20 rocking plate 27 rod 27a One end 27b the other end 40,340 Thrust flange (rotating member) 41,241,341 Link mechanism 44,301f First long hole 51a, 51b spherical surface 51c, 51d supporting recesses Shoe 60,61 Spherical part 60a, 61a 205b, 305b Lubricating oil introduction path 247 sleeve 309a passage O Instantaneous rotation center x central axis of shaft c virtual circle s virtual sphere s1 Center line of the first slot s2 Center line of the second slot

Claims (9)

[Claims] 1. A shaft rotatably supported by a casing, a rotating member fixed to the shaft and rotating integrally with the shaft, a swash plate tiltably attached to the shaft, and the rotating member. A link mechanism that connects the swash plate and transmits the rotation of the rotating member to the swash plate, a plurality of pistons slidably inserted in a plurality of cylinder bores provided in the casing, and the swash plate. And a plurality of connecting members that connect the plurality of pistons to each other, the position of the instantaneous rotation center of the swash plate when the swash plate is tilted, regardless of the tilt angle of the swash plate. It is on a fixed point on the coordinate system that rotates with the shaft, and it passes through the center of rotation of all the connecting members when all the pistons are located at the top dead center. Swash plate type compressor, characterized in that located above. 2. A shaft rotatably supported by a casing, a rotating member fixed to the shaft and rotating integrally with the shaft, a swash plate tiltably attached to the shaft, and the rotating member. A link mechanism that connects the swash plate and transmits the rotation of the rotating member to the swash plate, a swing plate that is rotatably attached to the swash plate, and a plurality of cylinder bores provided in the casing. In a swash plate compressor including a plurality of slidably inserted pistons and a plurality of connecting members that connect the swing plate and the plurality of pistons, the swash plate when the swash plate tilts The position of the instantaneous rotation center is on a fixed point on the coordinate system that rotates with the shaft regardless of the tilt angle of the swash plate, and all the pistons are located at the top dead center. The swash plate compressor is located on an imaginary circle that passes through the center points of rotation of all the connecting members. 3. A shaft rotatably supported by a casing, a rotating member fixed to the shaft and rotating integrally with the shaft, a swash plate tiltably attached to the shaft, and the rotating member. A link mechanism that connects the swash plate and transmits the rotation of the rotating member to the swash plate, and a plurality of pistons that are respectively connected to the swash plate via a pair of shoes positioned so as to sandwich the swash plate. In the swash plate type compressor provided with, the position of the instantaneous rotation center of the swash plate when the swash plate is tilted is on a fixed point on the coordinate system that rotates together with the shaft regardless of the tilt angle of the swash plate. A swash plate compressor characterized in that it is located on a virtual circle passing through the center point of a virtual sphere drawn by the spherical surfaces of all the pair of shoes when all the pistons are located at the top dead center. 4. A shaft rotatably supported by a casing, a rotating member fixed to the shaft and rotating integrally with the shaft, a swash plate tiltably attached to the shaft, and the rotating member. A link mechanism that connects the swash plate and transmits the rotation of the rotating member to the swash plate, a swing plate that is rotatably attached to the swash plate, and a link mechanism that is connected to the swing plate via a rod. A plurality of pistons, wherein one end of a spherical shape of the rod is supported by the oscillating plate so as to be relatively rollable with each other, and the other end of the rod is fixed to the piston. The position of the instantaneous rotation center of the swash plate when it tilts is on a fixed point on the coordinate system that rotates with the shaft regardless of the tilt angle of the swash plate, and all the pistons are top dead. A swash plate compressor located on an imaginary circle passing through the center points of the spherical ends of all the rods when positioned at a point. 5. The link mechanism is provided in one of the rotating member and the swash plate and has a circular arc-shaped first long hole, and in the other of the rotating member and the swash plate, the first link hole is provided. A first pin that engages with an elongated hole; one of the swash plate and the shaft is provided with an arc-shaped second elongated hole; and the other of the swash plate and the shaft has the second elongated hole. 5. A second pin that engages with is provided, and the centers of curvature of arcs drawn by the center lines of the first and second elongated holes are both coincident with the instantaneous rotation center. The swash plate compressor according to any one of 1. 6. The link mechanism is provided in one of the rotary member and the swash plate, and has a circular arc-shaped first long hole, and in the other of the rotary member and the swash plate, the first link hole is provided. A support sleeve having a first pin that engages with the elongated hole and rotatably supporting the swash plate, is fixed to the shaft, and one of the swash plate and the support sleeve has an arc-shaped first Two
And a second pin that engages with the second long hole is provided on the other of the swash plate and the supporting sleeve, and the center lines of the first and second long holes are drawn. The swash plate compressor according to any one of claims 1 to 4, wherein each of the centers of curvature of the arcs coincides with the instantaneous center of rotation. 7. The center line of the second elongated hole straddles the center axis of the shaft.
The swash plate compressor described. 8. The position of the second pin is displaced along the thickness direction of the swash plate with respect to the middle point in the thickness direction of the swash plate when the inclination angle of the swash plate is minimum. The swash plate compressor according to any one of claims 5 to 7, characterized in that. 9. The link mechanism is provided on one of the rotating member and the swash plate and has an arc-shaped first long hole, and on the other of the rotating member and the swash plate, the first link hole is provided. A first pin that engages with the elongated hole, a lubricating oil introduction path that communicates from a rear end of the shaft to a front end of the shaft is formed in the shaft, and the swash plate has an arc-shaped second length. A hole is provided, a second pin is provided on the shaft, which engages with the second elongated hole, and traverses the lubricating oil introducing passage, and an arc drawn by the center lines of the first and second elongated holes. 2. The passages are provided in the second pin so that the center of curvature of each of them coincides with the center of instantaneous rotation, and the lubricating oil introduction passage is not blocked by the second pin. The swash plate compressor according to any one of claims 1 to 4.