JP3404909B2 - Swash plate tilt guide structure for variable capacity swash plate compressor - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a swash plate tilt guide structure for a variable displacement swash plate compressor.

[0002]

2. Description of the Related Art A variable capacity type swash plate compressor for tilting a swash plate to change its capacity is disclosed in Japanese Patent Publication No. 4-74546. One ear is formed on the drive plate fixed to the rotary shaft, and a cam groove is formed on the ear. A fulcrum pin is fixed to the back of a swash plate slidably and tiltably supported on the rotary shaft, and the fulcrum pin is engaged with the cam groove. The tilting of the swash plate is guided by the engagement between the fulcrum pin and the cam groove, and the compression reaction force on the swash plate is received by the ear through the fulcrum pin and the cam groove. The cam groove is set to be displaced in the rotational direction of the rotary shaft from the plane connecting the top dead center corresponding portion on the swash plate on which the single-headed piston is located at the top dead center position and the central axis of the rotary shaft. The resultant force of the compression reaction force acts near the set position of the cam groove, and the ears properly receive the resultant force.

[0003]

The action position of the resultant force of the compression reaction force forms a loop, but the cam groove is parallel to the plane. Therefore, the loop moves in a direction parallel to the plane according to the change of the tilt angle of the swash plate. A thrust bearing is interposed between the drive plate and the front cover, and the resultant force is finally received by the front cover via the thrust bearing. Therefore, the resultant force is concentrated on a specific portion on the race fixed to the drive plate of the pair of races sandwiching the roller of the thrust bearing, and flaking occurs on the specific portion on the race. If the race on the drive plate side is allowed to rotate relative to the drive plate in order to avoid flaking, the sliding contact portion between the drive plate and the race is worn. The occurrence of flaking or wear reduces the reliability of the compressor.

An object of the present invention is to improve the reliability of a variable capacity swash plate compressor.

[0005]

To this end, according to the present invention, a single-headed piston is housed in a plurality of cylinder bores arranged around a rotary shaft so that the piston can reciprocate linearly, and a rotary support is fixed to the rotary shaft. , The swash plate is slidably and tiltably supported on the rotary shaft, and the swash plate tilt guide mechanism interposed between the rotary support and the swash plate guides the tilt of the swash plate, and the pressure and suction in the crank chamber. The present invention is directed to a variable capacity type swash plate compressor that controls the tilt angle of a swash plate according to the difference between the pressure and a one-headed piston. In the invention of claim 1, the swash plate is supported so as to be rotatable relative to the rotary shaft. , One guide pin having a spherical surface portion is provided on the swash plate, and a guide hole for slidingly guiding the spherical surface portion is provided on the rotary support to constitute the swash plate tilt guide mechanism, and the single-headed piston is top-dead. Rotation with the top dead center corresponding part on the swash plate placed at the point position The guide hole shifting set in the rotation direction of the rotation axis than the plane connecting the axis of rotation of, and the guide hole was interlinked obliquely the axis of to the plane.

According to the second aspect of the present invention, a suction passage for introducing the refrigerant gas into the compression chamber defined by the single-head piston in the cylinder bore is formed in the rotary valve, and the compression chamber is synchronized with the reciprocating movement of the single-head piston. Targeting a compressor in which a rotary valve is fixed to a rotary shaft so as to sequentially connect the suction port and the suction passage, the oblique direction of the axis of the guide hole with respect to the plane is from the rotation axis side of the rotary shaft. The direction of moving away from the plane as the distance increases.

According to the third aspect of the invention, the guide pin is tilted in alignment with the guide hole so that the guide pin and the guide hole are substantially parallel to each other when the tilt angle of the swash plate is maximum. Claim 4
In the invention, the supporting arm is provided so as to project from the rotary support, the guide hole is formed in the support arm, and the rotary support is provided with the balance weight on the side opposite to the support arm with respect to the rotation axis.

[0008]

The tilting of the swash plate is guided by the sliding contact guide action between the spherical surface portion and the guide hole and the slide support action on the rotary shaft. The spherical portion moves along the guide hole in a direction oblique to the plane. When the swash plate tilt angle is the maximum tilt angle, it is assumed that the plane intersects the center axis of the cylinder bore in which the swash plate tilt angle is the maximum tilt angle. When the rotation angle θ of the rotation axis at this time is 0 °, the swash plate tilt angle decreases from the maximum tilt angle. Is rotationally displaced relative to the rotation axis in the rotation direction or the opposite direction. That is, as the tilt angle of the swash plate becomes smaller than the maximum tilt angle, the position of the plane at the rotation angle θ = 0 ° of the rotation shaft shifts in the rotation direction of the rotation shaft or in the opposite direction. Therefore, the acting position of the resultant force of the compression reaction force shifts in the rotation direction of the rotation shaft as the tilt angle of the swash plate becomes smaller.

According to the second aspect of the present invention, as the tilt angle of the swash plate becomes smaller, the connection timing between the intake passage and the intake port in the rotary valve becomes relatively faster when the top dead center arrangement timing of the single-headed piston is used as a reference. Such a change in the suction start timing of the refrigerant gas suction improves the volumetric efficiency.

According to the third aspect of the invention, when the swash plate tilt angle is maximum, the guide pin is substantially parallel to the guide hole when viewed in the axial direction of the rotating shaft, so that the diameter of the guide hole can be made small and the rotary support member Weight reduction is possible.

According to the invention of claim 4, the rotational imbalance due to the weight of the support arm having the guide hole is canceled by the rotational imbalance due to the weight of the balance weight.
The rotary support rotates smoothly.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment embodying the present invention will now be described with reference to FIG.
~ It demonstrates based on FIG. As shown in FIG. 1, a front housing 2 is joined to the front end of the cylinder block 1, and a rear housing 3 is connected to the rear end of the cylinder block 1 with a valve plate 15 and valve forming plates 16 and 17.
Are joined through. The cylinder block 1, the front housing 2 and the rear housing 3 form a housing of the compressor. A rotary shaft 4 is rotatably supported by a front housing 2 and a cylinder block 1 which form a crank chamber 2-1. The front end of the rotating shaft 4 is the crank chamber 2
-It projects from -1 to the outside.

A disk-shaped rotary support 5 is fixed to the rotary shaft 4. A support arm 5-1 is provided on the outer peripheral side of the rotary support 5.
And a guide hole 5-2 is formed in the support arm 5-1. The guide hole 5-2 has a circular cross section.
A thrust bearing 9 is interposed between the rotary support 5 and the end wall of the front housing 2.

A swash plate 6 is directly supported on the rotary shaft 4 so as to be slidable, tiltable and relatively rotatable in the direction of the rotary axis 4-1 of the rotary shaft 4. A connecting piece 7 is fixed to the back of the swash plate 6, and a guide pin 8 is fixed to the connecting piece 7. A spherical portion 8-1 is integrally formed at the tip of the guide pin 8. The spherical surface portion 8-1 is slidably fitted in the guide hole 5-2. The tilting of the swash plate 6 is guided by the sliding contact guide relationship between the guide hole 5-2 and the spherical surface portion 8-1 and the sliding support action of the rotary shaft 4.

A balance weight 5-5 is provided on the peripheral portion of the rotary support 5 on the side opposite to the support arm 5-1 about the rotary shaft 4.
Are integrally formed. The balance weight 5-5 cancels the rotational imbalance due to the weight of the support arm 5-1 so that the rotary support 5 rotates smoothly.

A position regulating ring 10 is fixedly mounted on the rotary shaft 4. As shown in FIG. 4, the minimum inclination angle of the swash plate 6 is regulated by the contact between the swash plate 6 and the position regulation ring 10.
As shown in FIG. 1, the maximum inclination angle of the swash plate 6 is regulated by the contact between the inclination regulating projection 5-3 of the rotary support 5 and the swash plate 6.

As shown in FIG. 3, the cylinder block 1 is formed with a plurality of cylinder bores 1-1, 1-2, 1-3, 1-4, 1-5 arranged in an annular shape. -1 ~ 1
A single-headed piston 11 is housed in -5. The single-headed piston 11 defines a compression chamber 12 in the cylinder bores 1-1 to 1-5. The rotary motion of the rotary support 5 that rotates integrally with the rotary shaft 4 is transmitted to the swash plate 6 through the engagement between the guide hole 5-2 and the spherical surface portion 8-1. The rotating motion of the swash plate 6 is a hemispherical shoe 1.
The single-headed piston 11 is converted into forward and backward reciprocating swings via 3 and 14.

As shown in FIG. 1, a suction chamber 3-1 and a discharge chamber 3-2 are defined in the rear housing 3. The refrigerant gas in the suction chamber 3-1 pushes back the suction valve 16-1 on the valve forming plate 16 from the suction port 15-1 on the valve plate 15 by the returning motion of the single-headed piston 11, and the compression chamber 12
Flows in. The refrigerant gas flowing into the compression chamber 12 is discharged from the discharge port 15-2 on the valve plate 15 to the discharge valve 1 on the valve forming plate 17 by the forward movement of the single-headed piston 11.
7-1 is pushed away and discharged into the discharge chamber 3-2.

The reaction force of compression in each compression chamber 12 is a single-headed piston 11, a swash plate 6, a guide pin 8 and a support arm 5.
It acts on the rotary support 5 via -1. The compression reaction force acting on the rotary support 5 is received by the front housing 2 via the thrust bearing 9.

The rotary shaft 4 rotates in the direction of arrow α shown in FIG. 1 and 2, the inclination angle of the swash plate 6 is maximum, and the single-headed piston 11 in the cylinder bore 1-1 is arranged at the top dead center position. 4 and 5, the inclination angle of the swash plate 6 is the minimum. When the swash plate tilt angle is maximum, the spherical surface portion 8-1 is the farthest from the rotation axis 4-1 in the guide hole 5-2, and when the swash plate tilt angle is minimum, the spherical surface portion 8-1 is inside the guide hole 5-2. It comes closest to the axis of rotation 4-1.

When the inclination angle of the swash plate is maximum, in FIG. 2, the top dead center corresponding portion 6-1 on the swash plate 6 where the single-headed piston 11 in the cylinder bore 1-1 is located at the top dead center position, that is, the end surface of the shoe 14 A portion on the cam surface of the swash plate 6 that abuts the center of is on a plane γ that connects the rotation axis 4-1 of the rotation shaft 4 and the center axis β of the cylinder bore 1-1. The guide pin 8 is provided on the rotation direction α side of the rotation shaft 4 with respect to the plane γ between the rotation axis 4-1 and the central axis β. The guide hole 5-2 is located on the rotation direction α side of the rotation shaft 4 with respect to the plane γ between the rotation axis 4-1 and the central axis β. This position is near the position where the resultant force of the compression reaction force acts. The central axis δ of the guide hole 5-2 is set in a direction oblique to the plane γ so that the spherical surface portion 8-1 is separated from the plane γ as the swash plate inclination angle becomes smaller. The guide pin 8 is arranged so as to be substantially parallel to the central axis line δ of the guide hole 5-2 when the swash plate inclination angle is maximum.

The arrangement of the guide holes 5-2 with respect to the swash plate 6 is such that the swash plate 6 is rotationally displaced in the rotation direction α of the rotary shaft 4 as the swash plate inclination angle becomes smaller. As shown in FIG. 2, the rotation angle θ of the rotary shaft 4 when the single-headed piston 11 in the cylinder bore 1-1 is located at the top dead center position when the swash plate tilt angle is maximum is 0 °. Then, when the swash plate inclination angle is minimum and the rotation angle θ is 0 °, the top dead center corresponding portion 6-1 on the swash plate 6 is displaced from the plane γ in the rotation direction α of the rotation shaft 4, as shown in FIG. Therefore, the action position of the resultant force of the compression reaction force is displaced in the rotation direction α of the rotation shaft 4 more than when the swash plate inclination angle is maximum. That is, the positions where the thrust bearing 9 receives the resultant force of the compression reaction are dispersed according to the variation of the swash plate inclination angle,
Such dispersion avoids damage to the thrust bearing 9.

When the swash plate has a maximum inclination angle in which the guide pin 8 is deepest in the guide hole 5-2, the guide pin 8 is arranged to be substantially parallel to the guide hole 5-2. Such an arrangement relationship minimizes the size of the inclination of the guide pin 8 with respect to the guide hole 5-2 when the swash plate inclination angle is the minimum. Therefore, the diameter of the guide hole 5-2 can be reduced to the extent that the pin portions other than the spherical portion 8-1 of the guide pin 8 and the inner edge of the guide hole 5-2 do not interfere with each other, and the weight of the rotary support 5 can be reduced. is there.

Next, the embodiment shown in FIG. 6 will be described. In this embodiment, the guide pin 8 is attached to the swash plate 6 in an orthogonal state. An insertion groove 5-6 is connected to the tilted guide hole 5-2 as in the above embodiment. The guide pin 8 is inserted into the insertion groove 5-6, and the spherical portion 8-1 is inserted into the guide hole 5
-You will be guided through the inside. Also in this embodiment, the same effect of preventing damage to the thrust bearing 9 as described above can be obtained, and further, the guide pin 8 can be shortened and the weight can be reduced.

Next, the embodiment shown in FIGS. 7 to 12 will be described.
As shown in FIG. 7, the rear housing 3 is joined and fixed to the rear end of the cylinder block 1 via a gasket 18, a valve plate 19, a discharge valve forming plate 20 and a gasket type retainer forming plate 21.

As shown in FIG. 10, a plurality of cylinder bores 23 (six in this embodiment) are formed in the cylinder block 1 around the rotary shaft 4 at equal angular intervals.
A single-headed piston 11 is housed in each cylinder bore 23. A discharge chamber 3-2 is formed on the peripheral side in the rear housing 3, and a suction chamber 3-1 is formed in the radial center of the rear housing 3. The compression chambers 23-1, 2 divided into the cylinder bores 23 by the single-headed piston 11
3-2, 23-3, 23-4, 23-5, 23-6 are separated from the discharge chamber 3-2 by a valve plate 19, and a discharge port 19-7 is formed on the valve plate 19. There is. A flapper valve type discharge valve 20-1 is formed on the discharge valve forming plate 20.
A retainer 21-1 is formed on the top. Discharge valve 20-1
Opens and closes the discharge port 19-7 on the discharge chamber 3-2 side, and the retainer 21-1 regulates the amount of bending displacement of the discharge valve 20-1.

A cylindrical accommodating chamber 24 is formed at the center of the radius of the rear housing 3. The accommodation chamber 24 communicates with the suction chamber 3-1. A cylindrical rotary valve 25 is rotatably housed in the housing chamber 24. Support hole 2
The end portion 4-2 of the rotary shaft 4 supported in the inside 2 is projected into the accommodation chamber 24, and the protruding end portion 4-2 is the rotary valve 25.
Is fitted to. The rotation of the rotating shaft 4 is transmitted to the rotary valve 25 via the protruding end 4-2, and the rotary valve 25
Interlock with the rotation of the rotary shaft 4.

A suction passage 26 is formed through the rotary valve 25 from the back end surface 25-1 to the seal end surface 25-2. The inlet 26-1 of the suction passage 26 opens toward the suction chamber 3-1. As shown in FIG. 11, the outlet 2 of the suction passage 26
6-2 opens on the seal end surface 25-2. The seal end surface 25-2 is in sliding contact with the valve plate 19. That is, the valve plate 19 serves as the valve seat of the rotary valve 25.

The valve plate 19 has compression chambers 23-1 to 23-2.
3-6 as many suction ports 19-1, 19-2, 19-3, 19
-4, 19-5, and 19-6 are arranged around the rotary shaft 4 at equal angular intervals. Suction port 19-j and compression chamber 23
-j (j = 1 to 6) are in one-to-one communication with each other, and each suction port 19-j is connected to the outlet 2 of the suction passage 26 as shown in FIG.
It is connected to the orbiting area of 6-2. In FIG. 10, the compression chamber 23
The single-headed piston 11 in -1 is at the top dead center position, and the compression chamber 2
The single-headed piston 11 in 3-4 is at the bottom dead center position. The rotating shaft 4 is rotating in the direction of arrow α.

The compression chamber 23-j (j = 1 to 1) in which the one-headed piston 11 enters the suction stroke from the top dead center position to the bottom dead center position
6) is connected to the outlet 26-2 of the suction passage 26, and the inlet 3-4
The refrigerant gas introduced from the suction chamber 3-1 into the suction chamber 3-1 is sucked into the compression chamber 23-j in the suction stroke via the suction passage 26.

A capture groove 25-3 is formed in the seal end surface 25-2 of the rotary valve 25. The trapping groove 25-3 traps the refrigerant gas leaking from the suction port 19-j along the surface of the rotary valve 25 and supplies the refrigerant gas to the compression chamber near the start of the compression stroke. This capture supply improves the volumetric efficiency.

From the suction port 19-j to the rotary valve 25
A part of the refrigerant gas leaked along the surface of the above flows to the back pressure region 24-1 between the bottom surface of the housing chamber 24 and the back end surface 25-1.
The back pressure area 24-1 is sealed by the seal ring 27 into the suction chamber 3-1.
The back pressure region 24-1 presses the rotary valve 25 against the valve plate 19 to enhance the sealing performance between the valve plate 19 and the rotary valve 25. .

As shown in FIG. 8, when the tilt angle of the swash plate is maximum, the top dead center corresponding portion 6-1 on the swash plate 6 where the single-headed piston 11 in the cylinder bore 1-1 is located at the top dead center position, that is, A portion on the cam surface of the swash plate 6 that abuts the center of the end surface of the shoe 14 is on a plane γ that connects the rotation axis 4-1 of the rotation shaft 4 and the center axis β of the cylinder bore 1-1. The guide pin 8 is provided on the rotation direction α side of the rotation shaft 4 with respect to the plane γ between the rotation axis 4-1 and the central axis β. The guide hole 5-4 has a rotation direction α of the rotation shaft 4 which is larger than a plane γ between the rotation axis 4-1 and the central axis β.
On the side. This position is near the position where the resultant force of the compression reaction force acts. The central axis ζ of the guide hole 5-4 has a plane γ so that the spherical portion 8-1 approaches the plane γ as the swash plate inclination angle becomes smaller.
It is set in the direction that crosses diagonally.

The arrangement of the guide holes 5-4 with respect to the swash plate 6 causes the swash plate 6 to be rotationally displaced in the direction opposite to the rotation direction α of the rotary shaft 4 as the swash plate inclination angle becomes smaller. As shown in FIG. 8, the rotation angle θ of the rotary shaft 4 when the single-headed piston 11 in the cylinder bore 1-1 is located at the top dead center position when the swash plate tilt angle is maximum is 0 °. Then, when the swash plate inclination angle is minimum and the rotation angle θ is 0 °, as shown in FIG. 9, the top dead center corresponding portion 6-1 on the swash plate 6 is in a direction opposite to the rotation direction α of the rotation shaft 4 from the plane γ. It slips. Therefore, the acting position of the resultant force of the compression reaction force is displaced in the direction opposite to the rotation direction α of the rotation shaft 4 as compared with the case where the swash plate inclination angle is the maximum. That is, the receiving positions of the resultant force of the compression reaction force by the thrust bearing 9 are dispersed according to the variation of the swash plate tilt angle, and the damage of the thrust bearing 9 is avoided by such dispersion.

In this embodiment, the timing at which the suction passage 26 of the rotary valve 25 communicates with the suction port 19-j is unchanged. However, the top dead center arrangement timing of the single-headed piston 11 differs depending on the swash plate inclination angle, and the smaller the swash plate inclination angle, the later the top dead center arrangement timing.

A curve E _{1 in} FIG. 12 shows a pressure change in the compression chamber 23-j when the swash plate tilt angle is maximum, and a curve E ₂ shows a pressure change in the compression chamber 23-j when the swash plate tilt angle is minimum. In this figure, since the suction resistance is large at the maximum swash plate inclination angle, that is, at the time of maximum capacity operation, the timing of reaching the suction pressure in the compression chamber is delayed. In this embodiment, the inhalation timing based on the top dead center arrangement timing becomes relatively faster as the swash plate inclination angle becomes smaller, and becomes relatively late as the swash plate inclination angle becomes larger. Such inhalation timing is optimal for improving volumetric efficiency.

[0037]

As described in detail above, according to the present invention as set forth in claim 1, a plane connecting the top dead center corresponding portion on the swash plate on which the single-headed piston is arranged at the top dead center position and the rotation axis of the rotary shaft. Since the guide hole is set to be displaced in the rotation direction of the rotation shaft or the opposite direction thereof, since the axis line of the guide hole is oblique to the plane connecting the top dead center corresponding portion and the rotation axis line of the rotation shaft,
It is possible to improve the reliability of the compressor by dispersing the acting positions of the resultant force of the compression reaction force according to the variation of the tilt angle of the swash plate.

In the invention described in claim 2, since the suction timing can be appropriately changed according to the volume,
Volume efficiency can be improved. In the invention according to claim 3, the diameter of the guide hole can be reduced, and the weight of the rotary support can be reduced.

According to the fourth aspect of the present invention, the rotational imbalance due to the weight of the support arm can be offset, and the rotary support can be smoothly rotated.

[Brief description of drawings]

FIG. 1 is a side sectional view of an entire compressor showing a first embodiment embodying the present invention.

FIG. 2 is a sectional view taken along the line AA of FIG.

FIG. 3 is a sectional view taken along line BB of FIG.

FIG. 4 is a side sectional view of the entire compressor showing a swash plate inclination angle minimum state.

5 is a cross-sectional view taken along line CC of FIG.

FIG. 6 is a side sectional view of an essential part showing another example.

FIG. 7 is a side sectional view of the entire compressor showing another example.

8 is a cross-sectional view taken along the line DD of FIG.

FIG. 9 is a vertical cross-sectional view in a state where the swash plate tilt angle is minimum.

10 is a cross-sectional view taken along the line EE of FIG.

FIG. 11 is a perspective view of a rotary valve.

FIG. 12 is a graph showing changes in pressure in the compression chamber.

[Explanation of symbols]

1-1 to 1-5 ... Cylinder bore, 2-1 ... Crank chamber, 4 ... Rotating shaft, 5 ... Rotating support member, 5-2 ... Guide hole, 6 ... Swash plate, 8
... guide pin, 8-1 ... spherical part, 9 ... thrust bearing, γ ... plane, δ ... central axis of guide hole.

─────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP 63-288347 (JP, A) JP 6-200872 (JP, A) JP 63-186973 (JP, A) 114988 (JP, U) Actual Kaihei 5-52276 (JP, U) (58) Fields investigated (Int.Cl. ⁷ , DB name) F04B 27/08

Claims (4)

(57) [Claims] 1. A single-headed piston is housed in a plurality of cylinder bores arranged around a rotary shaft so as to be capable of reciprocating linear movement, a rotary support is fixed to the rotary shaft, and a swash plate can be slid on the rotary shaft. In addition, the swash plate tilt guide mechanism interposed between the rotary support and the swash plate guides the tilt of the swash plate, and the difference between the pressure in the crank chamber and the suction pressure via the single-head piston is provided. In a variable capacity type swash plate compressor that controls the inclination angle of the swash plate according to the above, the swash plate is supported on the rotation shaft so as to be relatively rotatable, and one guide pin having a spherical surface portion is provided on the swash plate. The swash plate tilt guide mechanism is provided by providing a guide hole for slidingly guiding the spherical surface portion in the rotary support, and the single-head piston is arranged at the top dead center position. The guide is provided in the rotation direction of the rotation axis rather than the plane connecting the axis. A swash plate tilt guide structure in a variable capacity type swash plate compressor in which the holes are shifted and the axes of the guide holes are oblique to the plane. 2. A compressor has a rotary valve having an intake passage for introducing a refrigerant gas into a compression chamber defined in a cylinder bore by a single-headed piston, and the intake passage of the compression chamber is synchronized with the reciprocating motion of the single-headed piston. A rotary valve is fixedly attached to the rotary shaft so as to sequentially connect the suction port and the suction passage, and the oblique direction of the axis of the guide hole with respect to the plane is as the distance from the rotation axis side of the rotary shaft increases. The swash plate tilt guide structure in the variable capacity swash plate compressor according to claim 1, wherein the swash plate tilt guide structure is in a direction away from the plane. 3. The guide pin according to claim 1, wherein the guide pin is tilted in accordance with the guide hole so that the guide hole and the guide pin are substantially parallel to each other when the tilt angle of the swash plate is maximum. Tilting guide structure for the variable displacement swash plate type compressor. 4. A support arm protruding from the rotary support, a guide hole being formed in the support arm, and a balance weight provided on the rotary support on the side opposite to the support arm with respect to the rotation axis. Any one of claim 1 to claim 3
The swash plate tilt guide structure in the variable capacity swash plate compressor according to the item.