JP2003148332A - Swash plate type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To miniaturize a compressor, and to enhance reliability by introducing a rotation stopping mechanism having the novel constitution for a wobble plate in a swash plate type compressor. SOLUTION: The wobble plate 6 is installed via a thrust bearing 13 on a drive plate 5 for rotating by being connected to a main shaft 4, and rocking by inclining, and fluid is compressed by reciprocating a plurality of pistons by rocking. The rotation stopping mechanism checks rotation of the wobble plate 6, and is provided with an outer ring 10 installed on the wobble plate 6, a pair of (two) cylindrical shoes 11 for engaging with a part of an inside surface, a pair of (two) spherical surface shoes 12 for engaging with a position different from those shoes, and a fixed center shaft 9 having a cross-sectional shape of, for example, a square so that these four shoes 11 and 12 engage with the respective different surfaces. Only four cylindrical shoes or spherical surface shoes may be allowable.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor for compressing a fluid such as a refrigerant in an air conditioner, in which a swash plate (drive plate) that is inclined with respect to its axis is attached to a main shaft. The present invention relates to a swash plate type compressor in which a wobble plate forced to swing by the swash plate reciprocates a plurality of pistons.

[0002]

2. Description of the Related Art There are two typical types of conventional swash plate type compressors. One type is that two hemispherical shoes attached to the end of the piston rod are attached to the front and back surfaces of the swash plate that is attached to the main shaft in a tilted state and rotates and swings. By sandwiching the swash plate in direct frictional contact, the reciprocating motion is directly taken out to the piston. The problem with this type is that the relative sliding speed between the swash plate and the shoe increases during high-speed rotation of the compressor, so that the swash plate and the shoe will not operate under operating conditions where the supply of lubricating oil is insufficient. This means that the lubrication state between the two becomes poor and problems such as seizure are likely to occur. Also,
Since there is a frictional contact portion, there is also a problem that the mechanical loss is large as compared with the case of rolling contact.

[0003] In another type, instead of taking out the reciprocating motion directly from the swash plate, for example, JP-A-2-275070.
As described in the publication, a wobble plate that engages with a swash plate-shaped drive plate via a rolling bearing such as a needle type thrust bearing is used, and the wobble plate makes a rotary motion. The wobble plate is connected to the wobble plate to reciprocate the piston. In this type, since a rolling bearing is used between the drive plate and the wobble plate, there is no problem of lubrication as in the former case and mechanical loss is small.

However, when a link mechanism such as a connecting rod is used for the connection between the wobble plate and the piston in this type, it is necessary to provide a detent mechanism for preventing the rotational movement of the wobble plate. This rotation stopping mechanism connects the wobble plate and the detent portion such as the housing. As the rotation stopping mechanism, as in the above-mentioned conventional example, a portion protruding in a radial direction from a part of the peripheral portion of the wobble plate. If an axial guide rod that slides into the
By providing not only the guide rod but also the protruding portion that engages with the guide rod on the wobble plate, the size of the entire compressor is increased. Further, since the wobble plate has an asymmetrical shape, an unbalanced moment such as a pendulum is generated around the center of the wobble plate, causing vibration, or the discharge capacity becomes unstable. Furthermore, when the compressor is operated at high speed, the sliding portion between the guide rod and the wobble plate may be overloaded and seizure may occur. I have anxiety.

The peripheral portion of the wobble plate is
When a part of each piston (piston rod) is slidably engaged directly without using a link mechanism such as a connecting rod, it is not necessary to provide a rotation stop mechanism. In this case, the wobble plate and A friction sliding portion is formed between the pistons.

[0006]

SUMMARY OF THE INVENTION The present invention is a swash plate compressor of the type that includes a wobble plate driven by a drive plate to reciprocate a piston, as found in the prior art. In view of the above-mentioned problems in the detent mechanism for the plate, the detent mechanism does not increase the size of the compressor,
A swash plate type that does not generate large vibrations and noises, is extremely robust, durable and reliable, and has a novel detent mechanism that enables stable operation of the compressor. The purpose is to provide a compressor.

[0007]

The present invention provides a swash plate type compressor described in claim 1 as a means for solving this problem.

In the swash plate type compressor of the present invention, the detent mechanism has an annular outer ring which is concentrically attached to the wobble plate as a unit or as a separate body, and different positions on the inner surface thereof. Two pairs of four shoes provided as sliding members on the inner surface of the shoe, and outer surfaces of the shoes that are different from each other so that the inner surfaces of the shoes engage with each other at different positions. A center shaft which is supported by the housing so as to be located at the center of the ring and not to rotate itself.

The main components of the detent mechanism in the present invention are one outer ring, four shoes, and one shoe.
Since it is only the center shaft of the book and the outer ring can be integrated with the wobble plate, the structure is simple and compact, so the rotation stopping mechanism is compactly packed in the center of the wobble plate and is in a high density state. As a result, the compressor can be downsized. In addition, since this detent mechanism has no fragile portion at all, it is extremely robust, and high operation stability and durability can be obtained, so that the reliability of the compressor can be enhanced. Furthermore, since the structure is well balanced, the possibility of generating vibrations and noise is reduced.

Since the swash plate type compressor of the present invention is provided with the rotation preventing mechanism having such a structure, a mechanism for changing the inclination angles of the drive plate and the wobble plate in order to change the discharge capacity, By providing a means for controlling the mechanism, it can be easily configured as a variable displacement compressor. Specifically, as a mechanism for changing the inclination angle of the wobble plate or the like, it is possible to provide a plane sliding surface in the axial direction between the four shoes and the center shaft. Further, the center shaft may be configured to be expandable and contractible. With either mechanism, the center position of the wobble plate, etc. moves in the axial direction, the tilt angle changes steplessly, and the strokes of all pistons change at the same time, resulting in no discharge capacity of the compressor. Change in stages.

The detent mechanism that is a feature of the present invention is roughly classified into three types. The first group is a type that uses one pair (two) of cylindrical shoes and one pair (two) of spherical shoes, and the second group is a type that uses two pairs of four shoes as all cylindrical shoes. Furthermore, the third group is a type in which all four shoes in two pairs are spherical shoes. In any of the formats, the above-mentioned excellent effects can be obtained.

In the swash plate compressor of the present invention, the base end of the center shaft can be supported in a cantilever manner by the housing. This significantly simplifies the construction of the compressor.

In the swash plate type compressor of the present invention, not only the base end of the center shaft is supported by the housing, but also the tip end is directly or indirectly supported by the housing, thereby supporting both ends. can do. Thereby, the support strength of the center shaft is significantly increased. In this case, if the tip end of the center shaft is intermediately supported by the main shaft via the bearing, the configuration is relatively simplified.

[0014]

1 to 3 show a swash plate type compressor according to a first embodiment of the present invention. The swash plate type compressor of the first embodiment is of a variable capacity type, and in FIG. 1 showing the longitudinal sectional structure of the entire compressor in an operating state that provides the maximum discharge capacity, 1 is the outer shell of the compressor. A part of the front housing 2 is a cylinder block integrated with the front housing 1 by fastening means such as through bolts (not shown). Inside the cylinder block 2, a plurality of (for example, five) cylinder bores 2a are formed in the lateral direction (“axial direction” described later) in FIG. 1 approximately uniformly around the center line. Reference numeral 3 denotes a rear housing, which is integrated with the front housing 1 and the cylinder block 2 by a fastening means (not shown) to form a housing. A suction chamber 26 as a space is formed in the outer peripheral portion inside the rear housing 3. In addition, a discharge chamber 27 as a space is formed in the central portion.

Reference numeral 4 is a main shaft for receiving a rotational power from an external power source, and a disc portion 4a having a substantially disk shape is integrally formed so as to be orthogonal to the main shaft. One ear-shaped arm 4b is provided so as to protrude in the axial direction from a part of the outer circumference of the disc portion 4a.
A guide groove 4c as a cam is formed in a predetermined position on the arm 4b in a predetermined shape. The main shaft 4 is supported by the front housing 1 via radial bearings 17 and 18, and is also supported by the front housing 1 in the axial direction via a thrust bearing 16 supporting the back surface of the disk portion 4a.
A shaft seal 19 is provided on these bearing portions to prevent fluid from leaking to the outside from around the main shaft 4.

Reference numeral 5 is a drive plate (swash plate),
It has two arms 5a protruding from the rear surface thereof toward the arm 4b on the main shaft 4 side, and one guide pin 15 is supported between the two arms 5a. The guide pin 15 is a guide groove 4 formed in the arm 4b.
It is inserted into c and is slidably engaged. Thereby, the drive plate 5 can rotate together with the main shaft 4 and can tilt with respect to the main shaft 4.

The drive plate 5 supports a substantially disk-shaped wobble plate 6 via a needle roller type thrust bearing 13. A plurality of spherical recesses are formed in the peripheral portion of the wobble plate 6, and a spherical end formed at one end of the piston rod 8 is fitted into each recess to be rotatably engaged. . The spherical ends formed at the other ends of the piston rods 8 are fitted into the spherical recesses formed in the plurality of pistons 7 and are rotatably engaged. These pistons 7
Cylinder bore 2 formed in the aforementioned cylinder block 2
It is slidably inserted in each a.

In the case of the first embodiment, the drive plate 5, wobble plate 6 and the like are prevented from rotating for the wobble plate 6 by the cantilevered center shaft 9 press-fitted into the cylinder block 2 on the extension line of the main shaft 4. It is supported via a mechanism 29. The respective embodiments of the present invention are different from each other in the specific structure of the rotation stopping mechanism and the structure of the center shaft and the like related thereto. Although a specific configuration of the rotation stopping mechanism 29, which is a feature of the first embodiment, will be described later, the outer ring 10 as an outer shell thereof is fitted and integrated with the wobble plate 6, and the drive plate 5 is The center opening of the outer ring 10 is loosely fitted to the outer peripheral surface of the outer ring 10 and can freely rotate with respect to the outer ring 10. In addition, in each of the embodiments of the present invention, the wobble plate 6 and the outer ring (10, etc.) are manufactured as separate components and then integrated, but both may be manufactured as one unit from the beginning. Reference numeral 14 is a snap ring for preventing the drive plate 5 from coming out of the outer ring 10 in the axial direction.

Reference numeral 20 is a valve plate made of a thick plate, and at least one suction port 23 and at least one discharge port 24 are opened so as to penetrate therethrough at positions corresponding to the cylinder bores 2a. Each intake port 23 of the valve plate 20 is closed from the cylinder bore 2a side by an intake valve made of a thin spring steel plate (not shown). Each discharge port 24 is closed from the discharge chamber 27 side by a part of the discharge valve 11 which is also made of a thin spring steel plate. Discharge valve 1
1 is fixed simultaneously when the valve stop plate 22 protecting it is screwed onto the valve plate 20 by means of bolts.
Further, the valve plate 20 and a suction valve (not shown) are sandwiched and fixed between the cylinder block 2 and the rear housing 3 when they are fastened and integrated. Two
A control valve 5 can adjust the pressure of the control pressure chamber 28, which is a common back pressure chamber of each piston 7, by using the pressure of the fluid in the suction chamber 26 and the discharge chamber 27.

The feature of the first embodiment is that the wobble plate 6 is used.
And the center shaft 9 and the like related thereto. 1 showing an operating state in which the discharge capacity is maximized, FIG. 2 showing an operating state in which the discharge capacity is substantially zero, and further a diagram showing a structure and an operation of a main part of the rotation stopping mechanism 29. As is clear from 3, the first
The detent mechanism 29 of the embodiment includes an outer ring 10 having an outer peripheral surface which is cylindrical and integrated with the above-mentioned wobble plate 6, and a pair of left and right cylindrical shoes 11 slidably engaged with the inner surface thereof. , A pair of upper and lower spherical shoes 12
And the above-mentioned center shaft 9 fixed to the cylinder block 2. Although the cross-sectional shape of the center shaft 9 is square, it may be another shape such as a rectangle.

In FIG. 3 (a) showing a cross section of the rotation stopping mechanism 29 in the assembled state, the left and right cylindrical shoes 1 are shown.
Since each inner surface of No. 1 and the left and right outer surfaces of the center shaft 9 opposed to each other are flat surfaces (shown as a flat surface P), each cylindrical shoe 11 slides on the center shaft 9 to rotate the shaft. It is possible to move in the direction (direction of the central axis of the center shaft 9 and the main shaft 4).

The outer surfaces of the left and right cylindrical shoes 11 shown in FIG. 3 (a) and the left and right inner surfaces of the outer ring 10 facing them are cylindrical surfaces having the same radius about the axis Y--Y. (Shown as a cylindrical surface C), the outer ring 10 slides around the cylindrical shoe 11 to move the axis Y-, as shown in each of FIGS. 3 (e) to 3 (g).
It can rotate around Y.

Further, in FIG. 3A, the inner surfaces of the upper and lower spherical shoes 12 and the upper and lower outer surfaces of the center shaft 9 facing them are both flat (shown as plane P). The spherical shoes 12 can slide on the center shaft 9 and move in the axial direction.

The outer surfaces of the upper and lower spherical shoes 12 shown in FIG. 3 (a) and the upper and lower inner surfaces of the outer ring 10 facing them are centered on the intersection of the axis YY and the axis XX. Since they are spherical surfaces having the same radius (shown as spherical surface S), the outer ring 10 slides around the spherical shoe 12 as shown in FIGS. 3 (b) to 3 (d). And can rotate about axis XX,
It also allows the outer ring 10 to rotate about axis Y-Y due to the presence of the cylindrical shoe 11, as described above.

As described above, the inner surfaces of the two cylindrical shoes 11 and the two spherical shoes 12 are both flat,
Since they can slide along the left and right and upper and lower outer surfaces of the center shaft 9 having a square cross section, the outer ring 10 can freely move in the axial direction in a state where the rotation is suppressed.

Further, with the above structure, the outer ring 10 can rotate not only about the axis Y-Y but also about the axis X-X. As a combination of rotations around
The central axis of the outer ring 10 can be oriented in any direction within a predetermined angle range.

Therefore, the detent mechanism 29 of the first embodiment, which comprises the center shaft 9 having a square cross section and fixed, the two cylindrical shoes 11 and the two spherical shoes 12, and the outer ring 10, is the outer ring. The wobble plate 6 integrated with 10 is allowed to move in the axial direction along the center shaft 9 and to freely tilt and change the direction within a predetermined angle range, but to rotate around the center shaft 9. Prevent doing.

Since the swash plate type compressor of the first embodiment is constructed in this way, it operates as follows. When the main shaft 4 is rotationally driven by an external power source such as an internal combustion engine or a motor mounted on the vehicle, the main shaft 4
The drive plate 5 connected to the disc portion 4a via the arm 4b, the guide groove 4c, the pin 15, and the arm 5a rotates integrally with the main shaft 4.
However, since the wobble plate 6 is supported by the drive plate 5 via the thrust bearing 13 and is prevented from rotating (spinning) by the rotation stopping mechanism 29 as described above, the wobble plate 6 is Only when tilted with respect to an imaginary plane orthogonal to the shaft 4, only a swinging motion of a size corresponding to the tilt angle is performed. As a result, the plurality of pistons 7 connected to the wobble plate 6 via the piston rods 8 reciprocate in the respective cylinder bores 2a.

In the case of the first embodiment, the drive plate 5 and the wobble plate 6 move when the guide pin 15 moves while sliding in the guide groove 4c on the main shaft 4 side and the center shaft 9 and the center shaft 9. As the tilt angle with respect to changes, the strokes of all pistons 7 change at the same time by the same amount. As a result, the discharge capacity of the compressor changes continuously.

Among the plurality of pistons 7, the working chamber formed on the top surface of the piston 7 in the suction stroke expands to a low pressure, so that the fluid in the suction chamber 26 to be compressed, for example, the air conditioner. The refrigerant is the suction port 2 of the valve plate 20.
The suction valve provided at 3 is pushed open to flow in. On the contrary, since the working chamber formed on the top surface of the piston 7 in the compression stroke is reduced, the fluid inside is compressed to a high pressure, and the discharge valve provided at the discharge port 24 of the valve plate 20 is compressed. 21 is pushed open and discharged into the discharge chamber 27.
The discharge capacity in that case is approximately proportional to the stroke length of the piston 7 determined by the inclination angles of the drive plate 5 and the wobble plate 6.

As described above, when the tilt angles of the drive plate 5 and the wobble plate 6 are changed, the discharge capacity of the compressor changes. Therefore, in order to control the discharge capacity, the first
In the compressor of the embodiment, the pressure in the control pressure chamber 28, which is the back pressure of all the pistons 7, is changed using the control valve 25. Normally, in the control pressure chamber 28, an intermediate pressure between the high pressure in the discharge chamber 27 and the low pressure in the suction chamber 26 has an intermediate pressure.
Introduced from 5.

When the pressure in the control pressure chamber 28, that is, the back pressure of the piston 7, is increased, the balance with the pressure in the working chamber formed on the top surface of each piston 7 is lost, so that a new balance is obtained. By the way, the average position of the plurality of pistons 7 moves toward a position close to the valve plate 20. As a result, the strokes of all the pistons 7 are reduced all at once, so that the discharge capacity of the compressor is reduced steplessly.

FIG. 2 shows a state in which the stroke of the piston 7 becomes substantially zero and the discharge capacity also becomes substantially zero. In this case, the pressure in the control pressure chamber 28 becomes maximum, and the inclination angles of the drive plate 5 and the wobble plate 6 become substantially zero, so that even if the drive plate 5 rotates together with the main shaft 4, The wobble plate 6 is in a substantially stationary state with substantially no swing motion. Therefore, all the pistons 7 are substantially at the position of the top dead center and hardly reciprocate in the cylinder bore 2a.

On the contrary, when the pressure control valve 25 is actuated to reduce the pressure in the control pressure chamber 28, the back pressure acting on the pistons 7 becomes small, so that the strokes of all the pistons 7 are simultaneously made. As the size increases, the discharge capacity of the compressor increases infinitely. At this time, drive plate 5
Thus, the inclination angle of the wobble plate 6 increases, and the amplitude of the swinging motion of the wobble plate 6 also increases. Figure 1
Indicates a state in which the pressure in the control pressure chamber 28 is minimized, the inclination angle of the drive plate 5 and the wobble plate 6 is maximized, and the stroke of the piston 7 and the discharge capacity of the compressor are maximized. ing.

The characteristic of the first embodiment is that the wobble plate 6 is used.
With respect to the center shaft 9 having a square cross section fixed by a cantilever (however, if it is a shape other than a perfect circle, such as a rectangle, it may not be a square). This is to prevent the wobble plate 6 from rotating by connecting it through the rotation stopping mechanism 29 including the cylindrical shoe 11 and the two spherical shoes 12 that are also slidable in the axial direction.

In the first embodiment, the wobble plate 6 and the drive plate 5 are provided by providing the small and robust detent mechanism 29 at the center of the wobble plate 6.
It is possible to reliably prevent the wobble plate 6 from rotating while firmly supporting. Therefore, the entire swash plate type variable displacement compressor is downsized, and the durability and reliability are improved. Further, since the rotation stopping mechanism 29 has a simple structure, it is also advantageous in terms of cost. Furthermore, since the detent mechanism 29 of the first embodiment has a structure in which looseness does not easily occur and has a symmetrical shape with respect to the center, it is possible to prevent generation of secondary vibration and noise even at high speed operation. It is possible to reduce wear of the sliding portion.

As a means for changing the inclination angle of the drive plate 5 and the wobble plate 6 to change the discharge capacity of the compressor, the pressure in the control pressure chamber 28 is changed in the first embodiment. Is configured as
It goes without saying that the present invention does not have a feature in this means, and therefore other means capable of achieving the same purpose can be adopted.

FIG. 4 shows a second embodiment of the swash plate type compressor of the present invention. The feature of the second embodiment is that, compared with the cantilever-supported center shaft 9 in the first embodiment, a center shaft 30 having both ends supported in the axial direction is used.
The cross-sectional shape of the center portion of the center shaft 30 is a square or the like other than the circular shape like the center shaft 9, but the end portion near the main shaft 4 has a circular cross section, and the main shaft 4 of the main shaft 4 is inserted through the radial bearing 31. It is supported by the disk portion 4a and indirectly supported by the housing. Also, as the rotation stop mechanism,
The same structure as the detent mechanism 29 of the first embodiment is used.

In the swash plate type compressor of the second embodiment, since the center shaft 30 is supported at both ends, the structure is more robust than that of the swash plate type compressor of the first embodiment. Except for this point, the configuration is the same as that of the first embodiment, so that the second embodiment has substantially the same operational effect as that of the first embodiment.

FIG. 5 and FIG. 6 show a third embodiment of the swash plate type compressor of the present invention. The structural feature of the third embodiment is that, in place of the center shaft 9 in the above-described first embodiment, the center shaft 9 and a pair of spherical shoes 12 have the same shape and are partially Spherical head 32a
The center shaft 32 having the above is used. Since the center shaft 32 has the enlarged head portion 32a, it cannot be inserted and assembled into the outer ring 10 similar to the first embodiment as it is.
In the third embodiment, a spherical shoe 34 having a spherical inner surface matching the spherical outer surface of the head portion 32a and having a flat outer surface is used, and the spherical shoe 34 can be inserted in the axial direction. As possible, an outer ring 35 having a groove 35a having a flat bottom surface is used.
Otherwise, it has the same configuration as the first embodiment.

The detent mechanism 33 in the third embodiment is
Since the spherical shoe 12 in the first embodiment is integrated with the center shaft 32, the center of the outer ring 35 and the drive plate 5 and the wobble plate 6 cannot move in the axial direction. The discharge capacity of the machine cannot be changed. Therefore, the swash plate type compressor of the third embodiment is a fixed displacement type. However, the characteristics of the detent mechanism 33 in the third embodiment, such as the detent action and the robustness, are the same as the detent mechanism 29 of the first embodiment.
The swash plate compressor of the third embodiment has the same effects as those of the first embodiment except that the discharge capacity is not variable. In the detent mechanism 33 of the third embodiment, the pair of spherical shoes 34 that engage with the spherical surface of the head portion 32a of the center shaft 32 act partially similar to the spherical shoe 12 of the first embodiment.

FIG. 7 shows a fourth embodiment of the swash plate type compressor of the present invention. The feature of the fourth embodiment is that, compared with the center shaft 32 of cantilever support in the third embodiment, a center shaft 36 of both ends supporting longer in the axial direction is used.
The central portion of the center shaft 36 is provided with a partially spherical head portion 36a. The outer ring 35 and the spherical shoe 34 similar to those in the third embodiment are used to receive the head portion 36a. Since the detent mechanism in the fourth embodiment is substantially the same as the detent mechanism 33 in the third embodiment, the same reference numeral 33 is attached.

In the swash plate type compressor of the fourth embodiment, since the center shaft 30 is supported at both ends, the structure is more robust than that of the swash plate type compressor of the third embodiment. Except for this point, the configuration is the same as that of the third embodiment, and therefore the fourth embodiment has substantially the same operational effects as the case of the third embodiment.

FIG. 8 shows a fifth embodiment of the swash plate type compressor of the present invention. In the fifth embodiment, the swash plate type compressor of the third embodiment, which is a fixed capacity type, is a variable capacity type. Therefore, since the head portion 32a of the center shaft 32 needs to be configured to be movable in the axial direction, in the fifth embodiment, the base portion 32b of the center shaft 32 is not fixed to the cylinder block 2 but is formed on the cylinder block 2. It is slidably inserted only in the axial direction into the formed axial hole 2b. For that purpose, a key or spline (not shown), serration, or the like is provided on the base portion 32b. Further, a compression spring 37 is mounted in the hole 2b so as to constantly urge the drive plate 5 and the wobble plate 6 in the axial direction in a direction in which the inclination angle increases. The fifth
In the embodiment, the space in the hole 2b is connected to the atmosphere or is communicated with a low pressure source such as the suction chamber 26 which has a substantially constant low pressure. The other structure is the same as that of the third or first embodiment.

Since the swash plate type compressor of the fifth embodiment is constructed in this way, when the pressure of the control pressure chamber 28, that is, the back pressure of all the pistons 7, is changed by the control valve 25,
For the reason described in the description of the operation of the swash plate type compressor of the first embodiment, the center of the drive plate 5 and the wobble plate 6, that is, the head 3 of the center shaft 32.
Since the position of 2a moves in the axial direction, the inclination angles of the drive plate 5 and the wobble plate 6 and the strokes of all the pistons 7 simultaneously change, and the discharge capacity of the compressor changes steplessly.

FIG. 8 can also be used in describing the sixth embodiment of the present invention. The sixth embodiment is also a variable displacement type swash plate compressor, and differs from the fifth embodiment described above in that the internal space of the axial hole 2b formed in the cylinder block 2 is controlled by the second control pressure. As the chamber 38, this control pressure chamber 3
A control pressure intermediate between the discharge pressure and the suction pressure is introduced from the control valve 25 to the control valve 8 as described above. On the other hand, the control pressure chamber 28 is connected to the suction chamber 26 to introduce a low pressure of a predetermined height.

In the swash plate type compressor of the sixth embodiment, the pressure in the control pressure chamber 38 controlled by the control valve 25,
By the balance with the pressure in the control pressure chamber 28, and when the compression spring 37 is provided, the urging force thereof, the total value of the compression reaction force and the suction reaction force acting on all the pistons 7, etc. The positions are added to determine the position of the head portion 32a of the center shaft 32. At the same time, since the inclination angle of the wobble plate 6 and the stroke of the piston 7 are determined, the discharge capacity of the compressor can be continuously changed by operating the control valve 25.

As is clear from the above description, in the swash plate type compressors of the first to sixth embodiments, the pair of two cylindrical shoes 11 and the pair of two spherical shoes 1 are used.
These are referred to as the first group of examples because they have the common feature of having 2 or 34. The swash plate type compressors of the seventh to twelfth embodiments to be described below are characterized in that four spherical shoes are used in two pairs without using spherical shoes. Therefore, these will be named the second group of Examples. Further, the swash plate type compressors of the following thirteenth to eighteenth embodiments have two spherical shoes.
Since four of them are used in a pair and two of them are constrained to be immovable, they will be referred to as the third group of embodiments.

9 to 11 show a seventh embodiment of the swash plate type compressor of the present invention. The features of the seventh embodiment are enlarged in FIG.
This is in the structure of the rotation stopping mechanism 39 as shown in FIG. The rotation stopping mechanism 39 includes a pair of cylindrical shoes 40 slidably contacting the upper and lower surfaces of the cantilevered center shaft 9 having a square cross section. As is clear from FIG. 11 (c), the cylindrical surfaces formed on the outer surfaces of the upper and lower cylindrical shoes 40 are centered on the axis XX shown in FIG. 11 (a). A generally rectangular and annular inner ring 41 having a cylindrical inner surface (shown as cylindrical surface C) of substantially the same radius as this cylindrical surface and slidably contacting it,
The center shaft 9 and the two cylindrical shoes 40 are provided so as to be included therein. As is clear with reference to FIG. 11C, the upper and lower outer surfaces of the inner ring 41 are flat surfaces and are in close contact with the upper and lower inner surfaces of the outer ring 42.

As is apparent from FIG. 11A, a part of the left and right surfaces of the inner ring 41 has a protrusion 41a.
To form a cylindrical surface centered on the axis Y-Y. The protrusion 41a is engaged with the groove 42a whose bottom surface formed on the left and right inner surfaces of the outer ring 42 is flat. However, for assembly reasons, the cylindrical shoe 43 is provided in the groove 42a, and the left and right cylindrical shoes 43 are provided. A cylindrical surface is formed on the inner surface of, and as shown as a cylindrical surface C, it is slidably engaged with the cylindrical surface of the projection 41a of the inner ring 41.

Since the detent mechanism 39 in the seventh embodiment is constructed in this way, the inner ring 41 is free to rotate with respect to the center shaft 9 around the upper and lower cylindrical shoes 40 and the axis XX. At the same time, the outer ring 42 with respect to the inner ring 41 is at a common cylindrical surface C between the cylindrical inner surface of the cylindrical shoe 43 and the outer surface of the projection 41a of the inner ring 41 facing the inner surface. Sliding allows for free rotation about axis Y-Y. As a combination of these two rotational movements, the outer ring 42 and the wobble plate 6 and the drive plate 5 carried by it can freely change their directions on the non-rotating center shaft 9 within a predetermined angular range. it can.

As a result, in the swash plate type compressor of the seventh embodiment, the wobble plate 6 makes an oscillating motion without rotation in response to the rotational drive of the drive plate 5, and the piston 7 is moved within the cylinder bore 2a. Not only is fluid sucked and compressed by reciprocating motion, but also the tilt angles of the drive plate 5 and the wobble plate 6 are changed according to changes in the pressure of the control pressure chamber 28 by the control valve 25, and all the pistons 7 The same operational effect as that of the above-described first embodiment is achieved by changing the stroke and continuously changing the discharge capacity of the compressor.

In the same way that the second embodiment exists in comparison with the first embodiment, the swash plate type compressor of the eighth embodiment as shown in FIG. 12 is constructed for the seventh embodiment. You can Only the detent mechanism 39 in the eighth embodiment is the same as that in the seventh embodiment, but the points other than the detent mechanism 39 including the center shaft 30 and the radial bearings 31 supported at both ends are not shown. Since it is the same as the second embodiment shown in FIG. 4 and the effects obtained are substantially the same, detailed description overlapping with them will be omitted here.

13 and 14 show a ninth embodiment of the swash plate type compressor of the present invention. The feature of the ninth embodiment resides in the structure of the rotation stopping mechanism 44. The ninth embodiment with respect to the seventh embodiment is
Since the position of the third embodiment is as if it were the same as that of the first embodiment, the configuration of the ninth embodiment can be easily inferred from the above description. Therefore, in brief description, as shown in FIG.
An inner ring 41, an outer ring 42, and a pair of left and right cylindrical shoes 43, which are similar to those used in the rotation stopping mechanism 39 of the seventh embodiment shown in FIG.

However, in the ninth embodiment, since the center shaft 45 having a partially cylindrical head is used, in order to receive the head 45a,
A pair of upper and lower cylindrical shoes 46 having an inner surface consisting of a cylindrical surface centered on the axis XX is used. Other configurations are similar to those of the above-described third or seventh embodiment.

In the swash plate type compressor of the ninth embodiment, since the center shaft 45 is cantilevered by the cylinder block 2 and the head portion 45a of the center shaft 45 does not move, its discharge capacity is constant. It is a fixed capacity type. Except for that point, the function and effect are similar to those of the swash plate type compressor of the seventh embodiment.

FIG. 15 shows a tenth embodiment of the swash plate type compressor of the present invention. The swash plate type compressor of the tenth embodiment has a cantilevered center shaft 45 of the ninth embodiment.
The center shaft 47 supported at both ends
It is equivalent to the one replaced by. Therefore, the rotation stopping mechanism 4
4 is the same as that of the ninth embodiment. Further, the head portion 47a formed in the central portion of the center shaft 47 also has a cylindrical surface formed in part. The operational effects of the tenth embodiment are the same as those of the ninth or fourth embodiment.

FIG. 16 shows an eleventh embodiment of the swash plate type compressor of the present invention. The swash plate compressor according to the eleventh embodiment has the same positional relationship as that of the swash plate compressor according to the seventh embodiment described above in the fifth embodiment with respect to the first embodiment. Therefore, the rotation stopping mechanism 44 is similar to that of the ninth embodiment, but the center shaft 45 is not fixed to the cylinder block 2 and its base portion 45b is formed in the axial hole 2b formed in the cylinder block 2. A key or spline (not shown) or a serration or the like (not shown) is inserted therein so as to be slidable only in the axial direction, and is biased in the axial direction by a compression spring 37. As a result, the position of the head portion 45a of the center shaft 45 becomes movable in the axial direction, the wobble plate 6 and the drive plate 5 also move, and the inclination angle changes, so that the swash plate compressor of the eleventh embodiment is It is a variable capacitance type.

The swash plate type compressor according to the twelfth embodiment of the present invention which can be described with reference to FIG. 16 also corresponds to the sixth embodiment (see FIG. 8). Since the detent mechanism is the same as the detent mechanism 44 of the ninth embodiment,
The swash plate type compressor according to the twelfth embodiment has the same structure and operational effects as the sixth embodiment.
It can be easily inferred from the description of the embodiment and the description of the ninth embodiment.

17 to 19 show a thirteenth embodiment of the swash plate type compressor of the present invention. Each of the thirteenth to eighteenth embodiments is the third embodiment described above,
A typical one among them is the thirteenth embodiment. The examples belonging to the third group each include four spherical shoes, two of which are restrained in the rotational direction.

The characteristics of the thirteenth embodiment are enlarged and shown in FIG.
The rotation stopping mechanism 48 has a structure as shown in FIG. The rotation stopping mechanism 48 has a pair of spherical shoes 52 having a square cross section and slidably contacting the upper and lower surfaces of the cantilevered center shaft 9. As will be apparent by also referring to (c) of FIG. 19, the spherical surface formed on the outer surfaces of the upper and lower spherical shoes 52 has an intersection point of the axis XX and the axis YY shown in (a) of FIG. Is the center. This spherical shoe 52
As shown as a broken circle in (f) of FIG. 19 and the like, the planar shape is a circle centered on the axis Y-Y. A state in which an outer ring 49 having a spherical inner surface having substantially the same radius as the outer spherical surface of the spherical shoe 52 and slidably contacting the spherical shoe 52 is integrated with the wobble plate 6. And supports the drive plate 5 via the thrust bearing 13.

As is apparent from FIGS. 19A and 19F, the left and right inner surfaces of the outer ring 49 also have the axis Y.
It is a spherical surface centered on the intersection of -Y and axis XX,
On the other hand, a pair of spherical shoes 50 each having a slidable spherical surface are axially slidably inserted in the center shaft 9 between the left and right outer surfaces of the center shaft 9 having a square cross section. . This allows the outer ring 49 to rotate about the axis Y-Y by the left and right spherical shoes 50. This rotation is also allowed on the spherical surface S between the spherical shoe 52 and the outer ring 49 described above. The rotation of the outer ring 49 about the axis XX also applies to the same spherical shoe 52 and outer ring 4
Since it is allowed by the spherical surface S between 9 and 9, it is not necessary for the left and right spherical shoes 50 to participate in this rotation, and it is necessary to prevent the outer ring 49 from rotating around the center shaft 9. 49
Four pins 51 are driven in.

Since the detent mechanism 48 in the thirteenth embodiment is constructed in this way, the outer ring 49 rotates around the axis X--X and the axis Y--Y with respect to the center shaft 9 by the upper and lower spherical shoes 52. And the left and right spherical shoes 50 also permit such rotation of the outer ring 49, and the spherical shoe 5
Since 0 and 52 can both freely slide on the center shaft 9 in the plane P of the inner surface, the outer ring 49 and the wobble plate 6 and the drive plate 5 carried by the outer ring 49 do not rotate. The direction can be freely changed on the center shaft 9 within a predetermined angle range.

Therefore, the swash plate compressor of the thirteenth embodiment is
Since it is possible to obtain substantially the same operational effects as the swash plate type compressor and the like of the above-described first embodiment, detailed description overlapping with the first embodiment and the like will be omitted here.

FIG. 20 shows a fourteenth embodiment of the swash plate type compressor according to the present invention. The feature of the 14th embodiment is that the cantilevered center shaft 9 of the swash plate type compressor of the 13th embodiment is used.
The point is that the rotation stopping mechanism 48 is replaced with the center shaft 30 supporting both ends. Therefore, the 14th
Since the embodiment can achieve the same effects as those of the second embodiment shown in FIG. 4, duplicated detailed description will be omitted here.

21 and 22 show a swash plate type compressor according to a fifteenth embodiment of the present invention. The feature of the fifteenth embodiment is that the thirteenth feature
In the detent mechanism 48 of the embodiment, instead of the center shaft 9, the cantilever type center shaft 32 having a partially spherical head 32a is used as in the third embodiment shown in FIGS. 5 and 6. Is the point that was used. The first
Also in the case of the fifth embodiment, in order to insert the center shaft 32 having a head into the outer ring 54 of the rotation stopping mechanism 53, an axial groove is formed in a part of the upper and lower inner surfaces of the outer ring 54. It is necessary to mount the spherical shoe 34 having the shape shown in FIG. 6 for the third embodiment in the groove.

Since the swash plate type compressor of the fifteenth embodiment is provided with the detent mechanism 53 having such a structure, it is substantially the same as the third embodiment described with reference to FIGS. 5 and 6. A similar effect is obtained. Since the fixed center shaft 32 has a head, the swash plate type compressor of the fifteenth embodiment is of a fixed capacity type.

FIG. 23 shows a sixteenth embodiment of the swash plate type compressor of the present invention. The swash plate compressor according to the sixteenth embodiment is characterized in that the center shaft 32 having a cantilevered head in the swash plate compressor according to the fifteenth embodiment is used in the fourth embodiment (see FIG. 7). As in the case of (1), it is replaced with a center shaft 36 having both ends and a head at the center.
The structure of the rotation stopping mechanism 53 itself is the same as that of the fifteenth embodiment. Since it has such a configuration,
The swash plate type compressor of the embodiment has substantially the same operational effects as the swash plate type compressor of the fourth embodiment.

FIG. 24 shows a seventeenth embodiment of the swash plate type compressor according to the present invention. The seventeenth embodiment corresponds to the above-mentioned fifth embodiment (see FIG. 8), and is characterized in that the base portion 32b of the center shaft 32 having a head is formed in the cylinder block 2 in the axial direction. The center shaft 3 is inserted into the hole 2b so as to be slidable only in the axial direction by a key or spline (not shown) or by means such as serration.
The point is that 2 can be expanded and contracted. The rotation stopping mechanism 53 itself is the same as that of the above-mentioned fifteenth embodiment. Therefore, the swash plate type compressor of the seventeenth embodiment has the same effects as those of the fifth embodiment.

Finally, the swash plate type compressor of the eighteenth embodiment of the present invention can be described with reference to FIG. 24, which is the same as that of the seventeenth embodiment. The eighteenth embodiment corresponds to the above-described sixth embodiment, in which a control pressure chamber 38 for axially pressing the base portion 32b of the center shaft 32 is provided, and a control pressure of any height from the control valve 25 is provided therein. Is supplied to change the inclination angle of the drive plate 5 and the wobble plate 6 to change the discharge capacity of the compressor steplessly. Therefore, the swash plate type compressor of the eighteenth embodiment has substantially the same effects as the swash plate type compressor of the sixth embodiment.

[Brief description of drawings]

FIG. 1 is a vertical sectional front view showing a first embodiment of a swash plate type compressor of the present invention.

FIG. 2 is a vertical sectional front view showing another operating state of the first embodiment shown in FIG.

3 (a) to 3 (g) are diagrams showing the structure and operation of a rotation stop mechanism, which is the main part of the swash plate compressor of the first embodiment, and FIG. Each of the drawings (b) to (d) is a vertical sectional front view in a different operating state, and each drawing (e) to (g) is a vertical sectional plan view in a different operating state.

FIG. 4 is a vertical sectional front view showing a second embodiment of the swash plate compressor of the present invention.

FIG. 5 is a vertical sectional front view showing a third embodiment of the swash plate type compressor of the present invention.

6 (a) to 6 (g) are views showing the structure and operation of a rotation stopping mechanism which is an essential part of the swash plate type compressor of the third embodiment, and FIG. Each of the drawings (b) to (d) is a vertical sectional front view in a different operating state, and each drawing (e) to (g) is a vertical sectional plan view in a different operating state.

FIG. 7 is a vertical cross-sectional front view showing a fourth embodiment of the swash plate type compressor of the present invention.

FIG. 8 is a vertical sectional front view showing a fifth embodiment and a sixth embodiment of the swash plate type compressor of the present invention.

FIG. 9 is a vertical sectional front view showing a seventh embodiment of the swash plate type compressor of the present invention.

FIG. 10 is a vertical sectional front view showing another operating state of the seventh embodiment shown in FIG.

11 (a) to 11 (g) each show the structure and operation of a rotation stop mechanism that is a main part of the swash plate compressor of the seventh embodiment, and FIG. Each of the drawings (b) to (d) is a vertical sectional front view in a different operating state, and each drawing (e) to (g) is a vertical sectional plan view in a different operating state.

FIG. 12 is a vertical sectional front view showing an eighth embodiment of the swash plate compressor of the present invention.

FIG. 13 is a vertical sectional front view showing a ninth embodiment of the swash plate type compressor of the present invention.

14 (a) to (g) show the structure and operation of a rotation stop mechanism, which is the main part of the swash plate compressor of the ninth embodiment, and FIG. 14 (a) is a cross-sectional side view, Each of the drawings (b) to (d) is a vertical sectional front view in a different operating state, and each drawing (e) to (g) is a vertical sectional plan view in a different operating state.

FIG. 15 is a vertical sectional front view showing a tenth embodiment of the swash plate type compressor of the present invention.

FIG. 16 is a vertical sectional front view showing an eleventh embodiment and a twelfth embodiment of the swash plate compressor of the present invention.

FIG. 17 is a vertical sectional front view showing a thirteenth embodiment of the swash plate type compressor of the present invention.

FIG. 18 is a vertical sectional front view showing another operating state of the thirteenth embodiment shown in FIG. 17.

19 (a) to (g) show the structure and operation of a rotation stop mechanism, which is the main part of the swash plate compressor of the thirteenth embodiment, and FIG. 19 (a) is a cross-sectional side view, Each of the drawings (b) to (d) is a vertical sectional front view in a different operating state, and each drawing (e) to (g) is a vertical sectional plan view in a different operating state.

FIG. 20 is a vertical sectional front view showing a fourteenth embodiment of the swash plate compressor of the present invention.

FIG. 21 is a vertical sectional front view showing a fifteenth embodiment of the swash plate compressor of the present invention.

22 (a) to (g) show the structure and operation of a rotation stop mechanism, which is an essential part of the swash plate compressor of the fifteenth embodiment, and FIG. Each of the drawings (b) to (d) is a vertical sectional front view in a different operating state, and each drawing (e) to (g) is a vertical sectional plan view in a different operating state.

FIG. 23 is a vertical cross-sectional front view showing a sixteenth embodiment of the swash plate compressor of the present invention.

FIG. 24 is a vertical sectional front view showing a seventeenth embodiment and an eighteenth embodiment of the swash plate compressor of the present invention.

[Explanation of symbols]

1 ... Front housing 2 ... Cylinder block 4 ... Main shaft 5 ... Drive plate 6 ... Wobble plate 7 ... Piston 9, 30, 32, 36, 45, 47 ... Center shaft 10, 35, 41, 49, 54 ... Outer ring 11, 40, 43, 46 ... Cylindrical shoe 12, 34, 50, 52 ... Spherical shoe 13 ... Thrust bearing 25 ... Control valve 28, 38 ... Control pressure chamber 29, 33, 39, 44, 48, 53 ... Detent mechanism 31 ... Radial bearing 41 ... Inner ring 51 ... pin

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Motohiko Ueda             1-1, Showa-cho, Kariya city, Aichi stock market             Inside the company DENSO (72) Inventor Takashi Inoue             14 Iwatani Shimohakaku-cho, Nishio-shi, Aichi Stock Association             Company Japan Auto Parts Research Institute (72) Inventor Mitsuo Matsuda             14 Iwatani Shimohakaku-cho, Nishio-shi, Aichi Stock Association             Company Japan Auto Parts Research Institute F term (reference) 3H045 AA04 AA12 AA27 BA19 CA03                       CA13 DA25 EA13                 3H076 AA06 BB33 BB38 BB41 CC20

Claims (10)

[Claims] 1. A main shaft that is supported by a housing through a bearing to receive rotational power from a power source, and a drive that is connected to the main shaft to rotate and can tilt with respect to the main shaft. The plate and the drive plate are supported by the thrust bearing to have the same inclination angle to perform the swinging motion, but the wobble plate that is prevented from the rotating motion and the wobble plate connected to the periphery of the wobble plate to reciprocate. A plurality of pistons that move and are inserted into a cylinder bore to suck and compress a fluid, and a swash plate type compressor that is provided with a rotation stop mechanism to prevent rotational movement of the wobble plate, The anti-rotation mechanism is concentric with the wobble plate, either integrally or separately. The outer ring attached to the outer ring, four pairs of shoes provided as sliding members at different positions on the inner surface of the outer ring, and the inner surfaces of the shoes engaging at different positions. And a center shaft that is provided with different outer surface portions and that is supported by the housing such that the outer surface portions are located at the center of the outer ring and that they do not rotate themselves. A swash plate type compressor characterized by being provided. 2. The mechanism according to claim 1, further comprising a mechanism for changing an inclination angle of the drive plate and the wobble plate in order to change a discharge capacity, and a means for controlling the mechanism. A swash plate type compressor. 3. The shoe according to claim 2, wherein a pair of four shoes is provided as a part of the mechanism for changing the inclination angles of the drive plate and the wobble plate,
A swash plate type compressor comprising a flat axial sliding surface between the center shaft and the center shaft. 4. The swash plate according to claim 2, wherein the center shaft is configured to be extendable / contractible as a part of the mechanism for changing the inclination angles of the drive plate and the wobble plate. Type compressor. 5. The method according to any one of claims 1 to 4,
A swash plate characterized in that two pairs of the four shoes include a pair of cylindrical shoes having a cylindrical surface formed on the outer surface or the inner surface and a pair of spherical shoes having a spherical surface formed on the outer surface or the inner surface. Type compressor. 6. The method according to any one of claims 1 to 4,
2. A swash plate type compressor, characterized in that two pairs of the four shoes are all cylindrical shoes having a cylindrical surface on an outer surface or an inner surface. 7. The method according to any one of claims 1 to 4,
A swash plate type compressor characterized in that four shoes in two pairs are spherical shoes each having a spherical surface formed on an outer surface or an inner surface. 8. The method according to claim 1, wherein
A swash plate type compressor, wherein the center shaft is supported in a cantilevered manner at its base end. 9. The method according to claim 1, wherein
A swash plate compressor in which the center shaft is supported at both ends. 10. The swash plate compressor according to claim 9, wherein the tip of the center shaft is intermediately supported by the main shaft via a bearing.