JPH0472071B2 - - Google Patents

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a refrigerant compressor for an automobile air conditioner, and in particular, a variable stroke swash plate type compressor suitable for regulating a swash plate tilt angle with excellent durability. Regarding machines.

[Conventional technology]

The structure that regulates the maximum and minimum strokes of conventional variable stroke compressors is described in USP No. 4428718 and S.A.E., Technical, Paper, Series 850040 (1985) Fig. 2, Fig. 4 (SAE,
Technical, Paper Series, 850040 (1985), Figures 2 and 4), the maximum stroke of the compressor is regulated by a sleeve and thrust bearing.

Further, Japanese Patent Application Laid-Open No. 61-215468 discloses that the rotating body and the swinging inclined plate are brought into contact with each other at only one place.

[Problem to be solved by the invention]

In the above conventional technology, when the compressor is operated at maximum stroke (maximum swash plate tilt angle), the axial component of the compression load accompanying gas compression is supported by the sleeve coming into contact with the thrust bearing. . Therefore, the reaction force is received by the three pin that engages the sleeve and the journal. In particular, when used in car air conditioners, etc., liquid refrigerant may be compressed depending on environmental conditions. At this time, the axial component of the compressive load reaches 1 ton, so an excessive load is applied to the sleeve pin and pin hole. When such an excessive load is applied to the pin, the pin hole is deformed, the gap between the pin and the pin hole becomes large, and the tilting function of the swash plate is significantly reduced.

Also, what is disclosed in Japanese Patent Application Laid-open No. 61-215468 is
A moment acts on a line connecting the drive shaft and the engagement portion between the drive plate and the swash plate, but no consideration has been given to providing stable support against this moment.

An object of the present invention is to eliminate the drawbacks of the swash plate tilt angle regulating structure of the variable stroke compressor and provide a variable stroke compressor with excellent durability.

[Means to solve the problem]

In order to achieve the above object, the variable stroke swash plate compressor of the present invention includes a housing having a crank chamber, a suction space, and a discharge space therein, a drive shaft supported by bearings by the housing, and a drive shaft supported by bearings by the housing. a drive plate fixed to the drive plate; a swash plate that is engaged with the drive plate so that the rotational direction of the drive shaft is regulated and that performs a tilting motion that is regulated within a range of a maximum tilt angle and a minimum tilt angle; a piston support that is rotatably supported by a bearing so as to be rotatable relative to the swash plate, is restrained from rotating by a rotation stopper mechanism, and performs a rocking motion corresponding to the inclination angle of the swash plate; A plurality of cylinders arranged in a circumferential direction, a piston reciprocating within each cylinder, and a connecting rod connecting the piston and the piston support,
The device is characterized in that portions for regulating the maximum tilting angle of the tilting motion are provided on both sides of a line connecting the engagement portion between the drive plate and the swash plate and the drive shaft.

[Effect]

With the above-described swash plate tilting angle regulating structure, the drive plate and the swash plate regulate the tilt angle at the maximum swash plate tilt angle, so the sleeve does not come into contact with the drive plate. Therefore, the axial component force accompanying the gas compression load is received by the drive plate and the swash plate, making it possible to avoid supporting the load by the sleeve pin.

In addition, since the restriction is provided on both sides of the line connecting the drive shaft and the engaging portion of the drive plate and swash plate, it is possible to prevent prying due to the moment exerted by the compressive load and stabilize the operation of the sleeve. can be kept.

〔Example〕

An embodiment of the present invention will be described below with reference to FIGS. 1 to 6. Figures 1 and 2 show the overall structure of the variable stroke swash plate compressor according to this embodiment. Figure 1 shows the state when the piston stroke is at its maximum, that is, the swash plate tilt angle is at its maximum. FIG. 2 shows the state of the minimum swash plate tilt angle. FIG. 3 is a sectional view taken along line I-I in FIGS. 1 and 2. A main shaft 13 is rotatably mounted at one end of the cylindrical cylinder block 2 via a radial needle roller bearing 18 in the center. A supporting front housing 1 is arranged and fixed to a swash plate chamber 10.
is formed. The cylinder block 2 includes a plurality of cylinders 3 arranged circumferentially around the main shaft 13 and parallel to the axis of the main shaft 13.
3 is formed. The main shaft 13 is located approximately on the center line of the cylinder block 2, and is rotatably supported by radial needle roller bearings 18 and 19 provided at the center of the cylinder block 2 and the front housing 1, and is press-fitted, pin 11, or The drive plate 14 is fixed by plastic bonding or the like. The drive plate 14 has a cam groove 1
42, and in the groove 142, the swash plate lug 1 is provided.
Pivot pin 1 fitted with a gap at 21
6 is movably attached. Further, the drive plate lug 141 provided with the cam groove 142 and the swash plate lug 121 are structured so that their sides come into contact with each other. As a result, when the drive plate 14 rotates due to the rotation of the main shaft 13,
Rotational force is applied from the ears 141 on the drive plate 14 to the swash plate ears 121, causing the swash plate 12 to rotate. A sleeve 15 is incorporated into the main shaft 13 so as to be slidable in the axial direction with respect to the main shaft 13. The sleeve 15 and the swash plate 12 are connected to each other by a sleeve pin 17. It is rotatably fastened around the Therefore, as the main shaft 13 rotates, the drive plate 14, swash plate 12, and sleeve 15 rotate together. A piston support 21 is fastened to the swash plate 12 via a ball bearing 23.
A spacer 221 and a retaining ring 22 fixed to the swash plate 12 allow the ball bearing 23 to be attached to the swash plate 12.
The hub part 1 of the swash plate is
It is fixed at 22.

On the other hand, the piston support 21 is restricted from moving in the right direction in FIGS.
Therefore, movement to the left in both figures is also restricted. Also, at the lower position of the piston support 21,
A support pin 26 is fixed in the radial direction by a method such as press fitting, screwing, or plastic coupling, and a slide ball 2 is attached to the support pin 26.
7. A pair of semi-cylindrical slide shoes 29 having spherical portions that come into contact with the slide balls are rotatably and slidably mounted. Further, the slide shoe 29 reciprocates in an axial groove 28 provided on the inner circumference of the front housing 1, and restricts movement around the axis so that the piston support 21 does not rotate around the main shaft 13. ing. The piston support 21 has balls 321 and 32 at both ends.
One end of a plurality of connecting rods 32 having the number 2 is rotatably attached around the center of the ball 321, and the piston 31 is attached to the other end so as to be rotatable around the center of the ball 322. The plurality of pistons 31 are assembled into a plurality of cylinders 33 provided in the cylinder block 2. Piston rings 34 and 35 are attached to the piston 31. The cylinder block 2 also includes a suction valve plate 5, a cylinder head 4,
The bolts 36a to 3 are integrated with the front housing 1, in which the discharge valve plate 6, the gasket 7, and the rear cover 3 are arranged, and are arranged so as to surround the drive plate 14, the swash plate 12, the piston support 21, etc.
6f etc., the front housing 1 and cylinder block 2 are airtight with an O ring 38, and the rear cover 3 and cylinder block 2 are sealed with an O ring 38.
It is kept airtight with ring 39. The cylinder head 4 is provided with a suction support 401 and a discharge port 402 corresponding to each cylinder 33, which communicate with a suction chamber 8 and a discharge chamber 9 provided in the rear cover 3, respectively. The rear cover 3 has an inlet 301
and a discharge port (not shown) are provided, and the suction passage 30
2, a control valve 41 is provided between the suction port 301 and the suction chamber 8. The upstream side of the control valve 41;
The interior of the front housing 1 and the swash plate chamber 10 are connected to through holes 303, 703, 603, 403 and 503 provided at the center of the rear cover 3, packing 7, discharge valve plate 6, cylinder head 4, and suction valve plate 5.
A passage 131 provided at the center of the main shaft 13 and a passage 143 connected to the passage 131 and opening in the drive plate 14 in the radial direction communicate with each other. Further, the downstream side of the control valve 41 communicates with the suction chamber 8 . The cam groove 142 formed in the drive plate 14 is a closed curve such that the top dead center position of the piston 31 does not change even if the pivot pin 16 moves within the cam groove 142.

With the configuration described above, when the main shaft 13 of the compressor is driven by the engine (not shown), the drive plate 14 and the swash plate 12 rotate, and the piston support 2 is rotated relative to the rotation axis of the main shaft 13.
1 makes a rocking motion. Therefore, as the piston 31 reciprocates within the cylinder, the refrigerant returned from the refrigeration cycle (not shown) flows into the suction port 301 and is controlled to an appropriate pressure by the control valve 41. Afterwards, it is introduced into the suction chamber formed in the rear cover 3, and is introduced into the suction port 40 of the cylinder head 4.
1. It flows into the cylinder through the suction valve plate 5 and completes the suction stroke. The refrigerant compressed by the piston 31 is discharged from the discharge port 402 of the cylinder head 4;
It is discharged through the discharge valve plate 6 into a discharge chamber 9 formed in the rear cover 3, and is discharged from a discharge port (not shown) into a refrigeration cycle (not shown).

Next, a mechanism for regulating the tilting angle of the swash plate will be described. As shown in FIG. 1, during the process in which the swash plate tilt angle moves from small to large, the sleeve 15 slides on the main shaft 13 from right to left in the same figure, and the swash plate 12 is tilted clockwise around the sleeve pin 17. and,
When the swash plate tilt angle reaches the maximum (the piston stroke is maximum), the cam groove 1 of the drive plate 14
42 , a conical surface 144 (tilting angle regulating section) formed on the opposite side to the center of the main shaft 13 , and a swash plate 12 .
The conical surface 124 (tilt angle regulating section) formed in the contact surface 124 contacts the conical surface 124 (tilt angle regulating section) formed in the conical surface 124 (tilt angle regulating section). At this time, appropriate gaps are provided between the sleeve 15 and the drive plate, and between the upper part of the pivot pin 16 and the cam groove, thereby avoiding collision between the respective members. Furthermore, when the swash plate tilt angle is minimum (the piston stroke is minimum), as shown in FIG. 2, the thrust washer 201 fixed to the bearing housing 21 of the cylinder block 2,
By bringing the tip of the sleeve 15 into contact with a thrust washer 202 that slides relative to the thrust washer 201, the position of the minimum stroke is regulated. The thrust force acting on the main shaft 13 when compressing gas is the thrust bearing 42 installed between the drive plate 14 and the front housing 1, and the radial force acting on the main shaft 13 is generated by the front housing 1 and the cylinder block 2. It is supported by two radial needle roller bearings 19 and 18 provided within the bearing housing 21.

When configured as described above, the compressive load is supported on the side opposite to the pivot pin with respect to the centerline of the main shaft, so there is an effect that the load acting on the pivot pin can be reduced.

Next, a case in which the maximum swash plate tilt angle is regulated at two locations, which is a main feature of the present invention, will be explained with reference to FIGS. 4, 5, and 6. FIG. 4b shows a front view of the drive plate, and FIG. 4a shows a side view. Figure 5a
1 shows a front view of the swash plate, and b shows a sectional view taken along the line a. Moreover, FIG. 6 shows a partial sectional view when both are combined. Drive plate 14
The center of the width across flats of the ear portion 141 is offset from the axial center of the drive plate (the same applies to the embodiments described above). In order to regulate the maximum tilt angle, the tilt regulating portions 145 are placed at positions symmetrical to the main axis (that is, on both sides of the line connecting the engagement portion between the drive plate and the swash plate and the drive shaft).
It has been installed in several places. Therefore, the tilting restriction section 14
The tilt angle of 5 is the maximum swash plate tilt angle of the compressor, that is, the maximum stroke position. On the other hand, swash plate 1
Similarly to the drive plate 14, 2 also has a swash plate lug 1.
The center between the contact surfaces of the ears 141 of the drive plate 14 of 21 is offset from the axis center (the same applies to the embodiments described above). The swash plate 12 has two tilting regulating portions 125 axially symmetrical so as to come into contact with the tilting regulating portion 145 of the drive plate 14.
It is formed in several places. Therefore, when the piston stroke of the compressor is at its maximum, the tilt restricting portion 145 of the drive plate 14 and the tilt restricting portion 125 of the swash plate 12 come into contact. At this time, the conical surface 14 of the drive plate 14 and the swash plate 12
4 and 124, and between the sleeve 15 and the drive plate 14, the respective members will not collide.

According to this embodiment, since the maximum swash plate tilting angle can be regulated at two locations, there is an effect that the load acting on the pivot pin can be further reduced.

7, 8 and 9 show other embodiments of the present invention. Figure 7 shows drive plate 1
Figure 8a shows the front and side views of the swash plate 1.
Fig. 9 is a front view of Fig. 2, b is a sectional view taken along the - line of Fig. 9, and Fig. 9 is a partial sectional view when the two are combined. Swash plate 12
At the center of the sleeve 15, a tilting restriction portion 126 having a width across flats is provided to engage with the sleeve 15 and extends to the left with respect to the sleeve pin hole, as shown in FIG. 8b. . On the other hand, drive plate 1
On the conical surface 144 of No. 4, a tilting restricting portion 146 having a width across flats slightly wider than the width across flats of the tilting restricting portion 126 formed on the swash plate 12 is provided symmetrically with respect to the axial center line of the main shaft. It is provided. Therefore, when the piston is operated at its maximum stroke, the tilting restricting portion 146 of the drive plate 14 and the tilting restricting portion 126 of the swash plate 12 come into contact with each other.

According to this embodiment, the maximum swash plate tilting angle can be regulated at two locations, and the tilting can be regulated without adding extra buildup to the drive plate and swash plate.

〔Effect of the invention〕

As described above, according to the present invention, in the swash plate tilt angle regulating structure, contact between the drive plate and the sleeve is avoided, and the tilt angle between the drive plate and the swash plate is controlled. By restricting the sleeve pin with the restricting parts provided on both sides of the line connecting the engaging part and the drive shaft, the load acting on the sleeve pin can be significantly reduced, and the moment acting on the sleeve pin can be supported at two locations. By doing so, the operation of the sleeve can be maintained stably, and a variable stroke swash plate compressor with excellent durability can be provided.

[Brief explanation of drawings]

1 and 2 are structural diagrams of a variable stroke swash plate compressor showing an embodiment of the present invention, and FIG.
Fig. 4 is a side view of the drive plate, Fig. 4b is a front view thereof,
FIG. 5a is a front view of the swash plate, FIG. 5b is a sectional view taken along the line -- in FIG. 9th
The figures show other embodiments of the present invention, FIG. 7a is a side view of the drive plate, FIG. 7b is a front view of the drive plate, FIG. 8a is a front view of the swash plate, and FIG. 8b is a front view of the swash plate. FIG. 8a is a cross-sectional view taken along the line -2, and FIG. 9 is a partial cross-sectional view of the drive plate assembled with the swash plate. 1...Front housing, 2...Cylinder block, 3...Rear cover, 12...Swash plate, 13...
... Main shaft, 14 ... Drive plate, 15 ... Sleeve, 16 ... Pivot pin, 17 ... Sleeve pin, 21 ... Piston support, 31 ... Piston, 32 ... Connecting rod, 33 ...
...Cylinder, 124, 125, 126... Swash plate tilting regulating section, 144, 145, 146... Drive plate tilting regulating section.

Claims (1)

[Claims] 1. A housing having a crank chamber, a suction space, and a discharge space inside, a drive shaft supported by bearings by the housing, a drive plate fixed to the drive shaft, and a drive plate fixed to the drive plate. A swash plate that is engaged with the drive shaft in a regulated rotational direction and that performs a tilting movement that is regulated within a range of a maximum tilt angle and a minimum tilt angle; a piston support that is restrained from rotating by a rotation prevention mechanism and that swings in response to the inclination angle of the swash plate; and a plurality of piston supports that are arranged circumferentially and parallel to the axis of the drive shaft. The device includes a cylinder, a piston that reciprocates within each cylinder, and a connecting rod that connects the piston and the piston support, and a portion that restricts the maximum tilting angle of the tilting motion is connected to the drive plate and the swash plate. A variable stroke swash plate compressor characterized by being provided on both sides of a line connecting a joint and a drive shaft. 2. The variable device according to claim 1, wherein the restriction portion is provided on the drive plate and the swash plate, and maximum tilting is restricted by abutment of the restriction portion. Stroke swash plate compressor. 3. The variable stroke swash plate compressor according to claim 1 or 2, wherein the regulating portion is arranged symmetrically with respect to the main axis of the drive shaft. 4. A patent characterized in that the restriction portion is provided on the outside of a sleeve pin that rotatably fastens the swash plate to a sleeve that is slidably incorporated in the drive shaft in the axial direction. Claim 1
The variable stroke swash plate compressor described in .