JPH10196530A - Lubrication structure of shaft sealing mechanism in swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide the lubrication structure of a shaft sealing mechanism in a swash plate compressor, in which the compressor can be miniaturized by easily machining a communicating passage, and reducing the dimension of the axial direction of a front housing. SOLUTION: A first communicating groove 45 for communicating a suction chamber 29 with a shaft sealing chamber 44, is formed in a partitioning wall 153 arranged in a front housing 15. The shaft sealing chamber 44 and a storage chamber 111 for a bearing 20 are communicated with each other by a second communicating passage 46. The storage chamber 111 and a first suction passage 171 are communicated with each other by a second communicating groove 47 arranged in the front side end surface of a cylinder block. Then, after a part of refrigerant gas introduced to the suction chamber 29 through a fourth suction passage 174 from a swash plate chamber, is introduced from the first communicating groove 45 to the shaft sealing chamber 44, and a shaft sealing mechanism 41 is cooled and lubricated, a part of refrigerant gas is introduced to the first suction passage 171 through a third communicating groove from the second communicating passage 46.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a lubricating structure for a shaft seal mechanism in a swash plate type compressor used in, for example, a vehicle air conditioner.

[0002]

2. Description of the Related Art A conventional swash plate type compressor is disclosed in
Japanese Patent Publication No. 109782 proposes the one disclosed in Japanese Patent Application Laid-Open No. 109782. In this swash plate type compressor, a front housing and a rear housing having a suction chamber defined inside on the outer periphery and a discharge chamber formed inside are jointed and fixed to both front and rear end surfaces of a cylinder block via valve plates, respectively. Further, a double-headed piston is housed in a plurality of cylinder bores formed in the cylinder block,
A drive shaft is inserted into and supported by a center hole of the cylinder block and the front housing via a shaft seal mechanism and a bearing. Further, the swash plate chamber and the suction chamber communicate with each other through a plurality of suction passages formed in a cylinder block. In the swash plate chamber formed in the cylinder block, the swash plate fixed to a drive shaft is rotated to reciprocate the double-headed piston. By moving the gas, the gas is sucked from the suction chamber into the compression chamber in the cylinder bore, and the compressed gas is discharged to the discharge chamber.

[0003] A shaft seal chamber is formed inside the shaft seal mechanism interposed between the inner peripheral surface of the boss portion of the front housing and the drive shaft. The shaft seal chamber and the suction chamber communicate with each other through two communication passages formed obliquely with respect to the front housing. Refrigerant gas in the suction chamber is guided to the shaft seal chamber through one of the communication passages, and the shaft seal mechanism is lubricated. Is done. Further, the refrigerant gas in the shaft seal chamber is led to another suction chamber by the other communication path.

[0004]

However, in the above-mentioned conventional swash plate compressor, it is necessary to form two communication passages obliquely with respect to the front housing by a drill or the like. There is a problem that the cost cannot be reduced. In addition, since the communication passage is inclined in the axial direction of the compressor, the axial dimension of the front housing is restricted, and the front housing cannot be shortened in the axial direction, resulting in an increase in the size of the compressor. There is. Furthermore, the inlet of one of the communication passages that guides the gas to the shaft seal chamber and the outlet of the other communication passage that discharges the gas in the cooled and lubricated shaft seal chamber are both open to the suction chamber. The pressure difference between the inlet and the outlet cannot be increased, which causes a problem that the cooling and lubrication efficiency of the shaft seal mechanism is low.

SUMMARY OF THE INVENTION An object of the present invention is to solve the above-mentioned problems in the prior art, to facilitate the working of the communication passage, to reduce the axial dimension of the front housing, and to reduce the size of the compressor. , And further cooling of the shaft seal mechanism,
An object of the present invention is to provide a lubricating structure of a shaft seal mechanism in a swash plate type compressor capable of improving lubrication efficiency.

[0006]

According to the first aspect of the present invention,
In order to achieve the above object, a front housing and a rear housing having a suction chamber defined inside on the outer periphery and a discharge chamber formed on the outer periphery are respectively joined and fixed to both front and rear end surfaces of the cylinder block via valve plates, and a plurality of cylinders are formed on the cylinder block. A plurality of pistons are accommodated in a cylinder bore, a drive shaft is inserted and supported in a center hole of the cylinder block and the front housing via a shaft seal mechanism and a bearing, and the swash plate chamber and the suction chamber are formed in the cylinder block. In the swash plate chamber formed in the cylinder block, the swash plate fixed to the drive shaft rotates to reciprocate the double-headed piston in the swash plate chamber formed in the cylinder block, thereby sucking gas from the suction chamber into the compression chamber in the cylinder bore. , An oblique structure configured to discharge the compressed gas to the discharge chamber. In the compressor, a first seal is formed in which a shaft seal chamber formed inside a shaft seal mechanism on the front housing side and the suction chamber on the front side are formed at a joint between a rear end surface of the front housing and a valve plate. A second communication passage connects the shaft seal chamber and the front bearing housing chamber supporting the drive shaft through a passage, and further connects the bearing housing chamber and the suction passage to a front end surface of the cylinder block. Means for communicating with each other through a third communication passage formed at the joint between the valve and the valve plate.

According to a second aspect of the present invention, in the first aspect, a communication passage is formed between a partition wall for partitioning the suction chamber and the discharge chamber of the front housing, and a boss portion for partitioning the discharge chamber and the shaft seal chamber. The communication groove formed in the end face of the wall on the valve plate side is the first communication path.

According to a third aspect of the present invention, in the first or second aspect, an annular gap formed between the outer peripheral surface of the drive shaft and the inner periphery of the center hole of the valve plate is used as the second communication path. .

According to a fourth aspect of the present invention, in any one of the first to third aspects, a communication groove formed in a front end surface of the cylinder block or a rear side surface of the valve plate is used as the third communication passage.

According to a fifth aspect of the present invention, in any one of the first to third aspects, a communication groove formed in at least one of a suction valve forming plate and a gasket interposed between a cylinder block and a valve plate, or a front and rear communication groove. The third communication path is formed through the communication path.

According to a sixth aspect of the present invention, in any one of the first to fifth aspects, the first communication passage is formed so as to be substantially orthogonal to the axis of the drive shaft. According to a seventh aspect of the present invention, in any one of the first to sixth aspects, one of the first communication passage and the third communication passage is connected to the suction passage adjacent to an inlet for introducing gas to the swash plate chamber. The other of the first and third communication passages communicates with a corresponding position, and the other of the first and third communication passages communicates with a position corresponding to a suction passage that is not adjacent to the introduction port.

According to an eighth aspect of the present invention, in order to achieve the above-mentioned object, in the seventh aspect, the inlet end of the first communication passage is located at a position farthest from an inlet for introducing gas to the swash plate chamber. The third communication passage is opened at a position corresponding to the passage, and the outlet side end of the third communication passage is opened to the suction passage located closest to the introduction port.

According to a ninth aspect of the present invention, in the second aspect, the discharge chamber communicates with a discharge passage for guiding gas in the discharge chamber to the outside of the apparatus, and the communication passage forming wall is sandwiched by the drive shaft. The discharge passage is formed at a position opposite to the opening position.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to FIGS. As shown in FIG. 1, a pair of front and rear (left and right) cylinder blocks 11,
A valve plate 13, 1 having a suction valve mechanism and a discharge valve mechanism described later
4, the front housing 15 and the rear housing 16 are joined. These cylinder blocks 1
1, 12, valve plates 13 and 14, front housing 15, and rear housing 16 are cylinder block 1.
1 and 12 and one bolt insertion hole 17 (see FIGS. 2 and 3) formed in the valve plates 13 and 14, and tightening bolts respectively penetrating the first to fourth suction passages 171 to 174 which also serve as bolt insertion holes. 18 are joined and fixed to each other.

A drive shaft 19 is rotatably supported in the center holes 111, 121 of the cylinder blocks 11, 12 via a pair of front and rear radial bearings 20, 20. A plurality of cylinder bores 21 are formed in the cylinder blocks 11 and 12 at predetermined intervals. Each cylinder bore 21 accommodates a double-headed piston 22 so as to be able to reciprocate in the front-rear direction. A compression chamber 23 is formed between the end face of the piston 22 of the cylinder bore 21 and the valve plates 13 and 14.

A swash plate chamber 25 is formed in the center of the cylinder blocks 11 and 12, and refrigerant gas is introduced into the swash plate chamber 25 from an inlet 24 (see FIG. 6) provided on the outer periphery of the cylinder block 11. It has become. The swash plate chamber 25 has a swash plate 26 fitted and fixed to the drive shaft 19.
Is accommodated, and the double-headed piston 22 is moored to a swash plate 26 via a shoe 27. A thrust bearing 28 is interposed between the boss portion of the swash plate 26 and the side wall forming the swash plate chamber 25 of the cylinder blocks 11 and 12. When the drive shaft 19 is rotated, the swash plate 26
Is pivotally rotated, and the piston 22 is reciprocated in the front-rear direction within the cylinder bore 21 to perform a compression operation.

As shown in FIG. 1, suction chambers 29 and 30 are provided near the outer periphery of the front and rear housings 15 and 16 by partition walls 151 and 161, and the discharge chamber 3 is provided near the center.
1 and 32 are respectively defined. The suction chamber 2
The swash plate chamber 25 communicates with the swash plate chamber 25 through the first to fourth suction passages 171 to 174, and the discharge chambers 31 and 32 communicate with the valve plates 13 and 14 and the cylinder block 11.
The discharge passage 33 and the outlet 36 (see FIG. 6) formed in the second refrigerant passage 12 communicate with the external refrigerant circuit.

Next, the suction valve mechanism and the discharge valve mechanism mounted on the valve plates 13 and 14 will be described. The valve plates 13, 14 are provided with suction holes 131, 141 corresponding to the cylinder bores 21. The valve plates 13 and 14 are formed with discharge holes 132 and 142 for discharging the compressed refrigerant gas corresponding to the respective cylinder bores 21 to the discharge chambers 31 and 32.
The cylinder blocks 11 and 12 and the valve plate 1
The suction valve forming plate 34 is interposed between the suction valves 3 and 14, and the plurality of suction valves 341 open and close the suction holes 131 and 141. The suction valve forming plate 34 and the cylinder block 1
A gasket 35 is interposed between the joining surfaces of the gaskets 1 and 12.

As shown in FIG. 5, the bolt insertion hole 17 and the first
The fourth to fourth suction passages 171 to 174 and the discharge passage 33 are formed, and the gasket 35 is formed with a hole 351 having the same shape as the hole 342 formed in the suction valve forming plate 34 for allowing opening and closing of the suction valve 341. .

A discharge valve forming plate 37 is interposed between the valve plates 13 and 14 and the front and rear housings 15 and 16, and the discharge valve 371 is connected to the discharge port 13.
2, 142 are opened and closed. The valve plates 13 and 14
A retainer forming plate 38 also serving as a gasket is interposed between the front and rear housings 15 and 16. The retainer forming plate 38 has an outer peripheral seal ring portion 381 for sealing the outer periphery of the suction chamber 29 and a seal ring portion 382 for the partition 151 of the front housing 15.
And the discharge valve 3 connected to the inside of the ring portion 382.
And a retainer 383 that regulates the open position of the shutter 71.

As shown in FIGS.
A shaft seal mechanism 41 is accommodated between the outer peripheral surface of the boss portion 152 and the inner peripheral surface of the boss 152 integrally formed with the front housing 15. A snap ring 42 is fitted on the outer end side of the seal mechanism 41, and the position of the shaft seal mechanism 41 is regulated by a stop ring 43. A shaft seal chamber 44 for supplying a refrigerant gas to the shaft seal mechanism 41 is formed at an inner end of the boss 152.

As shown in FIG. 5, a communication passage forming wall 153 is integrally formed between the partition 151 of the front housing 15 and the boss 152. A first communication passage 4 for communicating the suction chamber 29 and the shaft seal chamber 44 is provided on an end surface of the communication passage forming wall 153 on the valve plate side.
5 are formed. This first
The communication passage 45 is formed between the bottom of the suction chamber 29 and the shaft seal chamber 44.
The lower end inlet is formed in the up-down direction so as to communicate with the bottom of the fourth suction passage 1 which is located farthest from the introduction port 24 among the first to fourth suction passages 171 to 174.
74 are provided. The first communication passage 45 is formed so as to be orthogonal to the axis of the drive shaft 19.

As shown in FIG. 1, a center hole 11 of a cylinder block 11 for accommodating the radial bearing 20 is provided.
1, that is, the housing chamber 111 of the bearing 20 is communicated with the shaft seal chamber 44 through the second communication passage 46. The second communication passage 46 has a central hole 133 formed in the valve plate 13, the suction valve forming plate 34, the gasket 35, the discharge valve forming plate 37, and the retainer forming plate 38, respectively.
343, 352, 384 and the outer peripheral surface of the drive shaft 19.

As shown in FIGS. 4 and 5, the front side end surface of the cylinder block 11
11 (second communication passage 46) and first to fourth suction passages 171
To 174, a communication groove 112 which forms a third communication passage 47 for communicating with the first suction passage 171 located closest to the introduction port 24 is formed.

The radial bearing 20 is composed of a cylindrical race 201 press-fitted into the storage chamber 111 of the cylinder block 11, and a number of needles 202 held inside the race 201 by a retainer (not shown). I have. The end of the third communication groove 47 on the side of the accommodation chamber 111 is communicated with the accommodation chamber 111 and the second communication passage 46 by a recess 203 formed by cutting out a part of the race 201.

Next, the operation of the swash plate type compressor constructed as described above will be described. Now, when the swash plate 26 is rotated by the rotation of the drive shaft 19, each piston 22 reciprocates in the cylinder bore 21 in the front-rear direction via the shoe 27.
The refrigerant gas introduced into the swash plate chamber 25 from the inlet 24 by the reciprocating motion of the piston 22 is supplied from the swash plate chamber 25 to the first to fourth suction passages 1 formed in the cylinder blocks 11 and 12.
It is guided to the suction chambers 29 and 30 through 71 to 174. The refrigerant gas in the suction chambers 29 and 30 is supplied to the valve plate 1
The suction valve 3 is provided through suction ports 131 and 141 formed in the suction ports 3 and 14, respectively.
41 is pushed open to be sucked into the compression chamber 23 in the cylinder bore 21. The compressed gas pushes and opens the discharge valve 371 from the discharge ports 132 and 142 and is discharged to the discharge chambers 31 and 32. Further, the refrigerant gas discharged into the discharge chambers 31 and 32 is pressure-fed to the external refrigerant circuit from the outlet 36 via the discharge passage 33, and is sent to, for example, an evaporator of a vehicle air conditioner to be used for indoor air conditioning. .

A plurality of suction passages 171 to 174 formed in the cylinder block 11 as shown in FIG.
Are located at different positions from each other. When the refrigerant gas is introduced into the swash plate chamber 25 from the inlet 24,
This refrigerant gas moves as shown by the arrows in FIG. At this time, the gas flow is difficult to flow to the first suction passage 171 located closest to the introduction port 24 due to its straightness, and the supply to the fourth suction passage 174 located farthest increases. The reason for this is that the gas that has reached the fourth suction passage 174 after traveling straight has hit the inner peripheral surface of the swash plate chamber 25 and is deflected toward the fourth suction passage 174.
This is due to the difference in the flow rate flowing in the circumferential direction along the inner wall of the. Note that the second and third suction passages 172 and 173 have a flow rate smaller than the inflow amount into the fourth suction passage 174, and
It is larger than the suction passage 171. In particular, when the compressor is operated at a high speed, the flow rate of the refrigerant gas introduced from the inlet 24 increases, and such a tendency becomes remarkable. For this reason, since the pressure of the fourth suction passage 174 is higher than the pressure of the first suction passage 171, the shaft seal chamber 44 and the second
Through the communication passage 46, a flow path of the refrigerant gas to the third communication groove 47 provided corresponding to the first suction passage 171 is formed, and the cooling and lubrication of the shaft seal mechanism 41 in the shaft seal chamber 44 is reliably performed. Will be Then, the flow rate flowing from the first communication path 45 to the third communication path 47 via the second communication path 46 increases as the high-speed operation requires more lubrication.

As described above, since the first communication passage 45 is formed so as to be orthogonal to the axis of the drive shaft 19, the refrigerant gas is supplied to be orthogonal to the drive shaft 19. Therefore, the refrigerant gas is diverted and diffused in the front-back direction in the shaft seal chamber 44, and the shaft seal mechanism 4
1 is efficiently performed. The refrigerant gas which has been cooled and lubricated by the seal mechanism 41 is guided to the storage chamber 111 of the radial bearing 20 through the second communication passage 46, and after cooling and lubricating the bearing 20, passes through the third communication passage 47 to the first communication passage 47. It is guided to the suction passage 171.

Next, the operation and effect obtained by the configuration of this embodiment will be described. In the above embodiment, the shaft seal chamber 44 and the suction chamber 2
A first communication passage 45 that communicates with the valve housing 9 is formed at a joint between the front housing 15 and the valve plate 13. Therefore, the first communication passage 45 can be easily processed, and the axial dimension of the front housing 15 can be reduced as compared with the conventional configuration in which the first communication passage 45 is formed to be inclined. It is possible to reduce the size and weight of the compressor.

In the above-described embodiment, since the direction in which the first communication passage 45 is formed is perpendicular to the axis of the drive shaft 19, the refrigerant gas flowing from the suction chamber 29 into the shaft seal chamber 44 is perpendicular to the drive shaft 19. As described above, the flow can be divided and diffused in the front-rear direction by the collision, so that the cooling and lubrication of the shaft seal mechanism 41 can be efficiently performed.

In the embodiment, the first communication path 4
5 is a communication passage forming wall 1 provided in the front housing 15.
Since it is formed by the communication groove 154 formed on the rear end face of the rear member 53, the processing can be easily performed as compared with the conventional example in which the communication path is inclined by a drill.

In the above embodiment, the shaft seal chamber 4
Second communication path 4 that communicates with the bearing housing chamber 111
6 is formed by the gap between the outer periphery of the drive shaft 19 and the center hole 131 of the valve plate 13, there is no need to form a dedicated communication path, and the processing of the second communication path 46 is facilitated.

In the above embodiment, the third communication passage 47 that connects the bearing housing chamber 111 and the first suction passage 171 is formed at the joint between the valve plate 13 and the cylinder block 11. For this reason, the front housing 1
The third communication path 47 can be easily processed as compared with the conventional example in which the communication path inclined to 5 is formed by a drill. Further, the axial dimension of the front housing 15 can be reduced, and the compressor can be reduced in size and weight.

In the above embodiment, the third communication passage 47 is
A communication groove 1 formed so as to pass through a space between the cylinder bores 21 with respect to an end surface of the cylinder block 11 on the valve plate side.
Since it is 12, the processing can be easily performed.

In the above embodiment, the inlet of the first communication passage 45 on the suction chamber 29 side is located at a position farthest from the introduction port 24 and opens at a position corresponding to the fourth suction passage 174 having a high pressure. The outlet of the third communication passage 47 is located at a position closest to the introduction port 24 and opens to the first suction passage 171 having a low pressure. Therefore, the fourth suction passage 174, the suction chamber 2
9. The shaft seal mechanism in the shaft seal chamber 44 by positively generating a gas flow reaching the first communication path 45, the shaft seal chamber 44, the second communication path 46, the third communication path 47, and the first suction path 171. The cooling and lubricating action of 41 can be performed reliably.

In the above embodiment, the discharge chamber 31 communicates with the discharge passage 33 for guiding the gas in the discharge chamber to the outside of the apparatus.
The communication passage forming wall 153 is formed at a position opposite to the opening position of the discharge passage 33 with the drive shaft 19 interposed therebetween. Therefore, the discharge passage 31 is formed by the communication passage forming wall 153.
, But does not hinder the flow of the refrigerant gas from each discharge port 132 toward the discharge passage 33.

The above embodiment can be modified as follows. As shown in FIG. 7, the third communication passage 47 of the cylinder block 11 is omitted, and a groove or a groove is formed on a joint surface of any one or a plurality of members of the valve plate 13, the suction valve forming plate 34, and the gasket 35. Forming a penetrating third communication passage 47;

In the above embodiment, the cylinder block 11
As compared with the case where the third communication groove 47 is formed by post-processing, the third communication passage 47 can be simultaneously formed at the time of pressing the light-weight, one-plane valve plate 13, the suction valve forming plate 34, and the gasket 35. Therefore, the processing operation becomes easy.

In the above-described embodiment, the first communication passage 45 is made to be orthogonal to the axis of the drive shaft 19. Alternatively, for example, the first communication passage 45 may be directed in the tangential direction of the shaft 19 so that the gas is supplied to the shaft seal chamber 44. The shaft is rotated inside to improve the cooling / lubricating effect of the shaft seal mechanism 41, or is set to an arbitrary directional angle.

The suction passage 17 located at a position adjacent to the inlet 24 for guiding the refrigerant gas to the swash plate chamber 25 through the first communication passage 45.
1 and the third communication passage 47 is connected to the inlet 24.
Communication with the suction passage 174 at a position away from the suction passage.

In the above embodiment, the refrigerant gas flows from the third communication path 47 to the first communication path 45 via the second communication path 46, and the shaft seal mechanism 41 is cooled and lubricated. -The formation positions of the first communication passage 45 and the third communication passage 47 are set corresponding to the same one of the first to fourth suction passages 171 to 174, in addition to the combination described above,
To be set corresponding to the second and third suction passages 172 and 173, or to be set by any other combination.

A communication hole (not shown) is provided in the communication passage forming wall 153 by post-processing so that gas discharged from each discharge port 132 into the discharge chamber 31 can easily flow into the suction passage 33.

The technical ideas other than the claims that can be grasped from the above embodiment will be described below together with their effects. The lubricating structure of a shaft seal mechanism in a swash plate compressor according to any one of claims 1 to 5, wherein the first communication path is directed tangentially to an outer peripheral surface of the drive shaft.

In this swash plate type compressor, the gas swirls in the shaft seal chamber 44 to improve the cooling and lubricating effects of the shaft seal mechanism 41. The lubrication structure of the shaft seal mechanism in the swash plate type compressor according to claim 2, wherein the communication passage forming wall has a communication hole.

In this swash plate type compressor, even when the communication passage forming wall is disposed at a position close to the discharge passage, the flow of gas from each discharge port to the discharge passage can be made smooth and the compression efficiency can be prevented from lowering. it can.

[0046]

As described in detail above, the present invention has the following effects since it has the structure described in the claims.

According to the first aspect of the present invention, the first and third communication passages can be easily formed, the size of the front housing in the axial direction can be reduced, and the compressor can be downsized. The cooling and lubrication efficiency of the mechanism can be improved.

According to the second aspect of the present invention, in addition to the effect of the first aspect, the processing of the first communication passage can be more easily performed. According to the third aspect of the invention, in addition to the effect of the first or second aspect, it is not necessary to separately perform the processing of the second communication path, and the processing is facilitated.

The invention according to claim 4 or 5 is the invention according to claims 1 to 5.
In addition to the effects of the invention described in any one of the third aspect, the processing of the third communication passage can be more easily performed. Claim 6
According to the invention described above, in addition to the effect of the invention according to any one of claims 1 to 5, gas from the first communication passage to the shaft seal chamber is diverted back and forth upon hitting the drive shaft, and thus the shaft seal mechanism is provided. Cooling and lubrication can be performed more efficiently.

According to a seventh aspect of the present invention, in addition to the effects of the first aspect, a pressure difference between the first communication passage and the third communication passage can be increased, and a shaft seal can be provided. By increasing the amount of gas supplied to the chamber, cooling and lubrication of the shaft seal mechanism can be performed more efficiently.

According to the eighth aspect, the effect of the seventh aspect can be further improved. According to the ninth aspect of the present invention, in addition to the effect of the second aspect, the refrigerant gas can be smoothly guided from each discharge port to the discharge passage, and a decrease in compression efficiency can be prevented.

[Brief description of the drawings]

FIG. 1 is a vertical cross-sectional view of a central portion of a swash plate type compressor according to an embodiment of the present invention.

FIG. 2 is a sectional view taken along line II of FIG. 1;

FIG. 3 is a sectional view taken along line II-II of FIG.

FIG. 4 is a partial sectional view taken along the line III-III of FIG. 2;

FIG. 5 is an exploded perspective view of a cylinder block, a front housing, a valve plate, and the like.

FIG. 6 is a cross-sectional view of the swash plate type compressor passing through a swash plate chamber in which a swash plate and a thrust bearing are omitted.

FIG. 7 is an exploded perspective view showing another embodiment of the present invention.

DESCRIPTION OF SYMBOLS 11, 12: Cylinder block, 111: Center hole also serving as bearing housing chamber, 112: Communication groove forming third communication passage 47, 13: Valve plate, 15: Front housing, 151: Partition wall, 152 boss portion, 153 communication wall forming wall, 154 communication groove constituting the first communication passage 45, 171 to 174 first to fourth suction passage, 19 drive shaft, 20 radial bearing, 203 Recess, 21 ... Cylinder bore, 22 ... Double-ended piston, 23 ...
Compression chamber, 25 swash plate chamber, 26 swash plate, 29, 30 suction chamber, 31, 32 discharge chamber, 33 discharge passage, 34 suction valve forming board, 37 discharge valve forming board, 41 shaft seal Mechanism, 44: shaft seal chamber, 45: first communication passage, 4
6: second communication passage, 47: third communication groove.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Yasunori Ueda 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation

Claims (9)

[Claims] A plurality of cylinder bores formed in the cylinder block are fixedly joined to a front housing and a rear housing having a suction chamber formed inside and a discharge chamber formed on the outer periphery of the cylinder block via valve plates on both front and rear end surfaces of the cylinder block. A plurality of suction passages each having a double-ended piston housed therein, a drive shaft inserted and supported through a center hole of the cylinder block and the front housing via a shaft seal mechanism and a bearing, and the swash plate chamber and the suction chamber formed in the cylinder block. In the swash plate chamber formed in the cylinder block, by rotating a swash plate fixed to a drive shaft, the double-headed piston is reciprocated to suck gas from the suction chamber into a compression chamber in a cylinder bore, and to be compressed. Swash plate compressor configured to discharge the discharged gas to the discharge chamber. The shaft seal chamber formed inside the shaft seal mechanism on the front housing side and the suction chamber on the front side are formed by a first communication passage formed at a joint between the rear end surface of the front housing and the valve plate. The shaft seal chamber communicates with a front bearing housing chamber supporting a drive shaft through a second communication passage, and further connects the bearing housing chamber and the suction passage with a front end surface of the cylinder block and a valve. A lubricating structure for a shaft seal mechanism in a swash plate type compressor which is communicated by a third communication passage formed at a joint with a plate. 2. The method according to claim 1, wherein the first communication path includes:
A swash plate type compression which is a communication groove formed in a valve plate side end surface of a communication passage forming wall formed between a partition partitioning a suction chamber and a discharge chamber of the front housing, and a boss portion partitioning the discharge chamber and the shaft seal chamber. Lubrication structure of the shaft seal mechanism in the machine. 3. The swash plate compressor according to claim 1, wherein the second communication passage is an annular gap formed between an outer peripheral surface of the drive shaft and an inner periphery of a center hole of the valve plate. Lubrication structure of shaft seal mechanism. 4. The method according to claim 1, wherein
The lubricating structure of a shaft seal mechanism in a swash plate compressor, wherein the third communication passage is a communication groove formed in a front end surface of a cylinder block or a rear side surface of a valve plate. 5. The method according to claim 1, wherein:
A shaft seal mechanism in a swash plate type compressor, wherein the third communication passage is a communication groove formed in at least one of a suction valve forming plate and a gasket interposed between a cylinder block and a valve plate, or a communication passage formed through the front and rear. Lubrication structure. 6. The method according to claim 1, wherein:
A lubricating structure for a shaft seal mechanism in a swash plate type compressor, wherein the first communication passage is formed to be substantially orthogonal to an axis of a drive shaft. 7. The method according to claim 1, wherein
One of the first communication passage and the third communication passage communicates with a position corresponding to the suction passage adjacent to an inlet for introducing gas to the swash plate chamber, and the other of the first communication passage and the third communication passage. Is a lubricating structure of a shaft seal mechanism in a swash plate compressor which is communicated with a position corresponding to a suction passage not adjacent to the inlet. 8. The third communication passage according to claim 7, wherein an inlet-side end of the first communication passage is opened at a position corresponding to a suction passage located farthest from an inlet for introducing gas to the swash plate chamber. The lubricating structure of the shaft seal mechanism in the swash plate type compressor in which the outlet side end of the swash plate type is opened to the suction passage closest to the inlet. 9. The discharge chamber according to claim 2, wherein the discharge chamber communicates with a discharge passage for guiding gas in the discharge chamber to the outside of the apparatus, and the communication passage forming wall is provided between the discharge passage and the drive shaft. A lubricating structure for a shaft seal mechanism in a swash plate compressor formed at a position opposite to the opening position.