JP4292539B2 - Compressor - Google Patents

Description

[0001]
[Technical field to which the invention belongs]
The present invention relates to a compressor used in a vehicle air conditioner and the like, and relates to a compressor that improves the supply of lubricating oil around a drive shaft.
[0002]
[Prior art]
A drive shaft that passes through the crank chamber and is rotatably supported by the housing, and is arranged in the crank chamber and rotates in synchronization with the rotation of the drive shaft, and is rotatably supported on the inner wall surface of the housing via a thrust bearing. And a drive means for reciprocatingly sliding a piston in a cylinder bore formed in the housing as the power transmission member rotates, between the housing and the drive shaft. In addition, a radial bearing that receives the drive shaft and a shaft seal member that prevents fluid leakage in the crank chamber are arranged, and in particular, the sliding contact portion between the drive shaft and the shaft seal member has good lubrication to prevent seizure. It has been requested.
[0003]
For this reason, conventionally, a lubricating oil introducing groove for introducing the lubricating oil of the crank chamber is provided on the bearing surface of the thrust bearing on the inner wall surface of the housing, and the lubricating oil introduced through the lubricating oil introducing groove is rotated with the housing. An isolation space defined by a configuration in which the guide is guided to a sliding portion with the shaft through a lubricating oil supply hole (see Patent Document 1), and a radial bearing and a shaft seal member (a seal portion made of a lip seal). In addition, the crank chamber is communicated with the crank chamber through a lubricating oil passage provided in the housing, and is communicated with the crank chamber through a gap between the flat portion provided on the drive shaft and the slide bearing. A configuration in which oil is introduced into the isolation space and the lubricating oil in the isolation space is returned to the crank chamber via the other is considered (see Patent Document 2).
In addition, a configuration is conceivable in which oil accumulated in the crank chamber is scraped up by a drive rod protruding from the drive shaft in a direction perpendicular to the drive shaft and splashed onto each sliding portion (Patent Document). 3).
[0004]
[Patent Document 1]
Japanese Patent Laid-Open No. 8-284820 [Patent Document 2]
Japanese Patent Laid-Open No. 2002-310067 [Patent Document 3]
Japanese Utility Model Publication No. 63-7289
[Problems to be solved by the invention]
However, in the configurations of Patent Documents 1 and 2 described above, the lubricating oil descending along the inner peripheral surface of the housing is isolated via the lubricating oil introduction groove and the lubricating oil supply hole, or via the lubricating oil passage. Although the lubricating oil introduced into the bulkhead space has flowed in a random manner due to gravity, etc., the amount of oil supplied to the seal and radial bearings is uneven, There were concerns about inconvenience such as lack of lubricating oil.
[0006]
In particular, according to the former configuration, the supply of lubricating oil to the isolation space is ensured, but since there is no configuration that actively releases the lubricating oil introduced into the isolation space, There is a concern that the lubricating oil does not flow in the space, the temperature of the sealing member rises, the shaft sealing function decreases, and the lubricating oil leaks from between the shaft sealing member and the drive shaft.
[0007]
On the other hand, according to the latter configuration, since the flat portion is provided on the outer peripheral portion of the drive shaft, the lubricating oil is returned to the crank chamber through the gap between the flat portion and the slide bearing. However, even in such a configuration, it is expected that the lubricating oil will accumulate in the lower part of the isolation space due to the sliding bearing.As in the former case, the temperature of the sealing member rises, and the lubricating oil leaks as the shaft sealing function decreases. There are concerns about the problems that occur.
[0008]
Further, according to the configuration of Patent Document 3, since the oil stored in the crank chamber is merely scraped up by the drive rod, sufficient oil is supplied to the shaft seal member and the bearing that originally require oil. could not.
[0009]
The present invention has been made in view of the above points, and ensures good lubrication by positively supplying lubricating oil to a shaft seal member and a radial bearing provided around a drive shaft. By promoting the replacement of the lubricating oil supplied to the sealing member, the main problem is to suppress a decrease in the shaft sealing function due to the temperature rise of the shaft sealing member and reduce oil leakage.
Another object of the present invention is to actively supply lubricating oil to a shaft seal member and a radial bearing provided around the drive shaft by scooping up oil accumulated at the bottom of the crank chamber.
[0010]
[Means for Solving the Problems]
In order to achieve the above object, a compressor according to the present invention includes a drive shaft that passes through a crank chamber and is rotatably supported by a housing, and is arranged in the crank chamber in synchronization with the rotation of the drive shaft. A power transmission member that rotates and is rotatably supported on the inner wall surface of the housing via a thrust bearing, and a drive unit that reciprocally slides a piston in a cylinder bore formed in the housing as the power transmission member rotates. A radial bearing and a shaft sealing member for preventing leakage of fluid in the crank chamber between the housing and the drive shaft, and an isolation space between the radial bearing and the shaft sealing member. The first guide groove that extends downward on the bearing surface facing the thrust bearing on the inner wall surface of the housing, and communicates with the isolation space, A second guide groove formed in the housing from the outer peripheral portion of the sealing member to the outer peripheral portion of the radial bearing, and lubricating oil introduced through the first guide groove is supplied to the second guide groove. A communication hole formed in the housing is provided.
[0011]
Therefore, when the lubricating oil attached to the inner wall surface of the housing descends downward along the first guide groove, it is introduced into the second guide groove via the communication hole. Since the second guide groove is formed from the outer peripheral surface of the shaft seal member to the outer peripheral surface of the radial bearing, the lubricating oil introduced here is guided to the shaft seal member and the radial bearing through this groove. Thus, it becomes possible to positively supply the lubricating oil to the shaft seal member and the radial bearing.
[0012]
Here, the lubricating oil introduced into the second guide groove is preferably formed above the shaft seal member and the radial bearing in order to ensure a smooth flow.
[0013]
Furthermore, it is desirable that the outlet of the communication hole is opened so as to be in the second guide groove or over the second guide groove. Moreover, you may make it open the 1st guide groove so that the inside of the said communicating hole or the said communicating hole may be covered.
According to such a configuration, it is possible to guide almost all of the lubricating oil that descends along the first guide groove to the second guide groove through the communication hole, and a rich supply of lubricating oil is possible. Become.
[0014]
In addition to the above configuration, a third guide groove formed between the receiving surface of the radial bearing and the radial bearing, one end communicating with the isolation space and the other end communicating with the crank chamber. Further, it may be provided.
In particular, the third guide groove may be formed between a bearing surface that receives a lower portion of the radial bearing and the radial bearing.
[0015]
According to such a configuration, the lubricating oil supplied to the isolation space is surely returned to the crank chamber via the third guide groove, so that the replacement of the lubricating oil supplied to the isolation space is promoted. Thus, it is possible to avoid the deterioration of the shaft sealing function accompanying the temperature rise of the shaft sealing member, and to reduce the inconvenience that the lubricating oil leaks to the atmosphere.
In addition, it is not necessary to separately provide the lubricating oil supplied to the isolation space and the lubricating oil path supplied to the thrust bearing, and the lubricating oil supplied to the isolation space can be supplied to the thrust bearing as it is. It is possible to supply abundant lubricating oil to the isolation space and the thrust bearing.
[0016]
Here, the third guide groove may have various configurations. For example, even if the third guide groove is formed by a groove formed on the receiving surface of the radial bearing of the housing, the radial bearing is formed by a split bush. In the case where the sliding bearing is used, it may be constituted by a gap between the mating portions of the split bush. Further, the third guide groove may be constituted by a groove formed in the outer ring of the radial bearing.
[0017]
Further, in contrast to the above-described configuration, a counterweight is provided at the peripheral edge portion of the power transmission member, and an oil scooping portion is provided at a circumferential end portion of the counterweight. An inclined surface that faces the wall surface and is inclined with respect to a surface parallel to the drive shaft may be formed.
[0018]
According to such a configuration, when the power transmission member rotates with the rotation of the drive shaft, the oil accumulated in the crank chamber is scooped up by the oil scooping portion of the counterweight. At this time, since the inclined surface of the oil scooping portion is inclined so as to face the inner wall surface of the housing, the oil is scraped up toward the inner wall surface of the housing, and around the drive shaft via the thrust bearing. It will be supplied to the radial bearing and the shaft seal member.
[0019]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 shows a clutchless type variable capacity swash plate compressor used in a refrigeration cycle as an example of a compressor. This compressor includes a cylinder block 1, a rear head 3 assembled on the rear side (right side in the figure) of the cylinder block 1 via a valve plate 2, and a front side (left side in the figure) of the cylinder block 1. And a front head 4 assembled so as to be closed. The front head 4, the cylinder block 1, the valve plate 2, and the rear head 3 are fastened in the axial direction by fastening bolts 5 and constitute a housing for the entire compressor.
[0020]
A crank chamber 6 provided by the front head 4 and the cylinder block 1 accommodates a drive shaft 7 having one end protruding from the front head 4. A drive pulley (not shown) connected to the engine of the vehicle via a belt is fixed to a portion of the drive shaft 7 protruding from the front head 4. Further, one end side of the drive shaft 7 is hermetically sealed with the front head 4 via a shaft sealing member 10 provided between the drive shaft 7 and the refrigerant leakage along the drive shaft 7 is prevented. Like to do. One end side of the drive shaft 7 is rotatably supported by a radial bearing 11 accommodated on the crank chamber side of the shaft seal member 10 of the front head 4, and the other end side of the drive shaft 7 is supported by the cylinder block 1. Is rotatably supported by a radial bearing 12 housed in the housing.
[0021]
The cylinder block 1 is formed with a support hole 13 in which the radial bearing 12 is accommodated, and a plurality of cylinder bores 15 arranged at equal intervals on a circumference around the support hole 13. A single-head piston 16 is inserted into the cylinder bore 15 so as to be slidable back and forth. The one-head piston 16 is formed hollow by joining a head portion 16a inserted into the cylinder bore 15 and an engaging portion 16b protruding into the crank chamber 6 in the axial direction.
[0022]
A thrust flange 17 that rotates integrally with the drive shaft 7 is fixed to the drive shaft 7 in the crank chamber 6. The thrust flange 17 is rotatably supported via a thrust bearing 18 on an inner wall surface 4 a of the front head 4 formed substantially perpendicular to the drive shaft 7. The thrust flange 17 constitutes a power transmission member, and the thrust flange 17 is connected to a swash plate 20 via a link member 19.
[0023]
The swash plate 20 is attached so as to be able to tilt around a hinge ball 21 slidably provided on the drive shaft 7, and is integrated with the rotation of the thrust flange 17 via the link mechanism 19. It is designed to rotate. And the swash plate 20 is moored by the engaging part 16b of the one-headed piston 16 via a pair of shoes 22 which the peripheral part distribute | arranged back and forth.
[0024]
Accordingly, when the drive shaft 7 is rotated, the swash plate 20 is rotated accordingly, and the rotational motion of the swash plate 20 is converted into the reciprocating linear motion of the single-headed piston 16 via the shoe 22, and the single-headed piston 16 in the cylinder bore. The volume of the compression chamber 23 formed between the valve plate 2 and the valve plate 2 is changed.
[0025]
Reference numeral 24 denotes a suction hole formed in the valve plate 2 that communicates the suction chamber 25 formed in the rear head 3 and the compression chamber 23 via a suction valve (not shown), and 26 denotes a hole formed in the rear head 3. This is a discharge hole formed in the valve plate 2 that communicates the discharge chamber 27 and the compression chamber 23 via a discharge valve (not shown). Reference numeral 28 denotes a pressure control valve that controls the communication state between the discharge chamber 27 and the crank chamber 6 and adjusts the crank chamber pressure to adjust the tilt angle of the swash plate 20.
[0026]
By the way, the shaft seal member 10 and the radial bearing 11 are arranged with a space therebetween in the axial direction, and are annularly formed by the shaft seal member 10 and the radial bearing 11 between the front head 4 and the drive shaft 7. An isolation space 30 is formed. Further, as shown in FIG. 2, the front head 4 has a bearing surface for receiving the thrust bearing 18 on the inner wall surface 4a located above the drive shaft 7, more specifically, as shown in the figure, the thrust bearing 18 Is formed by the needle roller 18a and the thrust trace 18b that holds the needle roller 18a, the first guide groove 31 that guides the lubricating oil to the portion of the front head 4 that receives the thrust trace 18b extends downward. Yes. Further, a second guide groove 32 extending in the axial direction from the outer peripheral portion of the shaft seal member 10 to the outer peripheral portion of the radial bearing 11 is formed at a portion facing the isolation space 30 of the front head 4.
[0027]
The first guide groove 31 and the second guide groove 32 are connected by a communication hole 33 formed in the front head 4 at a predetermined angle with respect to the axial direction. The lubricating oil introduced into the second guide groove 32 is supplied to the second guide groove 32 through the communication hole 33. Here, the communication hole 33 is opened immediately below the first guide groove 31 so as to be able to receive the lubricating oil descending through the first guide groove 31, and is transmitted through the first guide groove 31. It is possible to introduce almost all of the lubricant that descends.
[0028]
Further, the front head 4 has a third guide groove 34 having one end communicating with the isolation space 30 and the other end communicating with the crank chamber 6 between the bearing surface receiving the lower portion of the radial bearing 11 and the radial bearing 11. Is formed. In this example, the third guide groove 34 is a receiving surface for receiving the lower end of the radial bearing 11 of the front head 4, more specifically, as shown in the figure, the radial bearing 11 is a needle roller 11 a and a radial race that holds this. 11b, it is configured by forming a groove extending in the axial direction in the portion of the front head 4 that receives the lower side of the radial race 11b as shown in FIG. Here, the third guide groove 34 opens to the inner wall surface 17a of the front head 4 on the inner side (drive shaft side) of the thrust bearing 18, and the lubricating oil flowing out from the third guide groove 34 is thrust bearing. The gap 18 is returned to the crank chamber 6.
[0029]
In the above configuration, when the lubricating oil adhering to the inner wall surface of the front head 4 descends downward along the first guide groove 31, almost all of it is introduced into the communication hole 33, and is transmitted through the communication hole 33. It is guided to the second guide groove 32. Since the second guide groove 32 is formed in the axial direction from the outer peripheral portion of the shaft seal member 10 to the outer peripheral portion of the radial bearing 11, the lubricating oil introduced into the second guide groove 32 causes the guide groove to pass through the second guide groove 32. Then, it is guided to the shaft seal member 10 and the radial bearing 11 and introduced into the isolation space 30 while being actively supplied to the shaft seal member 10 and the radial bearing 11.
[0030]
For this reason, since almost all of the lubricant oil that has fallen along the first guide groove 31 is supplied to the second guide groove 32, it is possible to supply the lubricant oil abundantly, and the second guide groove 32. Thus, the lubricating oil can be positively supplied to the shaft seal member 10 and the radial bearing 11, so that it is possible to ensure good lubrication of the shaft seal member 10 and the radial bearing 11. Therefore, seizure between the shaft seal member 10 and the drive shaft 7 can be eliminated, and the life of the radial bearing 11 can be extended.
[0031]
The lubricating oil supplied to the isolation space 30 is surely returned to the crank chamber 6 through the third guide groove 34 without stagnation in the isolation space 30. Therefore, it is possible to avoid the inconvenience that the temperature of the shaft seal member 10 rises and the shaft seal function is lowered, and it is possible to prevent the lubricating oil from leaking to the outside. If the third guide groove 34 is too large, the lubricating oil supplied to the isolation space will flow before it is sufficiently utilized for lubrication. It is desirable to make it smaller than the passage area.
[0032]
Further, in the above-described configuration, the lubricating oil supplied to the isolation space 30 and the path of the lubricating oil supplied to the thrust bearing 18 are common, so the lubricating oil supplied to the isolation space 30 is used as it is in the thrust bearing. 18 can be supplied to the thrust bearing 18 as well.
[0033]
In the above-described configuration, the configuration example in which the third guide groove 34 is formed on the bearing surface of the radial bearing 11 of the front head 4 is shown. However, as shown in FIG. 4, the radial bearing 11 is split into the split bush 11c. The third guide groove 34 may be formed by a gap between the mating portions of the split bush 11c. When the outer ring 11d of the radial bearing 11 is thick, the third guide groove 34 may be formed by a groove formed in the outer ring 11d of the radial bearing 11 as shown in FIG. Good.
[0034]
In FIG. 6, the thrust flange 17 is shown. In the thrust flange 17, a through hole 40 into which a drive shaft is inserted is formed at the center, and a connecting portion 17 a constituting a part of the link mechanism 19, A counterweight portion 17b disposed on the opposite side of the connecting portion 17a with respect to the through hole 40 serving as the rotation center is integrally provided. The counterweight portion 17b is formed in a fan shape having a predetermined circumferential angle with respect to the center of rotation. In this example, the distance from the center of rotation to the periphery is formed uniformly, and the thrust flange 17 is rotated. Along with this, the oil is accumulated in the oil accumulated at the bottom of the crank chamber 6.
[0035]
And the oil scooping part 41 is provided in the both ends of the circumferential direction of the counterweight part 17b. The oil scooping portion 41 is formed so as to protrude in the circumferential direction at both ends in the circumferential direction of the counterweight portion 17b, and on the side facing the inner wall surface 4a of the front head 4, An inclined surface 41 a that faces the inner wall surface 4 a and is inclined with respect to a surface parallel to the drive shaft 7 is formed. That is, the inclined surface 41a is inclined so as to gradually move away from the inner wall surface 4a of the front head 4. In this example, the inclined surface 41a is formed in a shape that widens toward the center of rotation from the periphery of the counterweight portion 17b. Has been.
[0036]
Accordingly, when the drive shaft rotates and the counterweight portion 17b rotates, the oil scooping portion 41 enters the oil accumulated at the bottom of the crank chamber 6 every time the counterweight portion 17b rotates, and the tip side in the rotational direction is When the scraping unit 41 comes out of the oil, the oil is scraped upward. At that time, the scraping portion 41 is formed with an inclined surface 41a that is gradually inclined toward the direction away from the inner wall surface 4a. It will be scattered toward the side. For this reason, the oil scattered toward the inner wall surface side is supplied to the radial bearing 11 and the shaft seal member 10 through the gaps of the thrust bearing 18, and abundant oil is supplied to these locations, so that the radial bearing 11 and the shaft seal member 10 can be accelerated and good lubrication can be ensured.
[0037]
【The invention's effect】
As described above, according to the present invention, the first guide groove that extends downward on the bearing surface facing the thrust bearing on the inner wall surface of the housing, and the isolation space communicate with the first guide groove. A second guide groove formed in the housing from the outer peripheral portion to the outer peripheral portion of the radial bearing and a communication hole that communicates the first guide groove and the second guide groove are provided to supply lubricating oil in the crank chamber. Since the second guide groove is guided, the lubricating oil introduced into the second guide groove can be positively supplied to the shaft seal member and the radial bearing through the guide groove.
[0038]
Further, by providing a third guide groove between the bearing surface that receives the lower part of the radial bearing and the radial bearing, one end of which communicates with the isolated space and the other end communicates with the crank chamber. It is possible to reliably return to the crank chamber via the third guide groove, and it is possible to promote replacement of the lubricating oil supplied to the isolation space. For this reason, it is possible to avoid a decrease in the shaft seal function due to the temperature rise of the shaft seal member, and it is possible to reduce inconvenience that the lubricating oil leaks to the atmosphere.
[0039]
Furthermore, by combining the above-described configurations, the lubricating oil supplied to the isolation space can be shared with the lubricating oil supplied to the isolation space and the lubricating oil path supplied to the thrust bearing. Can be supplied to the thrust bearing as it is, and the lubricating oil is not divided and supplied to the thrust bearing and the isolation space. For this reason, abundant lubricating oil can be supplied to both the isolation space and the thrust bearing, so that good lubrication of the shaft seal member and the radial bearing can be ensured, and cooling in the isolation space can be ensured. Is promoted, and leakage of the lubricating oil to the outside can be suppressed.
[0040]
Furthermore, a counterweight is provided at the peripheral edge of the power transmission member, and an oil scraping portion is provided at the circumferential end of the counterweight. The oil scraping portion faces the inner wall surface of the housing, If an inclined surface that is inclined with respect to the parallel surface is formed, the oil accumulated in the crank chamber is scraped up toward the inner wall surface of the housing by the inclined surface of the oil scooping portion. Abundant oil can be supplied to the radial bearing and the shaft seal member around the drive shaft, so that good lubrication can be ensured, the deterioration of the shaft seal function can be suppressed, and oil leakage can be reduced.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a compressor according to an embodiment of the present invention.
FIG. 2 is an enlarged cross-sectional view of a part of the front head of the compressor of FIG.
FIG. 3 is a schematic configuration diagram showing an example in which a third guide groove is formed in the housing (front head 4) below the radial bearing.
FIG. 4 is a schematic configuration diagram showing an example in which a radial bearing is formed by a split bush, and a third guide groove is formed by a gap at a mating portion of the split bush.
FIG. 5 is a schematic configuration diagram showing an example in which the third guide groove is configured by a groove formed in the outer ring of the radial bearing 11;
6 is a view showing a thrust flange, FIG. 6 (a) is a cross-sectional view of a thrust flange fixed to a drive shaft, and FIG. 6 (b) is a view of FIG. 6 (a). FIG. 6C is a perspective view showing the vicinity of the oil scooping portion provided on the thrust flange.
[Explanation of symbols]
4 Front head 4a Inner wall surface 6 Crank chamber 7 Drive shaft 10 Shaft seal member 11 Radial bearing 15 Cylinder bore 16 Piston 17 Thrust flange 17b Counterweight portion 18 Thrust bearing 30 Isolation space 31 First guide groove 32 Second guide groove 33 Communication Hole 34 Third guide groove 41 Oil scraping portion 41a Inclined surface

Claims (9)

A drive shaft that passes through the crank chamber and is rotatably supported by the housing, and rotates in synchronism with the rotation of the drive shaft disposed in the crank chamber, and can rotate on the inner wall surface of the housing via a thrust bearing And a drive means for reciprocally sliding a piston in a cylinder bore formed in the housing as the power transmission member rotates, and between the housing and the drive shaft, In a compressor that accommodates a radial bearing and a shaft seal member that prevents leakage of fluid in the crank chamber, and an isolation space is defined between the radial bearing and the shaft seal member.
A first guide groove extending downward on a bearing surface facing the thrust bearing on the inner wall surface of the housing;
A second guide groove formed in the housing from the outer periphery of the shaft seal member to the outer periphery of the radial bearing;
A compressor comprising a communication hole formed in the housing so as to supply the lubricating oil introduced through the first guide groove to the second guide groove.   The compressor according to claim 1, wherein the second guide groove is formed above the shaft seal member and the radial bearing.   3. The compressor according to claim 1, wherein an outlet of the communication hole is opened so as to cover the inside of the second guide groove or the second guide groove. 3. A third guide groove formed between the receiving surface of the radial bearing and the radial bearing, wherein one end communicates with the isolation space and the other end communicates with the crank chamber. Item 4. The compressor according to any one of Items 1 to 3. The compressor according to claim 4, wherein the third guide groove is formed between a bearing surface that receives a lower portion of the radial bearing and the radial bearing. The compressor according to claim 4 or 5, wherein the third guide groove is configured by a groove formed on a bearing surface facing the radial bearing of the housing. 6. The compression according to claim 4 or 5 , wherein the radial bearing is configured by a sliding bearing formed of a split bush, and the third guide groove is configured by a gap of a mating portion of the split bush. Machine. The compressor according to claim 4 or 5, wherein the third guide groove is configured by a groove formed in an outer ring of the radial bearing. A counterweight is provided at the peripheral edge of the power transmission member, and an oil scooping portion is provided at the circumferential end of the counterweight. The oil scooping portion faces the inner wall surface of the housing, and the drive shaft The compressor according to any one of claims 1 to 8, wherein an inclined surface that is inclined with respect to a parallel surface is formed.

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