JP2009264365A - Variable displacement compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement compressor for improving reliability in a seal member, by improving durability in the seal member to a rotary shaft. <P>SOLUTION: A shaft seal chamber 22 is formed inside a front housing 3, and a partition member 21 is arranged inside the shaft seal chamber 22. The partition member 21 separates the inside of the shaft seal chamber 22 into a first seal chamber 22a being the discharge refrigerant passage 33 side and a second seal chamber 22b being the radial roller bearing 8 and lip seal 10 side. A passage 31 for introducing compressed refrigerant gas is formed inside a driving shaft 7, The driving shaft 7 is provided with a discharge refrigerant passage 33 for communicating the first seal chamber 22a of the shaft seal chamber 22 with the passage 31. A clearance A for introducing the refrigerant gas in the first seal chamber 22a to a lip seal 10 in a second seal chamber, is formed between the partition member 21 and the driving shaft 7. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a variable displacement compressor, and more particularly to a lubricating structure of a seal member for a rotating shaft of a variable displacement compressor.

  Patent Document 1 discloses a swash plate compressor including a crankcase in which a crank chamber is formed, a rotating shaft having one end exposed to the outside of the crankcase, and a lip seal for the rotating shaft. According to this, the space part divided by the crankcase, the rotating shaft, the radial bearing, and the lip seal is formed inside the crankcase. Further, a pressure control passage for introducing the compressed refrigerant into the crank chamber is formed inside the rotating shaft. Further, the rotation shaft is provided with an oil supply hole that communicates the pressure control passage and the space. The compressed refrigerant is introduced into the space through the pressure passage and the oil supply hole, and flows into the crank chamber through a gap in the radial bearing. The refrigerant flowing into the crank chamber contains mist-like lubricating oil, and the crank chamber is lubricated by this lubricating oil.

  Patent Document 2 discloses a swash plate compressor in which a partition wall is provided in the shaft seal chamber to separate the seal portion and the rotary shaft bearing, and a gap is formed between the partition wall and the rotary shaft. The compressor communicates with the crank chamber and the shaft seal chamber, and is fixed to the rotating shaft so as to communicate with the first passage through which the refrigerant gas containing lubricating oil is guided from the crank chamber, and the rotating shaft bearing and the crank chamber. A second passage formed between the lug plate and the housing. According to this, the refrigerant gas in the vicinity of the outer periphery of the crank chamber passes through the first passage, the seal portion side of the shaft seal chamber, the gap between the partition walls, the rotary shaft bearing side of the shaft seal chamber, the rotary shaft bearing, the second passage, and the crank chamber. A path that circulates in order is formed, and the refrigerant gas containing the lubricating oil easily flows into the seal portion side of the shaft seal chamber. Therefore, the seal portion of the rotating shaft is efficiently lubricated.

JP-A-4-179874 JP 2006-307700 A

  Here, in the swash plate compressor described in Patent Document 1, the sliding portion between the rotating shaft and the lip seal, which is one of the members that define the space portion, is a refrigerant introduced into the space portion through the oil supply hole. It is lubricated by the lubricating oil inside. However, in the swash plate type compressor described in Patent Document 1, the oil supply hole provided in the rotating shaft extends along the radial direction of the rotating shaft, and therefore, on the radially outer side in the space portion due to the action of centrifugal force. It circulates toward and passes through the radial bearing. Therefore, a sufficient amount of lubricating oil is not supplied to the sliding portion between the rotating shaft and the lip seal, and there is a problem that the lubrication failure occurs and the reliability of the lip seal is lowered.

  Further, in the swash plate compressor described in Patent Document 2, a part of the refrigerant in the discharge chamber is introduced to the rotary shaft bearing side of the shaft seal chamber through a discharge refrigerant passage formed in the rotary shaft, It is introduced into the crank chamber via the second passage. However, in the swash plate compressor described in Patent Document 2, the lubricating oil of the refrigerant introduced from the discharge chamber to the rotating shaft bearing side of the shaft seal chamber is caused by centrifugal force to cause the outer peripheral surface of the shaft seal chamber on the rotating shaft bearing side. It becomes easy to stay in. Further, the swash plate compressor described in Patent Document 2 is provided with a partition wall that separates the shaft seal chamber into the seal portion side and the rotary shaft bearing side, and the partition wall forms a slight gap with the rotation shaft. The refrigerant lubricant introduced from the discharge chamber through the discharge refrigerant passage to the rotary shaft bearing side of the shaft seal chamber is difficult to be introduced to the seal portion side of the shaft seal chamber, and the sliding portion between the seal portion and the rotary shaft Therefore, a sufficient amount of lubricating oil is not supplied, which may cause poor lubrication and reduce the reliability of the seal portion.

  The present invention has been made to solve such problems, and provides a variable capacity compressor in which the durability of the seal member with respect to the rotating shaft is improved and the reliability of the seal member is improved. Objective.

  A variable capacity compressor according to the present invention includes a housing in which a crank chamber is formed, a rotating shaft provided in the crank chamber, at least one end exposed to the outside of the housing, a rotating shaft fixed to the rotating shaft, A lug plate that rotates as a unit, a rotary shaft bearing that rotatably supports the rotary shaft relative to the housing, and a refrigerant leaked along the rotary shaft to the outside of the housing, provided on the outer side of the rotary shaft bearing of the housing A shaft seal chamber that is a space defined by the seal member, the housing, the rotary shaft, the lug plate, the rotary shaft bearing, and the seal member, and the shaft seal chamber that is provided in the rotary shaft and contains a lubricant. In the variable capacity compressor having the discharge refrigerant passage leading to the first seal chamber, the shaft seal chamber is disposed on the discharge refrigerant passage side inside the shaft seal chamber, and the rotary shaft bearing. And a partition member separated from the second seal chamber on the seal member side. The partition member guides all the refrigerant introduced from the discharge refrigerant passage into the first seal chamber to the seal member in the second seal chamber. A passage is provided.

  The variable displacement compressor includes a housing, a rotating shaft, a lug plate, a rotating shaft bearing, a shaft seal chamber that is a space partitioned by a seal member, and a discharge refrigerant passage that guides a refrigerant containing lubricating oil to the shaft seal chamber. Therefore, the refrigerant containing the lubricating oil is guided to the shaft seal chamber through the discharge refrigerant passage. A partition member separating the shaft seal chamber into a first seal chamber on the discharge refrigerant passage side and a second seal chamber on the rotary shaft bearing and seal member side is provided inside the shaft seal chamber, and the discharge refrigerant passage is provided in the partition member. Since the guide passage for guiding all the refrigerant introduced from the first seal chamber to the seal member in the second seal chamber is provided, all of the refrigerant guided from the first seal chamber to the second seal chamber via the guide passage is Passes in the vicinity of the sliding portion between the rotating shaft and the seal member. That is, a sufficient amount of lubricating oil is supplied to the sliding portion between the rotating shaft and the seal member. Therefore, in the variable capacity compressor, it is possible to improve the durability of the seal member with respect to the rotating shaft and improve the durability of the seal member.

The partition member may be disposed on the rotating shaft or the lug plate.
The first seal chamber may be partitioned by a partition member such that the cross-sectional area of the first seal chamber decreases from the discharge refrigerant passage side toward the guide passage side. The flow rate of the refrigerant guided from the discharge refrigerant passage to the first seal chamber and guided to the second seal chamber via the guide passage is increased. Since the refrigerant whose flow rate is increased is guided to the seal member, it is possible to reduce the heat generation of the seal member, and the reliability of the seal member can be further improved.

  The partition member may be further provided with a guide passage for allowing the refrigerant that has passed through the guide passage to flow along the outer peripheral surface of the seal member. All of the refrigerant guided to the seal member through the guide passage is blocked by the inner peripheral surface of the guide passage, and passes through the vicinity of the sliding portion between the rotating shaft and the seal member without diffusing radially outward. Therefore, the lubricating oil can be supplied more reliably to the sliding portion between the rotating shaft and the seal member.

  According to this invention, in the variable capacity compressor, it is possible to improve the durability of the seal member with respect to the rotating shaft and improve the reliability of the seal member.

Embodiments of the present invention will be described below with reference to the accompanying drawings.
Embodiment 1 FIG.
FIG. 1 shows a variable capacity compressor 1 (hereinafter abbreviated as a compressor 1) according to Embodiment 1 of the present invention. In the following description, the front-rear direction in the compressor 1 is defined by arrows shown in FIG.
The compressor 1 includes a cylinder block 2. A front housing 3 is joined to an end of the cylinder block 2 on the front side, and a crank chamber 4 is formed therein. A rear housing 6 is joined to the rear end of the cylinder block 2 via a valve / port forming body 5.

  A drive shaft 7 that is a rotating shaft is rotatably provided at the center of the crank chamber 4. The front end of the drive shaft 7 is exposed to the outside through the front housing 3 and is connected to a drive source (not shown). The drive shaft 7 is configured by press-fitting a second shaft 7b having a hollow cylindrical shape opened at both ends into a first shaft 7a having a hollow cylindrical shape opened at one end. A passage 31 is formed on the inner peripheral side of the first shaft 7a and the inner peripheral side of the second shaft 7b. A passage 32 is formed between the inner peripheral surface of the first shaft 7a and the outer peripheral surface of the second shaft 7b. On the front side in the passage 32, an O-ring 7c is sandwiched between the inner peripheral surface of the first shaft 7a and the outer peripheral surface of the second shaft 7b.

  In the crank chamber 4, a lug plate 11 is fixed to the outer peripheral surface of the drive shaft 7, and the drive shaft 7 and the lug plate 11 can rotate together. The lug plate 11 is rotatably supported by a radial roller bearing 8 which is a rotary shaft bearing fitted in the front housing 3. The radial roller bearing 8 also rotatably supports the front side of the drive shaft 7 via the lug plate 11. Further, the rear side of the drive shaft 7 is rotatably supported by a radial roller bearing 9 fitted in the cylinder block 2. Further, the lug plate 11 is rotatably supported by a thrust bearing 12 provided between the inner wall surface 3 a of the front housing 3 and the lug plate 11.

  On the rear side of the lug plate 11, a swash plate 13 is provided on the outer peripheral surface of the drive shaft 7 so as to be tiltable and slidable with respect to the axial direction of the drive shaft 7. The guide hole 11a of the lug plate 11 and the connecting portion 13a of the swash plate 13 are connected via a guide pin 13b attached to the tip of the connecting portion 13a, and the lug plate 11 and the swash plate 13 are synchronized. It is designed to rotate. A plurality of pistons 14 arranged circumferentially around the drive shaft 7 are connected to the swash plate 13 via shoes 15. Each piston 14 is housed in a plurality of cylinder bores 2 a formed inside the cylinder block 2, and reciprocates in the cylinder bore 2 a in conjunction with the rotation of the swash plate 13.

  On the other hand, on the front side of the lug plate 11 and the radial roller bearing 8, a lip seal 10 that is a seal member for the drive shaft 7 is provided on the inner peripheral portion of the front housing 3. The lip seal 10 prevents refrigerant gas and lubricating oil in the crank chamber 4 from leaking out of the front housing 3 along the outer peripheral surface of the drive shaft 7. Here, a shaft seal chamber 22, which is a space defined by the front housing 3, the drive shaft 7, the radial roller bearing 8, the lip seal 10, and the lug plate 11, is formed inside the front housing 3. The drive shaft 7 is provided with a discharge refrigerant passage 33 that communicates the passage 31 in the drive shaft 7 with the shaft seal chamber 22. As will be described later, the compressed refrigerant gas is introduced into the passage 31, and all the refrigerant gas in the passage 31 is introduced into the shaft seal chamber 22 through the discharge refrigerant passage 33.

Next, the structure around the shaft seal chamber 22 will be described in detail with reference to FIG.
Inside the shaft seal chamber 22, a partition member 21, which is a ring having an L-shaped cross section, is provided at the front end of the lug plate 11. The partition member 21 is disposed so as to cover the opening 33 a of the discharge refrigerant passage 33 toward the shaft seal chamber 22, and is fixed so as to rotate integrally with the lug plate 11. Further, the lip seal 10 is arranged. That is, the shaft seal chamber 22 is separated by the partition member 21 into a first seal chamber 22a on the discharge refrigerant passage 33 side and a second seal chamber 22b on the radial roller bearing 8 and lip seal 10 side.

  Further, a gap A is formed between the inner peripheral surface 21 a of the partition wall member 21 and the outer peripheral surface 7 d of the drive shaft 7 facing the inner peripheral surface 21 a, and this gap A is guided in the partition wall member 21. It constitutes a passage. Therefore, the refrigerant gas that has flowed into the first seal chamber 22a via the discharge refrigerant passage 33 flows into the second seal chamber 22b via the gap A. All of the refrigerant gas that has flowed into the second seal chamber 22 b is guided to the lip seal 10 along the outer peripheral surface 7 d of the drive shaft 7 and passes through the vicinity of the lip seal 10.

  A passage 34 that is a hole penetrating the front housing 3 is formed in the front housing 3. Further, a groove extending along the radial direction is formed in the inner wall surface 3 a of the front housing 3, and the groove 35 is blocked by the front surface of the thrust bearing 12 to form a passage 35. One end of the passage 34 opens to the second seal chamber 22 b of the shaft seal chamber 22, and the other end of the passage 34 is connected to one end located on the radially inner side of the passage 35. The other end located on the radially outer side of the passage 35 opens to the outer peripheral side in the crank chamber 4.

  In addition, a space 36 defined by the front housing 3, the radial roller bearing 8, the lug plate 11, and the thrust bearing 12 is formed on the rear side of the radial roller bearing 8. Here, the radial roller bearing 8 has a bearing body portion in which a plurality of needles are arranged circumferentially in an annular bearing race 8a having a U-shaped cross section that opens radially inward. 8b is housed and configured. A gap d1 is formed between the inner peripheral surface of the bearing race 8a and the outer peripheral surface of the lug plate 11. Therefore, the refrigerant gas and the lubricating oil can flow through the radial roller bearing 8 through the gap d1 between the bearing race 8a and the lug plate 11.

  The thrust bearing 12 includes a pair of bearing races 12a and 12b, which are hollow discs having an L-shaped cross section, and a bearing body portion 12c in which a plurality of needles are circumferentially spaced apart. Have. The bearing races 12a and 12b sandwich the bearing body 12c in a state where a gap d2 is formed between opposite ends on the outer peripheral side and the inner peripheral side. Accordingly, the refrigerant gas and the lubricating oil can flow through the thrust bearing 12 through the gap d2 between the bearing races 12a and 12b. That is, the space portion 36 communicates with the second seal chamber 22b of the shaft seal chamber 22 via the radial roller bearing 8 on the one hand, and on the other side of the crank chamber 4 via the thrust bearing 12 on the other hand. It is in a state of communication.

  Returning to FIG. 1, a discharge chamber 16 is formed at the center of the rear housing 6, and is connected to one end of the external refrigerant circuit via a discharge opening (not shown). A suction chamber 17 serving as a suction side pressure region is formed around the rear housing 6 in an annular shape, and is connected to the other end of the external refrigerant circuit via a suction opening (not shown). The valve / port forming body 5 includes, for each cylinder bore 2a, a discharge port 5a for communicating the cylinder bore 2a with the discharge chamber 16, a discharge valve (not shown), and a suction port for communicating the cylinder bore 2a with the suction chamber 17. 5b and a suction valve (not shown) are provided.

  Further, a control valve 18 for controlling the internal pressure (crank pressure Pc) in the crank chamber 4 is provided inside the rear housing 6, and the control valve 18 includes a valve portion (not shown) that forms a throttle. Have. The control valve 18 is connected to the discharge chamber 16 on the one hand via the passage 41, and is connected to one end of a passage 42 formed in the rear housing 6 on the other hand. The other end of the passage 42 is connected to one end of a passage 43 formed in the valve / port forming body 5, and the other end of the passage 43 is connected to one end of a passage 44 formed in the cylinder block 2. ing. The other end of the passage 44 is connected to a space 45 formed in the cylinder block 2. An end portion on the rear side of the drive shaft 7 extends into the space portion 45, and the space portion 45 and the passage 31 in the drive shaft 7 communicate with each other via an opening portion 7 e on the rear side of the drive shaft 7. ing. The passage 31 is connected to the discharge refrigerant passage 33 described above.

  Further, a passage 46 for discharging the refrigerant gas in the crank chamber 4 is formed in a portion of the drive shaft 7 located between the lug plate 11 and the swash plate 13, and the crank chamber 4 and the drive shaft are formed. 7 is in communication with a passage 32 through a passage 46. The passage 32 communicates with one end of a passage 48 formed in the cylinder block 2. Here, a lip seal 47 is provided at the rear end of the drive shaft 7 to block the passage 31 and the passage 32 in the drive shaft 7 in the space 45. The other end of the passage 48 is connected to one end of a passage 49 formed in the valve / port forming body 5, and the other end of the passage 49 is connected to the suction chamber 17.

Next, operation | movement of the compressor 1 which concerns on Embodiment 1 of this invention is demonstrated based on FIG.
When the drive shaft 7 is rotated by being driven by a drive source (not shown), the swash plate 13 rotates in synchronization with the lug plate 11 that rotates integrally with the drive shaft 7. In conjunction with the rotation of the swash plate 13, the piston 14 reciprocates in the cylinder bore 2a. As the piston 14 reciprocates, a refrigerant gas such as carbon dioxide in the external refrigerant circuit is sucked into the suction chamber 17 and the suction chamber. The air is sucked into the cylinder bore 2a through the port 5b. The refrigerant gas sucked into the cylinder bore 2a is compressed by the piston 14, and the compressed refrigerant gas is discharged into the discharge chamber 16 through the discharge port 5a. The refrigerant gas discharged into the discharge chamber 16 circulates in the external refrigerant circuit.

  Here, a part of the refrigerant gas compressed in the cylinder bore 2 a and discharged into the discharge chamber 16 is supplied to the control valve 18 through the passage 41. The refrigerant gas supplied to the control valve 18 is throttled when passing through the valve portion in the control valve 18 to lower its temperature. The refrigerant gas whose temperature has been lowered is introduced into the first seal chamber 22a through the passages 42, 43, 44, the space 45, the passage 31, and the discharge refrigerant passage 33 in this order.

  As shown in FIG. 2, the first seal chamber 22a and the second seal chamber 22b are located between the inner peripheral surface 21a of the partition wall member 21 and the outer peripheral surface 7d of the drive shaft 7 facing the inner peripheral surface 21a. It communicates through the formed gap A. Therefore, the refrigerant gas introduced into the first seal chamber 22 a passes through the gap A, flows into the second seal chamber 22 b, and flows along the outer peripheral surface 7 d of the drive shaft 7. Since the lip seal 10 is disposed on the front side of the partition wall member 21, the refrigerant gas that has flowed into the second seal chamber 22b from the first seal chamber 22a, that is, the refrigerant gas introduced into the shaft seal chamber 22 is provided. Are guided to the lip seal 10 and pass near the sliding portion between the drive shaft 7 and the lip seal 10.

  Here, the refrigerant gas led into the second seal chamber 22b contains an oil component as a lubricating oil in a mist form, and the oil component in the refrigerant gas led to the lip seal 10 contains The sliding portion between the drive shaft 7 and the lip seal 10 is lubricated. Further, since the refrigerant gas is squeezed and the temperature is lowered when passing through a valve portion (not shown) of the control valve 18 (see FIG. 1), the drive shaft 7 is driven by the refrigerant gas guided to the lip seal 10. And the sliding portion between the lip seal 10 and the lip seal 10 are cooled.

  A part of the refrigerant gas that has passed in the vicinity of the lip seal 10 is introduced into the crank chamber 4 through the passages 34 and 35 sequentially. The remaining refrigerant gas passes through the radial roller bearing 8, the space 36, and the thrust bearing 12 in order, and is introduced into the crank chamber 4. The radial roller bearing 8 and the thrust bearing 12 are lubricated by the lubricating oil contained in the refrigerant gas that passes through them.

  Returning to FIG. 1, the crank gas Pc is generated in the crank chamber 4 by the refrigerant gas introduced into the crank chamber 4. The inclination angle of the swash plate 13 is controlled by the differential pressure between the crank pressure Pc and the pressure in the cylinder bore 2a, and the discharge capacity of the compressor 1 is determined by the inclination angle of the swash plate 13. The refrigerant gas introduced into the crank chamber 4 is discharged to the suction chamber 17 through the passage 46, the passage 32, the passage 48, and the passage 49.

  As described above, the compressor 1 includes the shaft seal chamber 22 that is a space defined by the front housing 3, the drive shaft 7, the lug plate 11, the radial roller bearing 8, and the lip seal 10, and oil components in the shaft seal chamber 22. Therefore, the refrigerant gas is led to the shaft seal chamber 22 through the discharge refrigerant passage 33. A partition member 21 that separates the shaft seal chamber 22 into a first seal chamber 22a on the discharge refrigerant passage 33 side and a second seal chamber 22b on the radial roller bearing 8 and lip seal 10 side in the shaft seal chamber 22. Since the gap A is provided in the partition wall member 21 to guide all the refrigerant gas introduced into the first seal chamber 22a from the discharge refrigerant passage 33 to the lip seal 10 in the second seal chamber 22b. All of the refrigerant gas guided from the first seal chamber 22 a to the second seal chamber 22 b passes through the vicinity of the sliding portion between the drive shaft 7 and the lip seal 10. That is, a sufficient amount of oil component is supplied to the sliding portion between the drive shaft 7 and the lip seal 10. Therefore, in the compressor 1, the durability of the lip seal 10 with respect to the drive shaft 7 can be improved, and the reliability of the lip seal 10 can be improved.

Embodiment 2. FIG.
Next, a compressor according to Embodiment 2 of the present invention will be described with reference to FIG. The compressor according to the second embodiment is configured by using a slide bearing instead of the radial roller bearing 8 according to the first embodiment. In the following description, the same reference numerals as those in FIGS. 1 and 2 are the same or similar components, and detailed description thereof will be omitted.
In the crank chamber 4, the lug plate 11 is rotatably supported by a plain bearing 51 as a slide bearing that is a rotating shaft bearing fitted in the front housing 3.

The plain bearing 51 is made of a metal member having a cylindrical shape with both ends opened. Therefore, a part of the refrigerant gas introduced into the first seal chamber 22 a through the discharge refrigerant passage 33 and flowing into the second seal chamber 22 b through the gap A is slid between the drive shaft 7 and the lip seal 10. After passing through the vicinity of the moving part, it passes through the plain bearing 51 and flows into the crank chamber 4 through the space part 36 and the thrust bearing 12. The remainder of the refrigerant gas that has flowed into the second seal chamber 22 b passes through the vicinity of the sliding portion between the drive shaft 7 and the lip seal 10 and then flows into the crank chamber 4 via the passages 34 and 35. Other configurations are the same as those in the first embodiment.
Thus, even when the plain bearing 51 is used as the rotary shaft bearing, the same effect as in the first embodiment can be obtained.

Embodiment 3 FIG.
Next, a compressor according to Embodiment 3 of the present invention will be described with reference to FIG. In the first embodiment, the radial roller bearing 8 that rotatably supports the lug plate 11 with respect to the front housing 3 is formed. However, in the third embodiment, the arrangement position of the radial roller bearing 8 and the partition member 21 Arrangement position is different. In the following description, the same reference numerals as those in FIGS. 1 and 2 are the same or similar components, and detailed description thereof will be omitted.

  A drive shaft 107, which is a rotation shaft, is rotatably provided at a central portion in the crank chamber 104 formed inside the front housing 103. The front side of the drive shaft 107 is rotatably supported by a radial roller bearing 108 that is a rotary shaft bearing fitted in the front housing 103. A partition wall member 121 that is an annular ring having an L-shaped cross section is provided between the discharge refrigerant passage 133 of the drive shaft 107 and the portion where the radial roller bearing 108 is disposed. The partition member 121 is disposed so as to cover the opening 133 a of the discharge refrigerant passage 133 toward the shaft seal chamber 122, and is fixed so as to rotate integrally with the drive shaft 107. The shaft seal chamber 122 is separated by a partition member 121 into a first seal chamber 122a and a second seal chamber 122b.

Further, a gap B is formed between the inner peripheral surface 121 a of the partition member 121 and the outer peripheral surface 107 d of the drive shaft 107 facing the inner peripheral surface 121 a, and this gap B is guided in the partition member 121. It constitutes a passage. Therefore, the refrigerant gas that has flowed into the first seal chamber 122a via the discharge refrigerant passage 133 flows into the second seal chamber 122b via the gap B. All of the refrigerant gas flowing into the second seal chamber 122b is guided to the lip seal 10 along the outer peripheral surface 107d of the drive shaft 107, and passes through the vicinity of the lip seal 10. Other configurations are the same as those in the first embodiment.
As described above, even when the radial roller bearing 108 is disposed so as to rotatably support the drive shaft 107 with respect to the front housing 103, and the partition wall member 121 is disposed on the drive shaft 107, the same as in the first embodiment. Has an effect.

Embodiment 4 FIG.
Next, a variable capacity compressor according to Embodiment 4 of the present invention will be described with reference to FIG. The compressor according to the fourth embodiment is configured by using a partition member 221 described below instead of the partition member 21 in the first embodiment. In the following description, the same reference numerals as those in FIGS. 1 and 2 are the same or similar components, and detailed description thereof will be omitted.

  As shown in FIG. 5, an annular partition member 221 is provided at the front end of the lug plate 11, and the lug plate 11 and the partition member 221 are fixed so as to rotate as a unit. . The partition member 221 has an inner peripheral surface 221b that partitions the first seal chamber 22a. The inner peripheral surface 221b is formed on a tapered outer peripheral surface 7f that is a portion where the discharge refrigerant passage 33 of the drive shaft 7 opens. It is formed so that it may become taper-shaped along. That is, the first seal chamber 22a is formed by the inner peripheral surface 221b of the partition wall member 221 so that the passage cross-sectional area decreases from the discharge refrigerant passage side toward the gap A formed between the first seal chamber 22a and the drive shaft 7. It is in a partitioned state. Therefore, the refrigerant gas flowing into the first seal chamber 22a from the discharge refrigerant passage 33 is throttled by the tapered inner peripheral surface 221b of the partition wall member 221, and the second seal is interposed through the gap A while increasing the flow velocity. It flows into the chamber 22b. Other configurations are the same as those in the first embodiment.

  Thus, since the inner peripheral surface 221b of the partition wall member 221 is formed in a tapered shape, the flow rate of the refrigerant gas flowing into the second seal chamber 22b through the gap A is increased, and the refrigerant gas whose flow rate is increased Passes in the vicinity of the lip seal 10. Here, the lip seal 10 is heated by the heat generated at the sliding portion with the drive shaft 7, but since the flow rate of the refrigerant gas passing through the vicinity thereof is increased, the lip seal 10 is released from the lip seal 10 to the refrigerant gas. The amount of heat increases. Therefore, it becomes possible to reduce the heat generation of the lip seal 10, and the reliability of the lip seal 10 can be further improved.

Embodiment 5 FIG.
Next, a variable capacity compressor according to Embodiment 5 of the present invention will be described with reference to FIG. The compressor according to the fifth embodiment is configured by using a partition member 321 described below instead of the partition member 21 in the first embodiment. In the following description, the same reference numerals as those in FIGS. 1 and 2 are the same or similar components, and detailed description thereof will be omitted.

  As shown in FIG. 6, an annular partition member 321 is provided at the front end of the lug plate 11, and the lug plate 11 and the partition member 321 are fixed so as to rotate together. . Similar to the partition member 21 in the first embodiment, the partition member 321 divides the shaft seal chamber 22 into the first seal chamber 22a and the second seal chamber 22b via the gap A between the drive shaft 7 and the partition member 321. Yes. Further, the front end of the partition member 321 extends so as to cover the lip seal 10, and a tapered inner peripheral surface that is substantially parallel to the tapered outer peripheral surface 10 b of the lip seal 10 is provided therein. 321c is formed. A gap C is formed between the outer peripheral surface 10b of the lip seal 10 and the inner peripheral surface 321c of the partition wall member 321, and this gap C constitutes a guide passage. That is, the refrigerant gas that has flowed into the first seal chamber 22a through the discharge refrigerant passage 33 passes through the gap A and then flows into the second seal chamber 22b through the gap C. The refrigerant gas flowing into the gap C is blocked by the inner peripheral surface 321c of the partition wall member 321 and is prevented from diffusing outward in the radial direction, and all of the refrigerant gas is in the drive shaft 7 and the lip seal 10. Passes near the sliding part. Other configurations are the same as those in the first embodiment.

  As described above, the partition member 321 is provided with the gap C through which the refrigerant that has passed through the gap A flows along the outer peripheral surface 10b of the lip seal 10, so that all of the refrigerant guided to the lip seal 10 through the gap A is provided. Is blocked by the inner peripheral surface 321c of the partition wall member 321 and passes near the sliding portion between the drive shaft 7 and the lip seal 10 without diffusing radially outward. Therefore, it is possible to supply the lubricating oil more reliably to the sliding portion between the drive shaft 7 and the lip seal 10.

Embodiment 6 FIG.
Next, a compressor according to Embodiment 6 of the present invention will be described with reference to FIG. In the compressor according to the sixth embodiment, the configuration of the partition member 321 in the fifth embodiment is applied to the partition member 121 in the third embodiment shown in FIG. In the following description, the same reference numerals as those in FIGS. 1, 2, and 4 are the same or similar components, and thus detailed description thereof is omitted.

  As shown in FIG. 7, the drive shaft 107 is provided with an annular partition member 421 so as to cover the opening 133 a of the discharge refrigerant passage 133, and the drive shaft 107 and the partition member 421 rotate integrally. So that it is fixed. The partition member 421 divides the shaft seal chamber 122 into a first seal chamber 122a and a second seal chamber 122b through a gap D with the drive shaft 107, similarly to the partition member 121 in the third embodiment. A front end portion of the partition member 421 extends so as to cover the lip seal 10, and a tapered inner peripheral surface 421c is formed therein. Similar to the inner peripheral surface 321c of the partition wall member 321 in the fifth embodiment, the inner peripheral surface 421c has a substantially parallel tapered shape along the tapered outer peripheral surface 10b of the lip seal 10, and A gap C which is a guide passage is formed between the two. Other configurations are the same as those in the first embodiment.

  As described above, even when the partition member 421 is configured so as to be integrated with the drive shaft 107, the same effect as in the fifth embodiment is obtained.

In the first to sixth embodiments, the discharge refrigerant passage is provided at one place of the drive shaft, but the number thereof is not limited and can be provided at a plurality of places.
Of course, in the third to sixth embodiments, a slide bearing may be applied instead of the radial roller bearing as in the second embodiment.
In the fifth and sixth embodiments, the partition wall member covers the tapered outer peripheral surface of the seal member. However, the partition member is not limited to the part of the seal member covered by the partition wall member, and the outer periphery is parallel to the axial direction. It is also possible to cover up to the surface.
In the fifth and sixth embodiments, a portion of the inner peripheral surface of the partition wall member that divides the first seal chamber can be configured in a tapered shape as in the fourth embodiment.
In Embodiments 5 and 6, the inner peripheral surface of the partition member provided with the guide passage is formed in a taper shape substantially parallel to the outer peripheral surface of the seal member, but the outer peripheral surface of the seal member and the inner peripheral surface of the partition member are Is not limited to being parallel. Even if these are not parallel, they may be inclined so as to prevent the refrigerant from diffusing outward in the radial direction.

BRIEF DESCRIPTION OF THE DRAWINGS It is a cross-sectional side view which shows the variable capacity type compressor which concerns on Embodiment 1 of this invention. FIG. 3 is a partial enlarged cross-sectional side view showing the structure around the shaft seal chamber of the variable capacity compressor according to the first embodiment. It is a partial expanded sectional side view which shows the structure of the shaft seal chamber periphery of the variable displacement compressor which concerns on Embodiment 2 of this invention. It is a partial expanded sectional side view which shows the structure of the shaft seal chamber periphery of the variable capacity compressor which concerns on Embodiment 3 of this invention. It is a partial expanded sectional side view which shows the structure of the shaft seal chamber periphery of the variable capacity type compressor which concerns on Embodiment 4 of this invention. It is a partial expanded sectional side view which shows the structure of the shaft seal chamber periphery of the variable capacity compressor which concerns on Embodiment 5 of this invention. It is a partial expanded sectional side view which shows the structure of the shaft seal chamber periphery of the variable capacity compressor which concerns on Embodiment 6 of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Variable displacement type compressor, 3,103 Front housing (housing), 4,104 Crank chamber, 7,107 Drive shaft (rotary shaft), 8,108 Radial roller bearing (rotary shaft bearing), 10 Lip seal (seal member) , 11, 111 lug plate, 21, 121, 221, 321, 421 partition member, 22, 122 shaft seal chamber, 22a, 122a first seal chamber, 22b, 122b second seal chamber, 33, 133 discharge refrigerant passage, 51 Sliding bearing (rotating shaft bearing), A, B, D Clearance (guide passage), C Guide passage.

Claims (4)

A housing in which a crank chamber is formed;
A rotating shaft provided in the crank chamber and having at least one end exposed to the outside of the housing;
A lug plate fixed to the rotating shaft and rotating integrally with the rotating shaft;
A rotary shaft bearing that rotatably supports the rotary shaft with respect to the housing;
A seal member which is provided on the outer side of the rotary shaft bearing of the housing and prevents leakage of the refrigerant along the rotary shaft to the outside of the housing;
A shaft seal chamber which is a space defined by the housing, the rotary shaft, the lug plate, the rotary shaft bearing, and the seal member;
In the variable capacity compressor provided with the discharge refrigerant passage provided in the rotating shaft and guiding the refrigerant containing the lubricating oil to the shaft seal chamber,
A partition wall member is provided inside the shaft seal chamber to separate the shaft seal chamber into a first seal chamber on the discharge refrigerant passage side and a second seal chamber on the rotary shaft bearing and seal member side. ,
The partition member is provided with a guide passage for guiding all the refrigerant introduced from the discharge refrigerant passage into the first seal chamber to the seal member in the second seal chamber. .   The variable capacity compressor according to claim 1, wherein the partition member is disposed on the rotating shaft or the lug plate.   The variable capacity compressor according to claim 1 or 2, wherein the first seal chamber is partitioned by the partition member so that a cross-sectional area of the first seal chamber decreases from the discharge refrigerant passage side toward the guide passage side. .   The variable capacity compressor according to any one of claims 1 to 3, wherein the partition member is further provided with a guide passage through which the refrigerant that has passed through the guide passage flows along the outer peripheral surface of the seal member. .

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