WO2011080924A1

WO2011080924A1 - Lubricating oil supply structure of vane-type compressor

Info

Publication number: WO2011080924A1
Application number: PCT/JP2010/007589
Authority: WO
Inventors: 知靖高橋; 孝則寺屋
Original assignee: 株式会社ヴァレオジャパン
Priority date: 2009-12-29
Filing date: 2010-12-28
Publication date: 2011-07-07
Also published as: JP5707337B2; BR112012016134A2; CN102667162A; JPWO2011080924A1; EP2520802A1; EP2520802A4

Abstract

Disclosed is a lubricating oil supply structure of a vane-type compressor which uses the back-pressure chambers of the conventional cylinder configuration but which is capable of supplying sufficient lubricating oil even to a plain bearing distant from the oil resevoir by means of only a slight change in the shape of the recess formed on the cylinder-side end of the block which closes the cylinder. The shape and position of a first and a second recess (36, 37) formed in blocks (5, 6) are machined such that, if the disclosed lubricating oil supply structure (1) of a vane-type compressor has an oil supply path by which lubricating oil, after passing from an oil reservoir (19) through the first recess (36) and entering a back-pressure chamber (10), can pass from said back-pressure chamber (10) through the second recess (37) to arrive at a second bearing (12), then, when the stroke volume of a vane (9) is increased and the pressure in the back-pressure chamber (10) is relatively low, the first recess (36) and the back-pressure chamber (10) are made to communicate and lubricating oil is supplied to the back-pressure chamber (10) from the oil reservoir (19), and when the stroke volume of the vane (9) is decreased and the pressure in the back-pressure chamber (10) is relatively high, the second recess (37) and the back-pressure chamber (10) are made to communicate, and the lubricating oil in the back-pressure chamber (10) is drawn out and supplied to the second bearing (12).

Description

Lubricating oil supply structure for vane compressor

The present invention relates to a vane compressor mounted on an air conditioner such as a vehicle air conditioner, and more particularly to a structure for supplying lubricating oil to a bearing for supporting a drive shaft of the vane compressor.

In this type of vane type compressor, a cylinder closed by sandwiching both sides with a block, a rotor housed rotatably in the cylinder, and sliding in a plurality of vane grooves formed in the rotor. A vane and a drive shaft that is connected to the rotor and transmits a rotational force from the outside to the rotor. The drive shaft is supported by the both blocks via bearings, and A vane type compressor having a structure in which a plain bearing is used as a type of bearing is already known as disclosed in Patent Document 1, for example.

JP 2007-64163 A

However, in the vane type compressor shown in Patent Document 1, the oil reservoir chamber is provided in the vicinity of one side in the axial direction of the drive shaft, and the oil passes through the oil supply passage from the oil reservoir chamber to the drive shaft. When the storage space is reached and supplied to one of the sliding bearings and then supplied to the other sliding bearing through the back pressure chamber, the oil from the oil reservoir chamber is supplied to both sliding bearings without unevenness. Otherwise, there is a concern that any of the sliding bearings will be insufficiently lubricated and abnormal noise and wear of the sliding bearing will easily occur.

In particular, in a vane type compressor having a relatively small number of vanes, such as two, the number of back pressure chambers formed at the bottom of the vane groove of the rotor, and thus the flow path area connecting the vicinity of the front and rear bearings. Therefore, the amount of oil supplied to the sliding bearing that is further away from the sliding bearing closer to the oil reservoir chamber is reduced.

In this case, it may be possible to adopt a structure in which lubricating oil is supplied to a sliding bearing located far from the oil reservoir chamber through a path other than the back pressure chamber, but the number of processing steps is required to form the path. As a result, the manufacturing cost of the vane compressor increases. For this reason, in recent vane type compressors that attempt to limit the number of blocks constituting the outer shell of the vane type compressor in order to reduce the number of parts in order to reduce costs, an oil separate from the back pressure chamber is used. The structure for providing the supply path is more difficult to adopt.

Therefore, the present invention uses a back pressure chamber of a rotor having an existing structure, and is only a slight change in the shape of the recess formed on the cylinder side end surface of the block that closes the cylinder, and is far from the oil reservoir chamber. It is an object of the present invention to provide a lubricating oil supply structure for a vane compressor that can supply sufficient lubricating oil to a sliding bearing.

A lubricating oil supply structure for a vane compressor according to the present invention includes a cylinder closed on both sides by a block, a rotor housed in the cylinder and formed with a plurality of vane grooves, and a vane groove in the rotor. A vane whose side surface slides on the inner side surface of the vane groove and whose tip protrudes and retracts from the vane groove and slides on the inner peripheral surface of the cylinder, and a spine formed at the bottom of the vane groove. A pressure chamber, a drive shaft that is supported by the block via each bearing and connected to the rotor to transmit a rotational force from the outside to the rotor, and an oil reservoir chamber in which lubricating oil is temporarily stored. In the vane type compressor, the lubricating oil enters from the oil reservoir chamber between the drive shaft and one of the blocks, and flows along the axial direction of the drive shaft. Then, after lubricating one of the bearings located in the middle, the first recess formed in the cylinder side end surface of the one block, the back pressure chamber, and the cylinder side end surface of the other block of the block are formed. Lubricating oil that flows in the order of the second recesses, enters between the drive shaft and the other block, flows again along the axial direction of the drive shaft, and lubricates the other bearing located in the middle thereof The first concave portion and the second concave portion each have a path, and each change a communication state with the back pressure chamber as the position of the back pressure chamber varies due to rotation of the rotor. When the amount of protrusion of the vane from the vane groove of the rotor is the amount of stroke of the vane, the change in the state of communication with the back pressure chamber and the time when the amount of stroke of the vane increases Link before By relatively lower than the surrounding pressure in the back pressure chamber, it is characterized in that as the lubricating oil is supplied to the back pressure chamber (claim 1). Here, when the bearing is a sliding bearing such as a plain bearing, the effects of the present invention can be enjoyed more effectively. Further, even if the cylinder is closed on both sides by a block integral with the cylinder and a block separate from the cylinder, both sides are closed by blocks separate from the cylinder. Also good. The change in the communication state with the back pressure chamber includes opening / closing of the communication state with the back pressure chamber and expansion / reduction of the communication region with the back pressure chamber. The same applies to the following vane type compressors.

As a result, the flow rate of the lubricating oil when it is sent from the back pressure chamber to the gap between the block that closes the drive shaft and the cylinder is the other block of the block that closes the drive shaft and the cylinder. In order to increase the flow rate of the lubricating oil when being fed into the back pressure chamber through the gap between the first and second recesses, the open / close state of the communication with the back pressure chamber and the communication area By setting the expansion / contraction, the flow rate of the lubricating oil delivered from the back pressure chamber to the gap between the drive shaft and the other block among the blocks closing the cylinder increases in accordance with the difference.

In particular, the lubricating oil supply structure of the vane type compressor according to the second aspect of the invention includes a timing when the space between the first recess and the back pressure chamber is opened, the second recess and the back. When the space between the pressure chamber and the back pressure chamber is opened, a shift occurs between the first recess and the back pressure chamber, and between the second recess and the back pressure chamber. It is characterized in that lubricating oil is supplied to the back pressure chamber by linking the deviation and the timing when the stroke amount of the vane increases. More specifically, when the stroke amount of the vane increases, the interval between the first recess and the back pressure chamber is opened earlier than between the second recess and the back pressure chamber. (Claim 3).

As a result, when the amount of stroke of the vane increases, the volume of the back pressure chamber at the bottom of the vane groove increases, and the pressure in the back pressure chamber decreases relatively. When the opening time and the time when the stroke amount of the vane increases, the lubricating oil is supplied from the oil reservoir chamber to the back pressure chamber through the first recess.

The lubricating oil supply structure for a vane compressor according to the present invention includes a cylinder closed on both sides by a block, a rotor housed in the cylinder and formed with a plurality of vane grooves, and a vane of the rotor The vane is housed in the groove, and the side surface slides on the inner surface of the vane groove, and the tip of the vane slides on the inner peripheral surface of the cylinder with the tip protruding and retracting from the vane groove. A back pressure chamber, a drive shaft that is supported by the block via bearings and is connected to the rotor and transmits a rotational force from the outside to the rotor, and an oil reservoir chamber in which lubricating oil is temporarily stored The lubricating oil enters from the oil reservoir chamber between the drive shaft and one of the blocks, and follows the axial direction of the drive shaft. And lubricate one of the bearings located in the middle of the first concave portion formed in the cylinder side end surface of the one block, the back pressure chamber, and the cylinder side end surface of the other block of the block. It flows in the order of the formed second recesses, enters between the drive shaft and the other block, flows again along the axial direction of the drive shaft, and lubricates the other bearing located in the middle thereof A lubricating oil path is provided, and the first recess and the second recess change the communication state with the back pressure chamber as the position of the back pressure chamber varies as the rotor rotates. When the amount of protrusion of the vane from the vane groove of the rotor is the amount of stroke of the vane, the change in the state of communication with the back pressure chamber and the amount of stroke of the vane decrease. And link By raising relatively than ambient pressure in said back pressure chamber, it is characterized in that as the lubricating oil is sent from the back pressure chamber (claim 4).

In particular, the lubricating oil supply structure of the vane type compressor according to the invention of claim 5 includes a timing when the space between the first recess and the back pressure chamber is closed, the second recess and the back pressure. A gap between the first recess and the back pressure chamber and between the second recess and the back pressure chamber. Lubricating oil is sent out from the back pressure chamber by linking the deviation with the timing when the stroke amount of the vane decreases. More specifically, when the stroke amount of the vane decreases, the gap between the first recess and the back pressure chamber is closed earlier than between the second recess and the back pressure chamber. (6).

As a result, when the stroke amount of the vane is decreasing, the volume of the back pressure chamber at the bottom of the vane groove is relatively reduced and the pressure in the back pressure chamber is relatively increased. When the timing when only the oil groove is opened and the timing when the stroke amount of the vane decreases, the lubricating oil existing in the back pressure chamber is sent from the back pressure chamber to the second recess side. And supplied to the vicinity of the bearing of the other block.

Further, in the lubricating oil supply structure for a vane compressor according to the invention of claim 7 in particular, at least one of the first recess and the second recess is arranged in a lateral width direction of the vane compressor. The driving shaft is divided into a portion having a relatively deep depth in the axial direction and a portion having a relatively shallow depth, and the communication state with the back pressure chamber is changed using the difference in depth. The depth of the entire region of the first concave portion or the second concave portion which is not classified into a relatively deep portion and a relatively shallow portion in the axial direction of the drive shaft is the depth of the entire region. The depth of the relatively deep part of the concave part divided into a shallow part and a narrow part is the same (claim 8).

As a result, the lubricating oil is mainly fed into the back pressure chamber from the first concave portion side, and the lubricating oil is similarly sent from the back pressure chamber to both the first concave portion and the second concave portion. And a pattern in which the lubricating oil is mainly fed from the first recess side to the back pressure chamber and the lubricating oil is mainly sent from the back pressure chamber to the second recess. Similarly, a pattern is formed in which lubricating oil is similarly fed from the recess side and the lubricating oil is mainly sent from the back pressure chamber to the second recess, so the drive shaft and cylinder are closed from the back pressure chamber. The flow rate of the lubricating oil when it is sent to the gap with the other block among the blocks to be moved is when it is fed into the back pressure chamber through the gap between the block that blocks the drive shaft and the cylinder. From the back pressure chamber to the drive shaft and cylinder The flow rate of lubricating oil to be delivered to the gap between the other blocks of the blocks that closes increases with the difference.

As described above, according to the present invention, the flow rate of the lubricating oil that is sent from the back pressure chamber to the gap between the block that blocks the drive shaft and the cylinder blocks the drive shaft and the cylinder. The first recess and the second recess with respect to the back pressure chamber so that the flow rate of the lubricating oil is larger than the flow rate of the lubricating oil when it is fed into the back pressure chamber from the gap with the other blocks of the blocks to be Set the open / close of the communication state and expansion / contraction of the communication area according to the timing of increase / decrease of the stroke amount of the vane, and send it from the back pressure chamber to the gap between the block that blocks the drive shaft and the cylinder The flow rate of the lubricating oil can be increased according to the difference. Therefore, even when the number of back pressure chambers at the bottom of the vane groove is small and the flow path area is small, the lubricating oil is surely and sufficiently supplied to the other bearing located farther from the oil reservoir than one bearing. Can be supplied in quantity. Therefore, it is possible to suppress the occurrence of noise or wear in the other bearing due to the lack of lubricating oil with respect to the other bearing, thereby improving the durability of the bearing and thus the vane compressor. It becomes possible.

In particular, according to the second and third aspects of the invention, when the stroke amount of the vane increases, the volume of the back pressure chamber at the bottom of the vane groove increases, and the pressure in the back pressure chamber increases. Therefore, when the timing when only the first recess is opened and the timing when the stroke of the vane increases, the first recess is removed from the oil reservoir chamber for the lubricating oil. It can be supplied to the back pressure chamber. In particular, according to the invention described in claim 4 and claim 5, when the stroke amount of the vane decreases, the volume of the back pressure chamber at the bottom of the vane groove is relatively reduced, Since the pressure in the back pressure chamber rises relatively, if the time when only the second recess is opened and the time when the stroke of the vane decreases, the lubricating oil present in the back pressure chamber Can be fed from the back pressure chamber to the second recess side and supplied to the vicinity of the bearing of the other block. As a result, it is possible to suppress the occurrence of abnormal noise or wear in the other bearing due to the lack of lubricating oil for the other bearing, and to improve the durability of the bearing and thus the vane compressor. Is possible.

In particular, according to the invention described in claims 7 and 8, the lubricating oil is mainly fed into the back pressure chamber from the first recessed portion side, and the first recessed portion and the second recessed portion are fed from the back pressure chamber. Similarly, the lubricating oil is sent to both sides, and the lubricating oil is mainly fed into the back pressure chamber from the first concave portion side, and the lubricating oil is mainly fed from the back pressure chamber to the second concave portion. And a pattern in which the lubricating oil is similarly fed into the back pressure chamber from both concave portions, and the lubricating oil is mainly fed from the back pressure chamber to the second concave portion. The For this reason, the flow rate of the lubricating oil when it is sent from the back pressure chamber to the gap between the block that blocks the drive shaft and the cylinder is the other block of the block that blocks the drive shaft and the cylinder. The flow rate of the lubricating oil when it is fed into the back pressure chamber from the clearance between the drive shaft and the other block among the blocks that block the cylinder is sent from the back pressure chamber. The flow rate of the lubricating oil increases according to the difference. As a result, it is possible to suppress the occurrence of abnormal noise or wear in the other bearing due to the lack of lubricating oil for the other bearing, and to improve the durability of the bearing and thus the vane compressor. Is possible. *

FIG. 1 is a cross-sectional view showing the overall configuration of a vane compressor according to the present invention. FIG. 2 shows the state of the front block in the axial direction of the drive shaft constituting the vane type compressor according to the first embodiment of the present invention when the side having the second recess is viewed from the rear side. It is explanatory drawing which shows only the 1st recessed part of the block of the axial direction back of the drive shaft which comprises a vane type compressor with a broken line. FIG. 3 is an explanatory view showing a state in which the concave portion on the side having the oil reservoir chamber is opened earlier than the concave portion on the opposite side in Embodiment 1 of the present invention, and FIG. FIG. 3B is a cross-sectional view of the drive shaft cut in the radial direction, and FIG. 3B is a cross-sectional view taken along line AA of FIG. FIG. 4 is an explanatory view showing a state in which both concave portions are opened in Embodiment 1 of the present invention, and FIG. 4 (a) is a sectional view of the rotor cut in the radial direction of the drive shaft. FIG. 4B is a cross-sectional view taken along the line BB of FIG. FIG. 5 is an explanatory view showing a state in which the concave portion on the side having the oil reservoir chamber is not closed yet in FIG. 5 (a). FIG. 5 (a) shows the rotor in the radial direction of the drive shaft. FIG. 5B is a sectional view taken along the line CC in FIG. 5A. FIG. 6 is an explanatory view showing a state in which the concave portion on the side having the oil reservoir chamber is closed earlier than the concave portion on the opposite side in Embodiment 1 of the present invention, and FIG. FIG. 6B is a cross-sectional view taken along the radial direction of the drive shaft, and FIG. 6B is a cross-sectional view taken along the line DD of FIG. FIG. 7 is a cross-sectional view taken along the line XX of FIG. 1 for the vane type compression in the first example of the second embodiment of the present invention. FIG. 8 is a cross-sectional view taken along the line YY of FIG. 1 for the vane type compressor according to the first embodiment of the second embodiment of the present invention. FIG. 9 shows a case where lubricating oil is supplied to the back pressure chamber in the first example of Embodiment 2 of the present invention. FIG. 9A shows the rotor cut in the radial direction of the drive shaft. 9C is a cross-sectional view of the driven shaft viewed from the axial direction rearward of the drive shaft, and FIG. 9C is a cross-sectional view of the state of the rotor cut in the radial direction of the drive shaft viewed from the axial front of the drive shaft. FIG. 9B is a cross-sectional view taken along line EE of FIGS. 9A and 9C. FIG. 10 shows a case where the lubricating oil is delivered from the back pressure chamber in the first example of the second embodiment of the present invention. FIG. 10 (a) shows the rotor cut in the radial direction of the drive shaft. FIG. 10C is a cross-sectional view of the rotor as viewed from the front in the axial direction of the drive shaft, with the rotor cut in the radial direction of the drive shaft. FIG. 10B is a cross-sectional view taken along the line FF of FIGS. 10A and 10C. FIG. 11 shows a case where lubricating oil is supplied to the back pressure chamber in the second example of the second embodiment of the present invention. FIG. 11A shows the rotor cut in the radial direction of the drive shaft. FIG. 11C is a cross-sectional view of the rotor cut in the radial direction of the drive shaft as viewed from the front in the axial direction of the drive shaft. FIG. 11 (b) is a cross-sectional view taken along the line GG of FIGS. 11 (a) and 11 (c). FIG. 12 shows a case where lubricating oil is delivered from the back pressure chamber in the second example of the second embodiment of the present invention. FIG. 12 (a) shows the rotor cut in the radial direction of the drive shaft. FIG. 12C is a cross-sectional view of the rotor cut in the radial direction of the drive shaft as viewed from the front in the axial direction of the drive shaft. FIG. 12B is a cross-sectional view taken along the line HH of FIGS. 12A and 12C. FIG. 13 shows a case where lubricating oil is supplied to the back pressure chamber in the third example of Embodiment 2 of the present invention. FIG. 13 (a) shows the rotor cut in the radial direction of the drive shaft. FIG. 13C is a cross-sectional view of the rotor cut in the radial direction of the drive shaft as viewed from the front in the axial direction of the drive shaft. FIG. 13 (b) is a cross-sectional view taken along the line II of FIG. 13 (a) and FIG. 13 (c). FIG. 14 shows a case where lubricating oil is delivered from the back pressure chamber in the third example of Embodiment 2 of the present invention. FIG. 14 (a) shows the rotor cut in the radial direction of the drive shaft. 14C is a cross-sectional view of the driven shaft viewed from the rear in the axial direction of the drive shaft, and FIG. 14C is a cross-sectional view of the rotor cut in the radial direction of the drive shaft viewed from the front in the axial direction of the drive shaft. FIG. 14B is a cross-sectional view taken along line JJ of FIGS. 14A and 14C.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

1 to 6 show the whole or a part of the configuration of an example of a vane type compressor 1 that can use the lubricating oil supply structure according to the present invention.

This vane type compressor 1 is suitable for a refrigeration cycle using, for example, a refrigerant as a working fluid, and is used for a vehicle air conditioner or the like. Further, as shown in FIG. 1, the vane compressor 1 includes a drive shaft 2, a rotor 3 fixed to the drive shaft 2 and movable as the drive shaft 2 rotates, and the rotor 3. It has a block 5 and a block 6 that define a compression space 4 to be described later, and the block 5 and the block 6 constitute a housing that houses the drive shaft 2, the rotor 3, and the like. .

Among these, the block 6 is a cylinder 6a for housing the rotor 3, and this cylinder 6a is located on the rear side in the axial direction of the drive shaft 2, and the rear side block 6b integrally formed with the cylinder 6a; Consists of. The cylinder 6a is opened to the block 5 side as shown in FIG. 3 (b), FIG. 4 (b), FIG. 5 (b) and FIG. The cylinder hole 6c is provided.

The block 5 includes a front side block 5a that abuts a front side end face located in front of the drive shaft 2 in the axial direction of the cylinder 6a, and a cylinder 6a of the block 6 extending from the front side block 5a in the axial direction of the drive shaft 2. And a shell 5b surrounding the outer peripheral surface of the rear block 6b. The block 5 is connected to the block 6 via a connector 7 such as a bolt. Further, a plurality of O-rings 11 are interposed between the shell 5b of the block 5 and the outer peripheral surfaces of the cylinder 6a and the rear side block 6b of the block 6 and are fixed with good airtightness. Furthermore, the block 5 is formed with a boss portion 5c extending from the front side block 5a along the axial direction of the drive shaft 2 to the opposite side of the shell 5b. A pulley (not shown) for transmitting the rotation is externally rotatably mounted, and rotational power is transmitted from the pulley to the drive shaft 2 via an electromagnetic clutch (not shown).

The rotor 3 is rotatably accommodated in a cylinder hole 6c formed in the cylinder 6a of the block 6, and includes a rotor body 3a fixed to the drive shaft 2 and a plurality of (provided to the rotor body 3a ( In this embodiment, there are a plurality of (two in this embodiment) vanes 9 inserted into the two vane grooves 8. The vane groove 8 is opened not only in the cylinder hole 6c of the block 6, but also on the front side block 5a side of the block 5 and the rear side block 6b side of the block 6, and on the far side in the sliding direction of the vane 9. A back pressure chamber 10 is formed at the bottom. Therefore, the back pressure chamber 10 is also opened to the front block 5 a side of the block 5 and the rear block 6 b side of the block 6. The vane 9 has a side surface that slides on the inner surface of the vane groove 8 and a tip that protrudes and protrudes from the vane groove 8 and slides on the inner peripheral surface of the cylinder 6a. In this case, the amount of protrusion of the vane 9 from the vane groove 8 is defined as the stroke amount.

The drive shaft 2 is rotatably supported by the front side block 5a of the block 5 and the rear side block 6b of the block 6 via plain bearings 12 and 13, respectively. However, the bearings are not limited to the plain bearings 12 and 13 as long as the bearings require supply of lubricating oil. The drive shaft 2 has a seal member 14 interposed between the inner peripheral surface of the block 5 in the vicinity of the base end of the boss portion 5c of the block 5, and the working fluid is exposed to the outside from the opening of the boss portion 5c. Prevents leakage.

The block 5 is formed with a suction port 16 and a discharge port 17 for the working fluid, and a space 18 is formed on the radially inner side of the drive shaft 2 with respect to the suction port 16. A suction space (low pressure space) 15 is defined by the space portion 18 and a hollow portion 22 formed in the cylinder 6a of the block 6 and opened to the block 5 side. Further, a discharge space (high pressure space) 24 is defined by the cylinder 6 a of the block 6 and the shell 5 b of the block 5, and this discharge space 24 communicates with the discharge port 17. Further, an oil separator 25 is disposed between the discharge space 24 and the discharge port 17, and the oil separated from the working fluid by the oil separator 25 is temporarily stored in an oil reservoir chamber 19 described later. .

When the rotor body 3a of the rotor 3 and the cylinder hole 6c of the cylinder 6a are viewed as a cross section in which the cylinder 6a is cut in the radial direction of the drive shaft 2 and the end face of the rotor body 3a faces the opening of the cylinder hole 6c, FIG. 3 (a), FIG. 4 (a), FIG. 5 (a) and FIG. 6 (a), the rotor body 3a has an axial center P1 of the cylinder hole 6c. The rotor body 3a is accommodated in the cylinder hole 6c so as to be displaced toward the suction port 16 and the discharge port 17 as compared with the center P2. This deviation is, for example, ½ of the difference between the inner diameter of the cylinder hole 6c and the outer diameter of the rotor body 3a.

As a result, the outer peripheral surface of the rotor body 3a is in contact with the inner peripheral surface of the cylinder hole 6c at a predetermined distance in a predetermined range in a predetermined range, and the outer peripheral surface of the rotor body 3a and the cylinder hole 6c A compression space 4 is defined between the two. Further, the compression space 4 is divided into a plurality of compression chambers 21 by being partitioned by the vanes 9. The volume of each compression chamber 21 changes with the rotation of the rotor 3.

Further, although not shown, a discharge port communicating with the discharge space 24 is provided on the inner peripheral surface of the cylinder hole 6c. For this reason, when the cylinder 6a of the block 6 is fitted in the shell 5b of the block 5, both ends of the cylinder 6a are in the axial direction of the drive shaft 2 of the cylinder 6a between the outer peripheral surface of the cylinder 6a and the inner peripheral surface of the shell 5b. A discharge space 24 defined by flanges 26 and 27 projecting in the radial direction of the drive shaft 2 from both ends is formed, and the discharge space 24 can communicate with the compression space 4 through a discharge port. The discharge port is opened and closed by a discharge valve (not shown) accommodated in the discharge space 24.

With the above configuration, the operation of suction, compression, and discharge of the working fluid in the vane compressor 1 is as follows. That is, when rotational power from a power source (not shown) is transmitted to the drive shaft 2 via a pulley and an electromagnetic clutch and the rotor 3 rotates, the working fluid flowing into the suction space 15 from the suction port 16 passes through the suction port. Inhaled into the compression space 4. Since the volume of the compression chamber 21 partitioned by the vanes 9 in the compression space 4 changes according to the rotation of the rotor 3, the working fluid confined between the vanes 9 is compressed and is discharged from a discharge port (not shown). It discharges to the discharge space 24 through a discharge valve (not shown). The working fluid discharged into the discharge space 24 moves in the circumferential direction along the outer peripheral surface of the cylinder 6a. After that, oil is separated by the oil separator 25 and then discharged from the discharge port 17 to the external circuit.

By the way, the vane compressor 1 further includes a lubricating oil supply structure for supplying the oil in the oil reservoir chamber 19 to the plain bearings 12 and 13 as a lubricant. As this lubricating oil supply structure, the oil reservoir chamber 19 is the starting point. A relay passage 30 connecting the drive shaft storage space 29 storing the drive shaft 2 in the rear side block 6b of the block 6 and the oil reservoir chamber 19 is provided. The rear block 6b of the block 6 is provided. In this embodiment, the downstream opening of the relay passage 30 opens below the end of the drive shaft 2 of the drive shaft storage space 29 or below the end of the drive shaft 2.

The drive shaft storage space 29 is a hole that extends along the axial direction of the drive shaft 2 in the rear side block 6b of the block 6 and extends along the axial direction. It is approximately equal to the outer diameter of the mounted state. The plain bearing 13 is mounted on the rear side block 6b in the main portion of the drive shaft storage space 29 that is in front of the opening of the relay passage 30.

Further, as a lubricating oil supply structure, there is provided a drive shaft storage space 31 for storing the drive shaft 2 in the front side block 5a of the block 5. The drive shaft storage space 31 is a hole extending along the axial direction of the block 5 so as to surround the outer periphery of the drive shaft 2 and reaches the opening of the boss portion 5c. A seal chamber 32 for housing the member 14 is provided. The inner diameter dimension of the portion of the drive shaft housing space 31 behind the seal chamber 32 is substantially equal to the outer diameter dimension of the drive shaft 2 with the plain bearing 12 mounted. The plane bearing 12 is mounted on the front block 5a in the portion of the drive shaft storage space 31 that is behind the seal chamber 32.

The plain bearings 12 and 13 are cylindrical, and the inner diameter is slightly larger than the outer diameter of the drive shaft 2. As a result, when the plain bearings 12 and 13 are mounted on the blocks 5 and 6, as shown in FIGS. 3B, 4B, 5B, and 6B, driving is performed. Lubricating oil supply passages 33 and 34 are formed in an annular shape between the outer peripheral surface of the shaft 2 and the inner peripheral surfaces of the plain bearings 12 and 13.

The lubricating oil supply passages 33 and 34 are connected to the first and second recesses 36 and 37 and the back pressure chamber 10 defined on the bottom side of the vane groove 8 as will be described in detail later. It is possible to communicate with each other.

The first recess 36 is located axially forward (rotor 3 side) of the drive shaft 2 relative to the plain bearing 13 with respect to the drive shaft storage space 29 provided in the rear side block 6 b of the block 6. The second recess 37 is formed so as to be continuous with the space 29, and is axially rearward of the drive shaft 2 with respect to the drive shaft storage space 31 provided in the front side block 5 a of the block 5 (in the axial direction of the drive shaft 2). It is located on the rotor 3 side) and is formed to be continuous with the drive shaft storage space 31. The first recess 36 and the second recess 37 are provided in the rear block 6 b of the block 6 or the front block 5 a of the block 5.

Further, the first recess 36 and the second recess 37 have the same shape, and are in a positional relationship shifted from each other by rotating at a predetermined angle with the axis P1 of the drive shaft 2 as the rotation center. Accordingly, the shape of the second recess 37 will be described with reference to FIG. 2. The circular line L1 constituting the circular opening edge of the drive shaft storage space 31 is used as the inner edge as it is, and the drive is performed from the circular line L1. A communication state forming portion 37a that extends radially outward of the shaft 2 and that has a relatively large radial dimension of the drive shaft 2 and a communication state formation in which the radial dimension of the drive shaft 2 is smaller than the communication state forming portion 37a. It has a shape having a non-corresponding portion 37b. The dimension of the arcuate line L2 forming the arcuate outer edge of the communication state forming portion 37a is, for example, substantially the same as the dimension of the bottom surface position of the vane 9 when the vane 9 has the minimum stroke amount. The dimension of the arcuate line L3 that forms the arcuate outer edge of the communication state non-corresponding portion 37b is smaller than the position of the back pressure chamber 10 on the drive shaft 2 side. That is, the dimension of the arc-shaped line L3 that forms the arc-shaped outer edge of the communication state formation non-corresponding portion 37b is a dimension that does not communicate with the back pressure chamber 10. Furthermore, both ends of the arcuate line L2 and both ends of the arcuate line L3 are connected by straight lines L4 and L5 extending radially from the axis P1 of the drive shaft 2 in this embodiment.

The first concave portion 36 will also be described with reference to FIG. 2. The circular line L1 constituting the circular opening edge of the drive shaft storage space 29 is used as an inner edge as it is, and the circular line L1 is used to drive the drive shaft 2. While expanding radially outward, it has a shape having a communication state forming portion 36a and a communication state non-corresponding portion 36b. The dimension of the arcuate line L2 forming the arcuate outer edge of the communication state forming portion 36a is, for example, substantially the same as the dimension of the bottom surface position of the vane 9 when the vane 9 is at the minimum stroke amount. The dimension of the arcuate line L3 that forms the arcuate outer edge of the communication state formation non-corresponding portion 36b is smaller than the position of the back pressure chamber 10 on the drive shaft 2 side. That is, the dimension of the arcuate line L3 forming the arcuate outer edge of the communication state non-corresponding portion 36b is a dimension that does not communicate with the back pressure chamber 10. Furthermore, both ends of the arcuate line L2 and both ends of the arcuate line L3 of the communication state non-corresponding portion 36b are connected by two straight lines L4 and L5 extending radially from the axis P1 of the drive shaft 2 in this embodiment. Has been.

A point X2 is provided in front of the rotor 3 in the rotation direction with respect to a point X1 that contacts the outer peripheral surface of the rotor body 3a of the rotor 3 and the inner peripheral surface of the cylinder hole 6c with a minimum clearance, and the tip of the vane 9 is set to X2. The straight line L5, S1 is set so that the back pressure chamber 10 at the bottom of the vane groove 8 becomes the boundary between the communication state forming part 36a and the communication state non-corresponding part 36b of the first recess 36. Form. The positional relationship is set such that the boundary line S2 of the second recess is further shifted by a predetermined angle forward along the rotational direction of the rotor body 3a.

As a result, the rotor body 3a rotates clockwise, and the back pressure chamber 10 of the vane 9 rotates clockwise about the axis P1 of the drive shaft 2 as a result. 3, in the range from the extension line S1 to the extension line S2, the first recess 36 communicates with the communication state forming part 36a, but the relationship with the second recess 37 does not correspond to the communication state formation. After being blocked by the part 36b, as shown in FIG. 4, the extension line S2 is crossed so that both the first concave part 36 and the second concave part 37 are in the communication state forming parts 36a and 37a. It becomes a state of communication. However, after the back pressure chamber 10 is in the open state of the first recess 36 that has previously communicated only with the communication state forming portion 36 a of the first recess 36, the communication state forming portion of the second recess 37. Communicating with 37a, the 2nd crevice 37 will also be in an open state.

When the back pressure chamber 10 is located within the extension line S2 from the extension line S1, the stroke amount of the vane 9 positioned in front of the contact point X1 increases. As a result, the pressure in the back pressure chamber 10 is relatively lowered as compared with the surroundings. For this reason, the lubricating oil that has entered the relay passage 30 and the drive shaft storage space 29 from the oil reservoir chamber 19 passes through the lubricating oil supply passage 34 between the plain bearing 13 and the drive shaft 2, and then the first recess 36. It is possible to reliably reach the back pressure chamber 10 through the communication state forming portion 36a.

Furthermore, a point X3 is provided on the rear side in the rotational direction of the rotor 3 with respect to the contact point X1 between the outer peripheral surface of the rotor body 3a of the rotor 3 and the inner peripheral surface of the cylinder hole 6c, and the tip of the vane 9 becomes X3. When in the position, straight lines L4, S4 are arranged so that the back pressure chamber 10 at the bottom of the vane groove 8 becomes a boundary between the communication state forming part 37a and the communication state non-corresponding part 37b of the second recess 37. Form. The positional relationship is set so that the boundary line S3 of the first recess is further shifted by a predetermined angle forward along the rotational direction of the rotor body 3a.

As a result, the rotor body 3a rotates clockwise, and the back pressure chamber 10 of the vane 9 rotates clockwise about the axis P1 of the drive shaft 2 as a result. As shown in FIG. 5, before the extension line S4 is exceeded, the state where the first concave portion 36 and the second concave portion 37 communicate with each other at the communication state forming portions 36a and 37a is maintained. In the range from the extension line S3 to the extension line S4 beyond the extension line S4, the second recess 37 communicates with the communication state forming portion 37a, and the relationship with the first recess 36 does not correspond to the communication state formation. It becomes what was obstruct | occluded in 36b, and since the extension line S3 is exceeded, it will be obstruct | occluded by the communication state formation non-corresponding | compatible part 37b also about the 2nd recessed part 37. However, since the back pressure chamber 10 is first closed with the first recessed portion 36 at the communication state non-corresponding portion 36b, the second recessed portion is closed after the communication state with the first recessed portion 36 is closed. 37 is closed at the communication state non-corresponding portion 37b, and the communication state with the second recess 37 is also closed.

In addition, when the back pressure chamber 10 is located within the extension line S4 from the extension line S3, the stroke amount of the vane 9 located behind the contact point X1 is decreased. Is reduced, and the pressure in the back pressure chamber 10 is relatively increased compared to the surroundings. For this reason, at least the lubricating oil in the back pressure chamber 10 can surely reach the plain bearing 12 through the communication state forming portion 37 a of the second recess 37.

7 to 14 show a part of the configuration of a plurality of examples of the embodiment 2 of the vane compressor 1 that can use the lubricating oil supply structure according to the present invention. Hereinafter, the first example to the third example of the second embodiment of the vane compressor will be described with reference to FIGS. 7 to 14. However, since the overall configuration of the vane compressor 1 is the same as the configuration shown in FIG. 1 of the first embodiment, it is not particularly shown, and the description thereof is omitted, which is different from the first embodiment of the second embodiment. The first concave portion 36 and the second concave portion 37, which are parts, are basically described, and the same reference numerals are given to the same components as those in the first embodiment, and the description thereof is omitted.

(First example)
7 to 10 show a first example of the embodiment 2 of the vane type compressor 1 that can use the lubricating oil supply structure according to the present invention.

The second recess 37 shown in the first example of the second embodiment is provided in the front side block 5a of the block 5, and is provided in the drive shaft storage space 31 provided in the front side block 5a of the block 5. On the other hand, it is located behind the plain bearing 13 in the axial direction of the drive shaft 2 (on the rotor 3 side) and is formed to be continuous with the drive shaft storage space 31. Then, as shown in FIG. 7, the second recess 37 has a circular line L1 constituting the circular opening edge of the drive shaft storage space 31 as an inner edge, and is a circle concentric with the circular line L1. A shape line L6 is used as an outer edge, and the shape extends from the circular line L1 to the outside in the radial direction of the drive shaft 2 with the same dimensions throughout the entire circumference. The dimension of the circular line L6 that forms the circumferential outer edge of the second recess 37 is, for example, substantially the same as the dimension of the bottom surface position of the vane 9 at the time of the minimum stroke amount of the vane 9.

And the 2nd recessed part 37 has the recessed deep part 37c and the recessed shallow part 37d, as FIG.7, FIG.9 and FIG.10 shows. As shown in FIGS. 9A and 10A, the recessed deep portion 37c and the recessed shallow portion 37d are formed with respect to the second recessed portion 37 with respect to the axis P1 of the rotor body 3a and the cylinder hole 6c. It is divided by two boundary lines S5 and S6 extending along a straight line passing through both of the centers P2, and the axial depth of the drive shaft of the recessed portion 37c is the axial direction of the drive shaft of the recessed shallow portion 37d. Is greater than the depth of. As a result, when the opening on the front block 5a side of the back pressure chamber 10 is within a range facing the concave portion 37c of the second concave portion 37, the communication area through which the lubricating oil passes through the second concave portion 37 is When it is relatively expanded and the opening on the front side block 5a side of the back pressure chamber 10 is in a range facing the concave shallow portion 37d of the second concave portion 37, the lubricating oil passes through the second concave portion 37. The communication area is relatively reduced.

Further, the first recess 36 shown in the first example of the second embodiment is provided in the rear side block 6b of the block 6, and with respect to the drive shaft storage space 29 provided in the rear side block 6b. The drive shaft 2 is positioned in front of the plain bearing 13 in the axial direction (on the rotor 3 side), and is formed so as to be continuous with the drive shaft storage space 29. As shown in FIG. 8, the first recess 36 has a circular line L1 constituting the circular opening edge of the drive shaft storage space 29 as an inner edge, and is a circle that is concentric with the circular line L1. A shape line L6 is used as an outer edge, and the shape extends from the circular line L1 to the outside in the radial direction of the drive shaft 2 with the same dimensions throughout the entire circumference. The dimension of the circular line L6 that forms the circumferential outer edge of the first recess 36 is, for example, substantially the same as the dimension of the bottom surface position of the vane 9 when the vane 9 is at the minimum stroke amount.

The first recess 36 is different from the second recess 37 in that the axial depth of the drive shaft is the same in the entire area as shown in FIGS. 9C and 10C. ing. Further, the depth dimension of the first recess 36 is the same as the axial depth of the drive shaft of the recess depth portion 37 c of the second recess 37. Thereby, even if the opening on the rear block 6b side of the back pressure chamber 10 is opposed to any range of the first recess 36, the communication area through which the lubricating oil passes through the first recess 36 is relatively expanded. It is in the state.

9A and 10A, the point where the boundary line S5 and the inner peripheral surface of the cylinder hole 6c intersect is defined as X5, and the boundary line S6 and the inner periphery of the cylinder hole 6c. The point where the plane intersects is X6, and the rotation direction of the rotor 3 is opposite to that shown in the arrows in FIGS. 9 (a) and 10 (a) when viewed from the front side of the vane compressor 1. In the case of clockwise rotation as shown by the arrows in FIGS. 9 (c) and 10 (c) as viewed from the rear side of the vane compressor 1, X5 is the starting point. In the range where X6 is the end point, as indicated by the thick arrow in FIG. 9B, the stroke amount that the vane 9 protrudes from the vane groove 8 beyond the outer surface of the rotor 3 is increased. In the range where X5 is the end point, the thick line arrow in FIG. As shown, the timing at which the stroke amount of the vane 9 is gradually retracted from the outer surface of the rotor 3 in the vane groove 8 decreases. A straight line connecting X5 and X6, which divides the timing when the stroke amount of the vane 9 increases or decreases, is the same as the boundary line S5 and the boundary line S6.

Thus, the timing when the opening on the front block 5a side of one back pressure chamber 10 and the shallow shallow portion 37d of the second recess 37 face each other and the timing when the stroke amount of the vane 9 increases. Therefore, as shown in FIG. 9B, the volume of the back pressure chamber 10 is expanded by the vane 9 sliding in the vane groove 8 in the direction of increasing the stroke amount. The pressure in the back pressure chamber 10 is relatively lower than the lubricating oil supply passages 33 and 34, and the back pressure chamber 10 is supplied with the lubricating oil from the lubricating oil supply passages 33 and 34. Since the back pressure chamber 10 communicates with the back pressure chamber 10 through a shallow shallow portion 37d, the communication area between the second recess 37 and the back pressure chamber 10 is relatively reduced. (B) Lubrication oil from the lubrication oil supply passage 33 to the back pressure chamber 10 An amount of an arrow and a lubricating oil supply passage 34 that represent as indicated by the arrow representing the amount of lubricating oil to the back pressure chamber 10, so that the mainly receives supply of the lubricating oil from the first recess 36.

In addition, the time when the opening on the front block 5a side of the other back pressure chamber 10 and the concave portion 37c of the second concave portion 37 face each other coincides with the time when the stroke amount of the vane 9 decreases. Therefore, as shown in FIG. 10B, the volume of the back pressure chamber 10 is reduced by the vane 9 sliding in the vane groove 8 in the direction of decreasing the stroke amount, When the pressure in the back pressure chamber 10 rises relative to the lubricating oil supply passages 33 and 34 and the lubricating oil is sent from the back pressure chamber 10 to the lubricating oil supply passages 33 and 34, the second recess 37 Since the back pressure chamber 10 communicates with the recessed depth portion 37c, the communication area between the second recessed portion 37 and the back pressure chamber 10 is relatively enlarged. ) Indicating the amount of lubricating oil to the lubricating oil supply passage 33 As indicated by the arrow representing the amount of lubricating oil into the lubricating oil supply passage 34, so that the first recess 36 to the second recess 37 sends similarly lubricating oil.

Therefore, the flow rate of the lubricating oil sent from the lubricating oil supply passage 33 to the back pressure chamber 10 via the second recess 37 is the lubricating oil sent from the back pressure chamber 10 to the lubricating oil supply passage 33 via the second recess 37. Therefore, it is possible to increase the flow rate of the lubricating oil sent from the back pressure chamber 10 to the lubricating oil supply passage 33 when viewed comprehensively.

(Second example)
11 and 12 show a second example of the second embodiment of the vane type compressor 1 that can use the lubricating oil supply structure according to the present invention.

The second recess 37 shown in the second example of the second embodiment has the same configuration as that of the first example of the second embodiment described above, as shown in FIGS. 11 (a) and 12 (a). On the other hand, as shown in FIGS. 11 (c) and 12 (c), the first recess 36 shown in the second example of the second embodiment has a recessed deep portion 37c and a recessed shallow portion 37d. It is configured. For this reason, about the 2nd recessed part 37, the code | symbol same as the 1st example of Example 2 is attached | subjected, the description is abbreviate | omitted, and only the 1st recessed part 36 is demonstrated below. However, the position of the first recess 36 in which the first recess 36 is provided is the same as that of the first example of the second embodiment, and a description thereof will be omitted.

Similarly to the second recess 37 shown in FIG. 7, the first recess 36 has a circular line L1 constituting the circular opening edge of the drive shaft storage space 31 as an inner edge, and is concentric with the circular line L1. A circular line L6 is used as an outer edge, and the circular line L1 extends from the circular line L1 to the outer side in the radial direction of the drive shaft 2 with the same dimensions throughout the entire circumference. The dimension of the circular line L6 that forms the circumferential outer edge of the first recess 36 is, for example, substantially the same as the dimension of the bottom surface position of the vane 9 when the vane 9 is at the minimum stroke amount.

Further, as shown in FIGS. 11 (c) and 12 (c), the deep concave portion 36c and the shallow shallow portion 36d of the first concave portion 36 are formed on the rotor body 3a with respect to the first concave portion 36. It is divided by two boundary lines S5 and S6 extending along a straight line passing through both the axis P1 and the center P2 of the cylinder hole 6c. The depth in the axial direction of the drive shaft of the recessed deep portion 36c is shallow. The depth is greater than the axial depth of the drive shaft of the portion 36d. As a result, when the opening on the rear block 6b side of the back pressure chamber 10 is in a range facing the recess depth portion 36a of the first recess 36, the communication area through which the lubricating oil passes through the first recess 36 is When the rear side block 6b side opening of the back pressure chamber 10 is within a range facing the concave shallow portion 36d of the first concave portion 36, the lubricating oil passes through the first concave portion 36. The communication area is relatively reduced.

Thus, as shown in FIGS. 11 (a), 11 (c), 12 (a), and 12 (c), the point where the boundary line S5 and the inner peripheral surface of the cylinder hole 6c intersect is defined as X5. 11A and 12B, the point where the boundary line S6 intersects the inner peripheral surface of the cylinder hole 6c is X6, and the rotation direction of the rotor 3 is viewed from the front side of the vane compressor 1. In (a), it turns counterclockwise as shown by the arrow, and in the state seen from the rear side of the vane compressor 1, it turns clockwise as shown by the arrow in FIGS. 11 (c) and 12 (c). In such a case, the vane 9 protrudes from the vane groove 8 beyond the outer surface of the rotor 3 as indicated by the thick arrow in FIG. 11B in the range where X5 is the start point and X6 is the end point. When the stroke amount increases, X6 is the starting point and X5 is the ending point The enclosed, as shown in bold arrows in FIG. 12 (b), the stroke of the vane 9 is gradually retracted from the outer surface of the rotor 3 in the vane groove 8 is timing to decrease. A straight line connecting X5 and X6, which divides the timing when the stroke amount of the vane 9 increases or decreases, is the same as the boundary line S5 and the boundary line S6.

Thus, when the opening on the front block 5a side of one back pressure chamber 10 and the shallow shallow portion 37d of the second recess 37 face each other, when the stroke amount of the vane 9 increases, and The timing when the opening on the rear block 6b side of the back pressure chamber 10 and the concave portion 36c of the first recess 36 face each other matches the timing when the stroke amount of the vane 9 increases. As shown in FIG. 11B, the volume of the back pressure chamber 10 is expanded by sliding the vane 9 in the vane groove 8 in the direction of increasing the stroke amount, and the back pressure is increased. Although the pressure in the chamber 10 is relatively lower than the lubricating oil supply passages 33 and 34, the back pressure chamber 10 is supplied with the lubricating oil from the lubricating oil supply passages 33 and 34, but the second recess 37 has a back pressure chamber. 10 communicates with the concave portion 37d. Therefore, the communication area between the second recessed portion 37 and the back pressure chamber 10 is relatively reduced, and the first recessed portion 36 communicates with the back pressure chamber 10 at the recessed depth portion 36c. The communication area with the back pressure chamber 10 is relatively enlarged. For this reason, the back pressure chamber 10 has an arrow indicating the amount of lubricating oil from the lubricating oil supply passage 33 to the back pressure chamber 10 in FIG. 11B and the lubricating oil from the lubricating oil supply passage 34 to the back pressure chamber 10. As indicated by an arrow indicating the amount, the supply of lubricating oil is mainly received from the first recess 36.

Further, when the opening on the front block 5a side of the other back pressure chamber 10 and the concave portion 37c of the second concave portion 37 face each other, when the stroke amount of the vane 9 decreases, Since the opening of the back pressure chamber 10 on the rear block 6b side and the time when the concave portion 36d of the first concave portion 36 faces each other coincide with each other, as shown in FIG. By sliding in the vane groove 8 in the direction of decreasing the stroke amount, the volume of the back pressure chamber 10 is reduced, and the pressure in the back pressure chamber 10 is higher than that of the lubricating oil supply passages 33 and 34. Since the second recess 37 communicates with the back pressure chamber 10 at the recess depth portion 37c when the lubricating oil is relatively raised and the lubricating oil is sent from the back pressure chamber 10 to the lubricating oil supply passages 33, 34, the second pressure is reduced. The communication area between the recess 37 and the back pressure chamber 10 is relatively Is enlarged, the first recess 36 is connected domain of the first recess 36 and the back pressure chamber 10 to communicates with the back pressure chamber 10 and the 凹浅 site 36d is relatively reduced. For this reason, the back pressure chamber 10 is indicated by an arrow indicating the amount of lubricating oil to the lubricating oil supply passage 33 and an arrow indicating the amount of lubricating oil to the lubricating oil supply passage 34 in FIG. The lubricating oil is mainly sent to the second recess 37.

Therefore, the flow rate of the lubricating oil sent from the back pressure chamber 10 to the lubricating oil supply passage 33 via the second recess 37 is the lubricating oil sent from the back pressure chamber 10 to the lubricating oil supply passage 34 via the first recess 36. And the flow rate of the lubricating oil sent from the lubricating oil supply passage 33 through the second recess 37 to the back pressure chamber 10 is larger than the flow rate of the back pressure chamber 10 when viewed comprehensively. The flow rate of the lubricating oil sent to the lubricating oil supply passage 33 can be increased.

(Third example)
FIGS. 13 and 14 show a third example of the second embodiment of the vane type compressor 1 in which the lubricating oil supply structure according to the present invention can be used.

The first recess 36 shown in the third example of the second embodiment has the same configuration as the second example of the second embodiment described above, as shown in FIGS. 13 (a) and 14 (a). On the other hand, as shown in FIGS. 13 (c) and 13 (c), the first recess 36 shown in the second example of the second embodiment has a recessed deep portion 37c and a recessed shallow portion 37d. It does not have. For this reason, about the 1st recessed part 36, the same code | symbol as the 2nd example of Example 2 is attached | subjected, the description is abbreviate | omitted, and only the 2nd recessed part 37 is demonstrated below. However, the position of the second concave portion 37 where the second concave portion 37 is provided is the same as in the first and second examples of the second embodiment, and the description thereof is omitted.

Similarly to the first recess 36 shown in FIG. 8, the second recess 37 has a circular line L1 constituting the circular opening edge of the drive shaft storage space 31 as an inner edge, and is concentric with the circular line L1. A circular line L6 is used as an outer edge, and the circular line L1 extends from the circular line L1 to the outer side in the radial direction of the drive shaft 2 with the same dimensions throughout the entire circumference. The dimension of the circular line L6 that forms the circumferential outer edge of the second recess 37 is, for example, substantially the same as the dimension of the bottom surface position of the vane 9 at the time of the minimum stroke amount of the vane 9.

In the third example, the second recess 37 is different from the first recess 36, and as shown in FIGS. 13A and 14A, the second recess 37 extends in the axial direction of the drive shaft in the entire region. The depth is the same. Furthermore, the depth dimension of the second recess 37 is the same as the axial depth of the drive shaft of the recess depth portion 36c of the first recess 36 in this third example. As a result, even if the opening on the front block 5a side of the back pressure chamber 10 faces any range of the second recess 37, the communication area through which the lubricating oil passes through the second recess 36 is relatively expanded. It is in the state.

Thus, as shown in FIGS. 13C and 14C, the point where the boundary line S5 and the inner peripheral surface of the cylinder hole 6c intersect is defined as X5, and the boundary line S6 and the inner periphery of the cylinder hole 6c. The point where the plane intersects is X6, and the rotation direction of the rotor 3 is opposite to that shown in the arrows in FIGS. 13 (a) and 14 (a) when viewed from the front side of the vane compressor 1. In the case of clockwise rotation as shown by the arrows in FIGS. 13C and 14C as viewed from the rear side of the vane type compressor 1, the starting point is X5. In the range where X6 is the end point, as shown by the thick arrow in FIG. 13B, the stroke amount of the vane 9 protruding from the vane groove 8 beyond the outer surface of the rotor 3 increases. In the range where X5 is the end point, the thick line in FIG. As shown in the arrow, the stroke amount of the vane 9 is gradually retracted from the outer surface of the rotor 3 in the vane groove 8 is timing to decrease. A straight line connecting X5 and X6, which divides the timing when the stroke amount of the vane 9 increases or decreases, is the same as the boundary line S5 and the boundary line S6.

In this way, the timing when the opening on the rear block 6b side of one back pressure chamber 10 and the depth portion 36c of the first recess 36 face each other coincides with the timing when the stroke amount of the vane 9 increases. Therefore, as shown in FIG. 13B, the volume of the back pressure chamber 10 is increased by sliding the vane 9 in the vane groove 8 in the direction of increasing the stroke amount. The pressure in the back pressure chamber 10 is relatively lower than the lubricating oil supply passages 33 and 34, and the back pressure chamber 10 is supplied with the lubricating oil from the lubricating oil supply passages 33 and 34. Since the back pressure chamber 10 communicates with the back pressure chamber 10 at the concave depth portion 37c, the communication area between the first recess 36 and the back pressure chamber 10 is relatively enlarged. (B) Lubrication oil from the lubrication oil supply passage 33 to the back pressure chamber 10 As shown by an arrow indicating the amount of oil and an arrow indicating the amount of lubricating oil from the lubricating oil supply passage 34 to the back pressure chamber 10, supply of lubricating oil from both the first recess 36 and the second recess 37 Will receive the same.

The time when the opening on the rear block 6b side of the other back pressure chamber 10 and the shallow shallow part 36d of the first recess 36 face each other coincides with the time when the stroke amount of the vane 9 decreases. Therefore, as shown in FIG. 14B, the volume of the back pressure chamber 10 is reduced by the vane 9 sliding in the vane groove 8 in the direction of decreasing the stroke amount, When the pressure in the back pressure chamber 10 rises relative to the lubricating oil supply passages 33 and 34 and the lubricating oil is sent from the back pressure chamber 10 to the lubricating oil supply passages 33 and 34, the first recess 36 Since the back pressure chamber 10 communicates with the shallow shallow portion 36d, the communication area between the first recess 36 and the back pressure chamber 10 is relatively reduced. ) And an arrow indicating the amount of lubricating oil to the lubricating oil supply passage 33 As indicated by the arrows representing the amount of lubricating oil to the oil supply passage 34 mainly so that the relative second recess 37 mainly transmits the lubricating oil.

Therefore, the flow rate of the lubricating oil sent from the back pressure chamber 10 through the first recess 36 to the lubricating oil supply passage 34 is the lubricating oil sent from the lubricating oil supply passage 34 to the back pressure chamber 10 through the first recess 36. Therefore, it is possible to increase the flow rate of the lubricating oil sent from the back pressure chamber 10 to the lubricating oil supply passage 33 when viewed comprehensively.

The lubricating oil supply structure according to the present invention has been described using the two-block vane compressor 1 in both the first and second embodiments. However, the two-block vane compressor 1 is not necessarily described. Although not shown in the drawings, a vane type compressor may be used which is closed by being sandwiched between a front side block and a rear side block, and has a separate cylinder from these blocks.

DESCRIPTION OF SYMBOLS 1 Vane type compressor 2 Drive shaft 3 Rotor 4 Compression space 5 Block 5a Front side block 5b Shell 6 Block 6a Cylinder 6b Rear side block 6c Cylinder hole 8 Vane groove 9 Vane 10 Back pressure chamber 12 Plain bearing 13 Plain bearing 16 Inlet 17 Discharge port 19 Oil reservoir chamber 21 Compression chamber 29 Drive shaft storage space 30 Relay passage 31 Drive shaft storage space 33 Lubricating oil supply passage 34 Lubricating oil supply passage 36 First recess 36a Communication state forming portion 36b Communication state formation not supported Part 36c Concave deep part 36d Concave shallow part 37 Second concave part 37a Communication state forming part 37b Continuity state non-corresponding part 37c Concave deep part 37d Concave part

Claims

A cylinder closed on both sides by a block, a rotor housed in the cylinder and formed with a plurality of vane grooves, and housed in the vane grooves of the rotor, with the side surfaces sliding on the inner surface of the vane grooves. A vane that moves and slides on the inner peripheral surface of the cylinder with its tip protruding and retracting from the vane groove, a back pressure chamber formed at the bottom of the vane groove, and supported by the block via each bearing And a vane type compressor having a drive shaft connected to the rotor and transmitting a rotational force from the outside to the rotor, and an oil reservoir chamber in which lubricating oil is temporarily stored.
Lubricating oil enters between the drive shaft and one of the blocks from the oil reservoir chamber, flows along the axial direction of the drive shaft, and lubricates one of the bearings located in the middle thereof. After that, the first recess formed on the cylinder side end surface of the one block, the back pressure chamber, and the second recess formed on the cylinder side end surface of the other block of the block flow in this order, A lubricating oil path that enters between the other blocks, flows again along the axial direction of the drive shaft, and lubricates the other bearing located in the middle thereof;
The first recess and the second recess can change the communication state with the back pressure chamber, respectively, as the position of the back pressure chamber varies due to the rotation of the rotor. When the amount of protrusion of the vane from the vane groove of the rotor is the amount of stroke of the vane, the change in the communication state with the back pressure chamber is linked to the time when the amount of stroke of the vane increases, A lubricating oil supply structure for a vane compressor, wherein the lubricating oil is supplied to the back pressure chamber by lowering the pressure in the back pressure chamber relative to the surroundings.
There is a difference between the time when the space between the first recess and the back pressure chamber is opened and the time when the space between the second recess and the back pressure chamber is opened. By linking the opening timing deviation between the recess and the back pressure chamber and between the second recess and the back pressure chamber and the timing when the stroke amount of the vane increases, 2. The lubricating oil supply structure for a vane compressor according to claim 1, wherein lubricating oil is supplied to the back pressure chamber.
The time when the stroke amount of the vane increases and the time when the space between the first recess and the back pressure chamber is opened earlier than the space between the second recess and the back pressure chamber are combined. The lubricating oil supply structure for a vane compressor according to claim 2, wherein the lubricating oil is supplied.
A cylinder closed on both sides by a block, a rotor housed in the cylinder and formed with a plurality of vane grooves, and housed in the vane grooves of the rotor, with the side surfaces sliding on the inner surface of the vane grooves. A vane that moves and slides on the inner peripheral surface of the cylinder with its tip protruding and retracting from the vane groove, a back pressure chamber formed at the bottom of the vane groove, and supported by the block via each bearing And a vane type compressor having a drive shaft connected to the rotor and transmitting a rotational force from the outside to the rotor, and an oil reservoir chamber in which lubricating oil is temporarily stored.
Lubricating oil enters between the drive shaft and one of the blocks from the oil reservoir chamber, flows along the axial direction of the drive shaft, and lubricates one of the bearings located in the middle thereof. After that, the first recess formed on the cylinder side end surface of the one block, the back pressure chamber, and the second recess formed on the cylinder side end surface of the other block of the block flow in this order, A lubricating oil path that enters between the other blocks, flows again along the axial direction of the drive shaft, and lubricates the other bearing located in the middle thereof;
The first recess and the second recess can change the communication state with the back pressure chamber, respectively, as the position of the back pressure chamber varies due to the rotation of the rotor. When the amount of protrusion of the vane from the vane groove of the rotor is the amount of stroke of the vane, the change in the communication state with the back pressure chamber is linked to the time when the amount of stroke of the vane decreases, A lubricating oil supply structure for a vane type compressor, wherein the lubricating oil is sent out from the back pressure chamber by raising the pressure in the back pressure chamber relative to the surroundings.
There is a difference between the timing when the first recess and the back pressure chamber are closed, and the timing when the second recess and the back pressure chamber are closed. By linking the gap of the closing timing between the recess and the back pressure chamber and between the second recess and the back pressure chamber and the timing when the stroke amount of the vane decreases, 5. The lubricating oil supply structure for a vane compressor according to claim 4, wherein the lubricating oil is delivered from the back pressure chamber.
The time when the stroke amount of the vane decreases and the time when the gap between the first recess and the back pressure chamber is closed earlier than between the second recess and the back pressure chamber are combined. The lubricating oil supply structure for a vane type compressor according to claim 5, wherein the lubricating oil supply structure is provided.
At least one of the first recess and the second recess is divided into a portion having a relatively deep depth and a relatively shallow portion in the axial direction of the drive shaft in the lateral width direction of the vane compressor. 5. The lubricating oil supply structure for a vane type compressor according to claim 1, wherein the communication state with the back pressure chamber is changed using the difference in depth.
The concave portion which is the first concave portion or the second concave portion and is not divided into a portion having a relatively deep depth in the axial direction of the drive shaft and a portion having a relatively shallow depth is a portion having a shallow depth in the entire region. 8. The lubricating oil supply structure for a vane compressor according to claim 7, wherein a depth of the relatively deep portion of the concave portion divided into a narrow portion and the narrow portion is the same.