JP2009156231A - Lubricant decompressing and supplying structure for vane type compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To enable to machine under the relatively high accuracy control at a relatively low cost, and to restrict a lack of supply of lubricating oil due to a stoppage by foreign materials such as dust included in the lubricating oil, in regard to structure for decompressing and supplying the lubricating oil of a vane type compressor. <P>SOLUTION: An annular lubricating oil throttle passage 29 is formed on a peripheral side of a driving shaft 3 of a vane type compressor 1, and this lubricating oil throttle passage 29 is communicated with a lubricating oil chamber 25 through a relay passage 27, and a lubricating oil supply passage 30 communicated with a downstream side of the lubricating oil throttle passage 29 is extended to at least a part, in which a rotor 4 and a rear side block 7 slide with each other, to provide a lubricating oil moving route A capable of depressing the lubricating oil from the lubricating oil chamber 25 inside of the lubricating oil throttle passage 29 and supplying it to the part, in which the rotor 4 and the rear side block 7 slide with each other. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a structure of a vane type compressor used for a vehicle air conditioner, and more particularly to a structure for supplying a lubricant such as lubricating oil to a predetermined part of the vane type compressor after reducing the pressure. is there.

  In this type of vane compressor, in order to supply the lubricating oil to the rotor end surface and the sliding portion of the side block rotor, a through-hole-shaped lubricating oil passage is provided in the rear side block, and the lubricating oil is disposed on the rear side side. The invention that is supplied from the oil reservoir chamber to the sliding portion of the bearing and the rotor through the lubricating oil passage provided in the rear side block has been already known as disclosed in Patent Document 1, for example. And in the vane type compressor shown by this patent document 1, as a bearing for supporting a drive shaft in the side wall by the side of a rear side, the bearing (code | symbol called a roller bearing or a needle bearing in FIG. 2 of the said patent document 1) 22) is shown.

Further, in this type of vane compressor, the control plate of the variable displacement mechanism is formed with a throttle hole extending along the axial direction of the drive shaft and penetrating the control plate, so that the high-pressure lubricating oil is The invention in which the pressure of the lubricating oil is reduced when it is supplied to the back pressure chamber through the throttle hole is already known from, for example, Patent Document 2. And also in the vane type compressor shown by this patent document 2, the bearing (code | symbol 12) called a roller bearing or a needle bearing in FIG. 1 of the said patent document 2 is used as a thrust bearing which supports a drive shaft to a rear side block. It is shown in the figure.
Japanese Utility Model Publication No. 3-99891 JP-A-5-223080

  However, as shown in Patent Document 1, a through-hole-shaped lubricating oil passage is formed in the rear side block, or as shown in Patent Document 2, an elongated throttle hole is formed in the control plate of the variable capacity mechanism. However, since the processing is relatively difficult because of the processing by pressing or the like, there is a concern that the manufacturing cost of the entire vane compressor becomes high, and there is concern about each lubricating oil passage and the throttle hole. Since it is relatively difficult to control the accuracy for unifying the inner diameter and the like, it is conceivable that the lubricating oils having different pressures are sent to the back pressure chamber and the back pressure varies.

  Furthermore, when foreign matter such as dust is mixed into the lubricating oil, the opening area of the through-hole-shaped lubricating oil passage provided in the rear side block is relatively small, and is provided on the control plate of the variable capacity mechanism. Since the opening area of the throttle hole is also relatively small, there may be a disadvantage that the lubricating oil passage and the throttle hole are clogged with foreign matter and the supply of the lubricating oil is hindered.

  Therefore, the present invention can be processed at a relatively low cost and under a relatively high accuracy control, and is further blocked by foreign matters such as dust contained in the lubricant, so that the supply of the lubricant is not possible. It is an object of the present invention to provide a lubricant pressure reducing supply structure for a vane type compressor that is also prevented from becoming sufficient.

  A lubricant supply structure for a vane compressor according to the present invention includes a cam ring closed by being sandwiched between two side blocks, a rotor housed in the cam ring and having a plurality of vane grooves formed therein. The vanes housed in the vane grooves of the rotor, the side surfaces of which slide on the inner surface of the vane grooves, and the tip of the vanes slides on the inner peripheral surface of the cam ring. A drive shaft that is supported by the side block and connected to the rotor to transmit a rotational force from the outside to the rotor, and a lubricant chamber that is formed in the side block and in which lubricant is temporarily stored. In the vane compressor having at least, an annular lubricant throttle passage is formed on the outer peripheral side of the drive shaft, and the lubricant throttle passage is provided at least via a relay passage. The lubricant supply passage connected to the lubricant chamber and the downstream side of the lubricant restriction passage extends at least to a sliding portion between the rotor end surface and the rear side block. And a lubricant moving path capable of reducing the pressure of the lubricant from the lubricant chamber in the lubricant restricting passage and supplying the lubricant to the sliding portion between the rotor end surface and the side block. (Claim 1). This lubricant throttle passage also includes a lubricating oil throttle / supply passage formed by a plain bearing and a drive shaft or an extension part of a side block and a drive shaft, which will be described in the embodiment of the invention. Moreover, although it is a sliding part of the rotor end surface and side block which becomes a supply destination of a lubricant, the side block here is not limited to the rear side block, and the front side block also corresponds.

  The drive shaft is supported by the rear side block by mounting a plain bearing, which is a separate member from the rear side block, on the outer peripheral side of the drive shaft, and the lubrication. The agent restricting passage is formed by a gap generated by mounting the plain bearing on the drive shaft. As described later, the radial width of the drive shaft of the lubricant throttle passage is such that one or two or more grooves are provided on the inner surface of the lane bearing facing the outer peripheral surface of the drive shaft, Of these, when the portion facing the inner surface of the plain bearing is not recessed from the other portion of the outer peripheral surface of the drive shaft, the size is relatively large, for example, 100 micrometers.

  Further, the inner surface of the plain bearing may be provided with one or more grooves in a portion facing the outer peripheral surface of the drive shaft (Claim 5), or the plane of the outer peripheral surface of the drive shaft. One or two or more portions facing the inner side surface of the bearing may be recessed relative to other portions of the outer peripheral surface of the drive shaft. In this case, the radial width of the drive shaft of the lubricant throttle passage is relatively small, for example, 10 micrometers. In addition, the portion expanded by the plain bearing groove or the drive shaft recess has no or low lubricant squeezing effect, and the lubricant throttle passage is expanded by the plain bearing groove or the drive shaft recess. The portion thus mainly functions as a lubricant supply passage.

  On the other hand, as a lubricant decompression supply structure of the vane type compressor, the drive shaft is supported on the rear side block by using a plain bearing that is a separate member from the rear side block. The lubricant supply passage is formed by a gap formed between the outer peripheral surface of the drive shaft and the inner surface of the plain bearing, and the lubricant restrictor The passage is formed by a gap generated between an outer peripheral surface of the drive shaft and a surface of the extension portion that extends in the radial direction of the drive shaft from the rear side block and the surface of the extension portion facing the drive shaft. The radial width of the drive shaft of the lubricant supply passage formed may be smaller than the radial width of the drive shaft of the lubricant throttle passage. In this case, the radial width of the drive shaft of the lubricant supply passage is, for example, 10 micrometers, and the radial width of the drive shaft of the lubricant throttle passage is, for example, 100 micrometers.

  Further, as a lubricant decompression supply structure of the vane type compressor, the drive shaft is supported on the rear side block by placing a plain bearing, which is a separate member from the rear side block, on the outer peripheral side of the drive shaft. The lubricant supply passage and the lubricant throttle passage are formed by a gap formed between the outer peripheral surface of the drive shaft and the inner surface of the plain bearing. In addition, the radial width of the drive shaft of the lubricant supply passage may be smaller than the radial width of the drive shaft of the lubricant throttle passage. Also in this case, the radial width of the drive shaft of the lubricant supply passage is 10 micrometers, for example, and the radial width of the drive shaft of the lubricant throttle passage is 100 micrometers, for example.

  Even in the lubricant pressure reducing supply structure of these vane compressors, one or two or more grooves may be provided in a portion of the inner surface of the plain bearing that faces the outer peripheral surface of the drive shaft. Item 5), or one or more portions of the outer peripheral surface of the drive shaft facing the inner surface of the plain bearing may be recessed from other portions of the outer peripheral surface of the drive shaft. Item 6).

  Furthermore, as a lubricant decompression supply structure of the vane compressor, the drive shaft is supported on the rear side block by an extending portion extending in the radial direction of the drive shaft from the rear side block. In addition, the lubricant throttle passage may be formed by a gap formed between an outer peripheral surface of the drive shaft and a surface of the extension portion facing the drive shaft. . The rear side block and the extending portion are integrally formed.

  As described above, the lubricant restricting passage is formed by a combination of the outer peripheral surface of the drive shaft and the inner surface of the plain bearing or the outer peripheral surface of the drive shaft and the surface facing the drive shaft of the extending portion extending from the rear side block. Therefore, the manufacturing cost is reduced as compared with the case where the lubricant throttle passage is processed and formed as a through-hole in a side block, etc., and the precision control of the dimensional width of the drive shaft of the lubricant throttle passage is advanced. Therefore, the pressure reduction of the lubricant sent to the back pressure chamber of the vane groove becomes uniform, and the back pressure does not vary.

  Also, one of the surfaces for defining the periphery of the lubricant throttle passage is constituted by the outer peripheral surface of the drive shaft, and since this drive shaft rotates, foreign matter such as dust enters the lubricant throttle passage. And even if caught, it will be crushed into small pieces, so it is easy to be rejected.

  In addition, since the lubricant throttle passage is formed in an annular shape on the outer peripheral side of the drive shaft, the opening area through which the lubricant in the lubricant throttle passage can move is a through-hole lubricant in the side block and the drive shaft. Since it is relatively large compared to the case where the throttle portion is formed, the lubricant throttle passage ensures a sufficient opening area for the lubricant to move even when dust is caught in the lubricant throttle passage. Therefore, a situation in which the amount of lubricant supplied to the sliding portion between the rotor end surface and the rear side block is insufficient is avoided.

  Thus, by having the lubricant throttle passage on the outer peripheral side of the drive shaft, the high-pressure lubricant that has moved from the lubricant chamber through the relay passage is reduced to a predetermined value when passing through the lubricant throttle passage. Therefore, the vane is strongly pressed against the inner peripheral surface of the cam ring and the inner peripheral surface of the cam ring is prevented from being worn while obtaining the action of pushing the vane toward the cam ring. It is possible to achieve the intended purpose.

  As described above, according to the present invention, the lubricant throttle passage faces the outer peripheral surface of the drive shaft and the inner surface of the plain bearing, and the outer peripheral surface of the drive shaft and the drive shaft of the extending portion extending from the rear side block. Since it is formed by the combination with the surface, the manufacturing cost of the vane compressor can be reduced as compared with the case where the lubricant throttle passage is processed and formed as a through hole in a side block or the like. And since the high precision control of the radial dimension of the drive shaft of the lubricant throttle passage is possible, the pressure reduction of the lubricant sent to the back pressure chamber of the vane groove becomes uniform, and the variation in back pressure is suppressed. Therefore, the performance of the vane compressor can be sufficiently exhibited and maintained.

  Further, according to the present invention, the drive shaft constitutes one of the surfaces constituting the periphery of the lubricant throttle passage, and since this drive shaft rotates, foreign matters such as dust enter the lubricant throttle passage. Therefore, the lubricant throttle passage can be prevented from being clogged for a long time by foreign matters such as dust contained in the lubricant. It is possible to prevent the amount supplied to the sliding portion between the rotor end surface and the rear side block from being insufficient.

  In addition, according to the present invention, since the lubricant throttle passage is formed in an annular shape on the outer peripheral side of the drive shaft, the opening area through which the lubricant in the lubricant throttle passage can move penetrates the side block and the drive shaft. Since it becomes relatively large compared to the case of forming a hole-shaped lubricant constriction portion, even when foreign matter such as dust is caught in the lubricant constriction passage, the lubricant constriction passage moves the lubricant. Since a sufficient opening area is secured, it is possible to prevent the amount of lubricant supplied to the sliding surface between the rotor end surface and the rear side block from being insufficient.

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

  1 to 3 show the overall configuration of a vane type compressor 1 according to a first embodiment of the present invention. The 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.

  The vane compressor 1 is inserted into a cam ring 2, a rotor 4 rotatably housed in the cam ring 2 and fixed to a drive shaft 3, and a plurality of vane grooves 5 provided in the rotor 4. A vane 6, a rear side block 7 fixed to the rear side end surface of the cam ring 2, and a front side block 8 that surrounds the front side end surface and outer peripheral surface of the cam ring 2 and is fitted to the rear side block 7. Has been.

  The drive shaft 3 is rotatably supported on the front side block 8 via a bearing 10 called a roller bearing and a needle bearing, and on the rear side block 7 via a plain bearing 11 described later. However, for example, a plain bearing may be used as the bearing 10 used for the front side block 8.

  The front side block 8 has a working fluid (refrigerant gas) suction port 12 and a low pressure chamber 13 communicating with the suction port. The rear side block 7 has a working fluid discharge port 14 and a discharge port. A high pressure chamber 15 serving as a path for sending the working fluid to the outlet 14 is formed. The high-pressure chamber 15 includes a high-pressure chamber 15 that communicates with the discharge valve storage chamber 19 through a through-hole 21 of the flange portion 2a described later, and an oil separator 43 that is described later with the high-pressure chamber 15 that communicates with the discharge valve storage chamber 19. And a high-pressure chamber 15 communicating with the discharge port 14.

  An elliptical space 9 is formed on the inner peripheral surface of the cam ring 2, and the compression space 16 is provided between the cam ring 2 and the outer peripheral surface of the rotor 4 by arranging the perfect circular rotor 4 in the space 9. The compression space 16 is partitioned by the vanes 6 to form a plurality of compression chambers 17, and the volume of each compression chamber 17 is changed by the rotation of the rotor 4.

  The vane groove 5 provided in the rotor 4 described above is opened not only on the inner peripheral surface side of the cam ring 2 but also on the front side block 8 side and the rear side block 7 side, and a back pressure chamber 23 is formed at the bottom thereof. ing. Therefore, the back pressure chamber 23 is also opened to the front side block 8 side and the rear side block 7 side.

  The rear side block 7 has a side block portion 7a that abuts on the cam ring 2 and a head portion 7b. The end surface facing the cam ring 2 is recessed in the axial direction of the drive shaft 3 to form the high pressure chamber 15 described above. A recess 15a is formed for this purpose.

  The front side block 8 is formed by integrally forming a side block portion 8a that comes into contact with the cam ring 2 and a shell-like head portion 8b that surrounds the side block portion 8a. A pulley (not shown) for transmitting rotational power from a source (not shown) is rotatably mounted on the boss portion 8c, and from this pulley via an electromagnetic clutch (not shown), an external drive source Rotational power is transmitted to the drive shaft 3.

  The cam ring 2 is formed with flange portions 2a and 2b projecting along the radial direction of the drive shaft 3 at both ends thereof. Among these, the front flange portion 2 b is formed in a shape matching the inner peripheral shape of the front side block 8 and is press-fitted into the front side block 8. On the other hand, the rear flange portion 2a is formed in a shape that matches the inner peripheral shape of the head portion 8b of the front side block 8 and is press-fitted into the head portion 8b in this embodiment. However, the rear side block 7 may be formed with a fitting portion, and the rear flange portion 2a may be formed in a shape matching the fitting portion so that the rear flange portion 2a is press-fitted into the fitting portion. . Thereby, in this embodiment, when the rear side block 7 is properly press-fitted into the head portion 8b of the front side block 8, the flange portion 2a is brought into contact with the end surface of the rear side block 7, and the outer peripheral edge of the rear side block 7 The high pressure chamber 15 is defined by closing the recess 15a formed in the vicinity.

  A discharge port 18 is provided on the outer peripheral surface of the cam ring 2 so as to correspond to the compression space 16. Further, between the outer peripheral surface of the cam ring 2 and the inner peripheral surface of the front side block 8, a discharge valve accommodating chamber 19 defined by flange portions 2a and 2b formed at both ends of the cam ring 2 is formed. At the same time, the discharge port 18 opens into the discharge valve accommodating chamber 19, and a compression chamber 17 formed between the vanes 6 can communicate with the discharge port 18. The discharge port 18 is opened and closed by a discharge valve 20 housed in the discharge valve housing chamber 19.

  The discharge valve storage chamber 19 and the high-pressure chamber 15 are separated by a flange portion 2a provided in the cam ring 2, and are communicated only via a through hole 21 formed in the flange portion 2a. Further, the rear side block 7 is provided with a centrifugal oil separator 43 for separating the lubricating oil mixed in the discharge gas downstream of the through hole 21 formed in the flange portion 2a of the cam ring 2. ing.

  According to said structure, the operation | movement of the suction | inhalation of a working fluid, compression, and discharge by a vane type compressor is as follows. That is, rotational power from an external power source (not shown) is transmitted to the drive shaft 3 via a pulley and an electromagnetic clutch (not shown), and when the rotor 4 rotates, the working fluid flowing into the low-pressure chamber 13 from the suction port 12 is sucked (not shown). The air is sucked into the compression space 16 through the port. Since the volume of the compression chamber 17 partitioned by the vanes 6 in the compression space 16 changes with the rotation of the rotor 4, the working fluid confined between the vanes 6 is compressed, and the discharge valve 18 is discharged from the discharge port 18. Is discharged to the discharge valve accommodating chamber 19 and led to the high pressure chamber 15 formed in the rear side block 7 through the through hole 21 formed in the flange portion 2a of the cam ring 2. Thereafter, the working fluid is introduced into the oil separator 43 through an introduction port (not shown), and after the lubricating oil is separated, the working fluid is guided to the high pressure chamber 15 communicating with the adjacent discharge port 14, and then the discharge port 14. It is discharged from.

  In the vane compressor 1 according to the present invention, the high-pressure lubricating oil separated by the oil separator 43 is supplied to the sliding portion between the end face of the vane 6 and the rear side block 7, the back pressure chamber 23, and the vane 6. As shown in FIG. 5, a lubricating oil moving path A is provided for feeding to the sliding portion between the end surface of the front side block 8 and the front side block 8.

  As shown in FIG. 5, the lubricating oil moving path A starts from a lubricating oil chamber 25 in which high-pressure lubricating oil separated by the oil separator 43 is temporarily stored. 3 is formed in the rear side block 7, and moves from the lubricating oil chamber 25 to the drive shaft storage space 26 via the relay passage 27. In this embodiment, the downstream opening of the relay passage 27 is opened below the end of the drive shaft 3 in the drive shaft storage space 26 or on the rear side of the end of the drive shaft 3.

  As shown in FIG. 4, the drive shaft storage space 26 has a portion that is relatively narrowed by an extension portion 28 extending in an annular shape from the rear side block 7 along the radial direction of the drive shaft 3. By arranging the drive shaft 3 in a relatively narrow portion of the drive shaft storage space 26, the outer peripheral surface of the drive shaft 3 and the extended side surface of the extension portion 28 (the surface facing the drive shaft 3). A lubricating oil throttle passage 29 that is narrower than the distance between the outer peripheral surface of the drive shaft 3 and the inner surface of the portion of the drive shaft storage space 26 that does not have the extension 28 is formed in an annular shape. The numerical value L1 of the dimension in the drive shaft radial direction of the lubricating oil throttle passage 29 is, for example, 100 micrometers.

  The plain bearing 11 is attached to the drive shaft 3 on the front side of the extending portion 28 of the drive shaft storage space 26. In this embodiment, the plain bearing 11 includes a cylindrical body 11a and a flange formed by bending the end of the cylindrical body 11a with respect to the cylindrical body 11a at an angle intersecting the axial direction, such as a right angle direction. It is comprised with the part 11b. The inner diameter dimension of the cylindrical body 11 a is slightly larger than the outer diameter dimension of the drive shaft 3. Thus, when the plain bearing 11 is mounted on the drive shaft 3, as shown in FIG. 4, the lubricating oil is provided between the outer peripheral surface of the drive shaft 3 and the inner peripheral surface of the cylindrical body 11a of the plain bearing 11. The supply passage 30 is formed in an annular shape. A numerical value L2 of the dimension in the drive shaft radial direction of the lubricating oil supply passage 30 is, for example, 10 micrometers.

  As shown in FIG. 4, the lubricating oil supply passage 30 communicates with the back pressure chamber 23 of the vane groove 5 via the passage 31 on the side opposite to the lubricating oil throttle passage 29. Further, the back pressure chamber 23 communicates with a sliding portion between the end surface of the rotor 4 and the side surface of the rotor of the front side block 8 via a passage located on the side opposite to the passage 31.

  According to the above configuration, as shown in FIGS. 4 and 5, the high-pressure lubricating oil accumulated in the lubricating oil chamber 25 is guided to the drive shaft storage space 26 via the relay passage 27 and then the drive shaft. 3, the pressure is reduced in the lubricating oil throttle passage 29, and sent to the lubricating oil supply passage 30. The lubricating oil acts as a lubricant for preventing wear on the sliding portion between the outer peripheral surface of the drive shaft 3 and the inner peripheral surface of the plain bearing 11, and further passes through the passage 31 to the back pressure chamber 23. And reaches the gap between the end surface of the rotor 4 and the rotor side surface of the rear side block 7 to the sliding portion between the end surface of the rotor 4 and the rotor side surface of the rear side block 7. Works as a lubricant to prevent wear.

  Furthermore, the lubricating oil moves through the back pressure chamber 23 along the axial direction of the drive shaft 3 and reaches the opening end on the side of the front side block 8 described above, and then the passage located on the side opposite to the passage 31. Then, it enters the gap between the end surface of the rotor 4 and the rotor side surface of the front side block 8 and functions as a lubricant for preventing wear on the sliding portion between the end surface of the rotor 4 and the rotor side surface of the front side block 8.

  Here, the lubricating oil throttle passage 29 has been described as being formed by extending the annular extending portion 28 from the rear side block 7 into the drive shaft storage space 26 along the radial direction of the drive shaft 3. It is not limited to this. As shown in FIG. 6, the plain bearing 11 is extended along the axial direction of the drive shaft 3 to the vicinity of the opening of the relay passage 27, and the thickness of the tip portion thereof is increased in an annular shape. An annular lubricating oil constricting passage 29 constituted by the inner peripheral surface of the open end portion and the outer peripheral surface of the drive shaft 3 may be provided.

  That is, the lubricating oil throttle passage 29 and the lubricating oil supply passage 30 are sequentially formed from the rear side of the drive shaft 3 between the inner peripheral surface of the open end portion of the plain bearing 11 and the outer peripheral surface of the drive shaft 3. It will be. Also in this case, the numerical value L1 of the dimension in the driving shaft radial direction of the lubricating oil throttle passage 29 is, for example, 100 micrometers, and the numerical value L2 of the driving shaft radial direction dimension of the lubricating oil supply passage 30 is, for example, 10 micrometers. ing.

  Also with such a configuration, a route similar to the lubricating oil movement route A shown in FIGS. 4 and 5 is configured, and the lubricating oil can also perform the same operations and functions as described above. In addition, about the modification of this Example 1, in FIG. 6, about the structure similar to previous Example 1, the description was abbreviate | omitted by attaching | subjecting the same code | symbol.

  Further, as to the structure of the plain bearing 11, as shown in FIG. 9 of Example 2 to be described later, one or two or more extending in a spiral shape instead of being linearly curved with respect to the inner peripheral surface thereof while facing the axial direction of the drive shaft. It is good also as what has the groove | channel 35 (it is two on the illustration). As a result, when the lubricating oil moves through the lubricating oil supply passage 30, the width of the lubricating oil supply passage 30 in the drive shaft radial direction is relatively narrow, so that the lubricating oil does not move smoothly due to resistance. This is avoided by flowing a part of the lubricating oil through the groove 35. Further, the plain bearing 11 may have a configuration including only the cylindrical body 11a without the flange portion 11b.

  A second embodiment of the vane type compressor 1 of the present invention and its modification will be described with reference to FIGS. The overall configuration of the vane type compressor 1 is the same as that of the first embodiment described above except for a part of the lubricating oil movement path A, so that FIG. 1 to FIG. The figure corresponding to 3 is omitted, and the description of the same configuration as in the first embodiment is also omitted by attaching the same reference numerals.

  In FIG. 7, the lubricating oil moving path A does not have the lubricating oil throttle path 29 in the configuration described so far, and is formed by the outer peripheral surface of the drive shaft 3 and the inner peripheral surface of the plain bearing 11. A configuration having an annular lubricating oil throttling and supply passage 34 is shown. That is, in this second embodiment, the dimension of the lubricating oil throttle / supply passage 34 in the drive shaft radial direction is the same value L1 as the lubricating oil throttle passage 29 of the first embodiment, for example, 100 micrometers. Accordingly, the lubricating oil throttle / supply passage 34 also functions as a lubricating oil throttle passage.

  According to the above configuration, as shown in FIGS. 7 and 8, the high-pressure lubricating oil accumulated in the lubricating oil chamber 25 is guided to the drive shaft storage space 26 via the relay passage 27, and then the drive shaft. 3 and is sent to the lubricating oil throttle / supply passage 34. The lubricating oil is depressurized when it passes through the lubricating oil throttle / supply passage 34 and, at the same time, prevents wear on the sliding portion between the outer peripheral surface of the drive shaft 3 and the inner peripheral surface of the plain bearing 11. After acting as a lubricant for the above, it reaches the back pressure chamber 23 through the passage 31 and pushes the vane 6 toward the cam ring 2 and enters the gap between the end face of the rotor 4 and the rotor side face of the rear side block 7. It acts as a lubricant for preventing wear on the sliding portion between the end surface of the rotor 4 and the rotor side surface of the rear side block 7.

  Furthermore, also in this embodiment, the lubricating oil moves through the back pressure chamber 23 along the axial direction of the drive shaft 3, reaches the opening end of the back pressure chamber 23 on the front side block 8 side, and then passes through the passage. 31 enters the gap between the end surface of the rotor 4 and the side surface of the rotor of the front side block 8 through a passage located on the opposite side of the rotor 31, and prevents wear on the sliding portion between the end surface of the rotor 4 and the side surface of the rotor of the front side block 8. Works as a lubricant for.

  9 to 11 show a first modification of the second embodiment. In the first modification, a plain bearing 11 having a groove 35 in the cylindrical body 11a is used. In this embodiment, the grooves 35 of the plain bearing 11 are formed in about two strips, and each groove 35 is curved in a spiral shape instead of being linear while facing the axial direction of the drive shaft 3. It has a shape. However, the number of grooves 35 is not necessarily limited to this, and may be one or three or more. However, when the plain bearing 11 is manufactured through the steps described later, the rigidity does not become uneven. The number of grooves 35 is also limited to a certain number (for example, two).

  And the lubricating oil throttle / supply combined passage 34 formed by the plain bearing 11 and the outer peripheral surface of the drive shaft 3 is on the inner surface other than the groove 35 on the plain bearing 11 side, and the drive shaft radial width is The inner surface of the lubricating oil supply passage 30 shown in the first embodiment has the same numerical value L2 as the radial width of the drive shaft, for example 10 micrometers, and the plain bearing 11 side faces the drive shaft 3 of the groove 35. In this case, the width in the drive shaft radial direction is such a size that does not cause a squeezing effect on the lubricating oil.

  However, the drive shaft radial width of the portion formed by the inner surface other than the groove 35 of the plain bearing 11 and the outer peripheral surface of the drive shaft 3 in the lubricating oil throttle / supply combined passage 34 is, for example, as in the first embodiment. The same numerical value L1 as the width in the drive shaft radial direction of the lubricating oil throttle passage 29 shown, for example, 100 micrometers may be used.

  As a result, when the lubricating oil passes through the lubricating oil throttle / supply passage 34, all of the lubricating oil prevents wear on the sliding portion between the outer peripheral surface of the drive shaft 3 and the inner peripheral surface of the plain bearing 11. Lubricating oil that acts as a lubricant for moving along a portion formed by the outer peripheral surface of the drive shaft 3 and the inner surface other than the groove 35 of the plain bearing 11 is decompressed. Since the lubricating oil that moves in the part formed by the outer peripheral surface of the drive shaft 3 and the inner side surface of the groove 35 moves in a relatively wide part, the entire lubricating oil throttling / supply passage 34 is lubricated as a whole. It is possible to prevent resistance to oil movement.

  Next, the formation of the plain bearing 11 will be outlined with reference to FIG. 10. First, the groove 35 is formed on the flat plate material 37 according to the required number of stripes by pressing, and the flange portion 11b is formed. Folding allowance 38 is applied. The groove 35 extends inward from the short-side end of the plate material 37, but is formed so as not to exceed the folding allowance 38. Then, the plain bearing 11 is formed by bending the plate material 37 into a roll shape while being bent at the folding margin 38. Thereby, shaping | molding of the plain bearing 11 which has the groove | channel 35 is also easy.

  FIG. 12 shows a second modification of the second embodiment. In the second modification, the drive shaft 3 has another outer periphery by chamfering the outer peripheral surface along the axial direction thereof. It has a recess 39 that is recessed from the surface. Thereby, when the plain bearing 11 is mounted on the drive shaft 3, the lubricating oil throttle / supply passage 34 is formed by the inner peripheral surface of the plain bearing 11 and the outer peripheral surface other than the recess 39 of the drive shaft 3. On the other hand, there is also a lubricating oil non-throttle passage portion 40 that does not produce a throttling effect on the lubricating oil between the inner peripheral surface of the plain bearing 11 and the surface of the recess 39.

  That is, the drive shaft radial width of the lubricating oil throttle / supply passage 34 is the same numerical value L2, for example, 10 micrometers, as the radial width of the drive shaft of the lubricating oil supply passage 30 shown in the first embodiment. In addition, the width in the drive shaft radial direction of the lubricating oil non-throttle passage portion 40 is secured so as not to cause a throttling effect on the lubricating oil. However, the drive shaft radial direction width of the lubricating oil throttle / supply passage 34 may be the same value L1, for example, 100 micrometers, as the drive shaft radial direction width of the lubricating oil throttle passage 29 shown in the first embodiment, for example. good.

  As a result, when the lubricating oil passes through the lubricating oil throttle / supply passage 34, all of the lubricating oil prevents wear on the sliding portion between the outer peripheral surface of the drive shaft 3 and the inner peripheral surface of the plain bearing 11. The lubricating oil that acts as a lubricant for moving and moves in parts other than the lubricating oil non-throttle passage portion 40 is decompressed. The lubricating oil that moves through the non-throttle passage portion 40 moves in a relatively wide area. As a result, it is possible to prevent the lubrication oil throttle / supply passage 34 as a whole from resisting the movement of the lubrication oil.

  A third embodiment of the vane type compressor 1 of the present invention will be described with reference to FIG. The overall configuration of the vane type compressor 1 is the same as that of the first and second embodiments except for a part of the lubricating oil movement path A. The figures corresponding to FIGS. 1 to 3 are omitted, and the description of the same configuration as that of the first embodiment is also omitted by attaching the same reference numerals.

  In FIG. 13, the plain bearing 11 is not provided, but instead, an extension portion 42 extending in an annular shape from the rear side block 7 along the radial direction of the drive shaft is provided. The oil throttle / supply combined passage 34 is formed in an annular shape by an outer peripheral surface of the drive shaft 3 and an extended side surface of the extension portion 42 (a surface facing the drive shaft 3). The dimension of the lubricating oil throttle / supply passage 34 in the drive shaft radial direction is a numerical value L1 similar to that of the lubricating oil throttle passage 29 of the first embodiment, for example, 100 micrometers. The supply / use passage 34 also functions as a lubricating oil throttle passage.

  According to the above configuration, as shown in FIG. 13, the high-pressure lubricating oil accumulated in the lubricating oil chamber 25 is guided to the drive shaft storage space 26 via the relay passage 27 and then the shaft of the drive shaft 3. It moves along the direction and is sent to the lubricating oil throttle / supply passage 34. The lubricating oil is depressurized when passing through the lubricating oil throttle / supply passage 34, and at the same time, wear is prevented against the sliding portion between the outer peripheral surface of the drive shaft 3 and the inner peripheral surface of the extending portion 42. After having acted as a lubricant for the air, it reaches the back pressure chamber 23 through the passage 31 and pushes the vane 6 toward the cam ring 2 side. In addition, the gap between the end surface of the rotor 4 and the rotor side surface of the rear side block 7 is formed. It acts as a lubricant for preventing wear on the sliding portion between the end surface of the rotor 4 and the rotor side surface of the rear side block 7.

  Furthermore, also in this embodiment, the lubricating oil moves in the back pressure chamber 23 along the axial direction of the drive shaft 3 and reaches the opening end on the side of the front side block 8 described above, and then is opposite to the passage 31. Lubricant for preventing wear on the sliding portion between the end surface of the rotor 4 and the rotor side surface of the front side block 8 by entering the gap between the end surface of the rotor 4 and the side surface of the rotor of the front side block 8 through the passage located on the side Work as.

  Although not shown, a groove having the same shape as the groove 35 of the plain bearing 11 described above is formed on the extending side surface of the extending part 42, or a recessed part similar to the recessed part 39 described above is formed on the drive shaft 3. And it is good also as what has the lubricating oil non-throttle passage part which functions similarly to the lubricating oil non-throttle passage part 40 mentioned above. As a result, the supply amount of the lubricating oil is secured, so that the dimension in the drive shaft radial direction of the lubricating oil throttling / supplying passage 34 is the same value L1 as the lubricating oil throttling passage 29 of the first embodiment, for example, 10 micron. Can be meters.

The bearing structure of the vane type compressor according to the present invention is:
A cam ring closed by being sandwiched between two side blocks, a rotor housed in the cam ring and formed with a plurality of vane grooves, and housed in the vane grooves of the rotor. The vane slides on the inner surface of the vane groove, and a vane whose tip protrudes and protrudes from the vane groove and slides on the inner peripheral surface of the cam ring, and is connected to the rotor to transmit a rotational force from the outside to the rotor. In a vane type compressor having at least a drive shaft and a lubricant chamber formed in the side block and in which a lubricant is temporarily stored,
The drive shaft is rotatably supported by the side block via a plain bearing. The plain bearing is formed on a cylindrical body through which the drive shaft can be inserted, and on an outer side from one axial end of the cylindrical body. And a flange portion extending toward the surface, and a gap is provided between the flange portion of the plain bearing and the end surface of the side block. Yes.

  The technical field of the present invention relates to the structure of a vane compressor used in, for example, a vehicle air conditioner, and more particularly to the structure of a bearing for rotatably supporting a drive shaft.

Problems to be solved by the present invention are as follows.
By the applicant of the present application, for example, in paragraph “0022” of the specification of Japanese Patent Application No. 2006-231586 (unpublished), the drive shaft 3 is a shell member corresponding to the front side block 8 and a rear side member corresponding to the rear side block 7. In US Pat. No. 6,048,831, to support rotatably through a plain bearing. However, the plain bearing is not shown in the drawings attached to the above-mentioned patent application, and whether or not the plain bearing has a flange portion is not specifically described. The flange portion 11b of the plain bearing 11 of the present invention is not described. A solution means is shown in which it is used for clearance management between the rotor 4 and the rear side block 7 (the front side block 8 is also possible) in contact with the rotor 4 and the surface treatment on the end surfaces of the side blocks 7 and 8 is not required. It is not.

  That is, in the present invention, as shown in FIGS. 4, 6, 7, and 11, the flange portion 11 b of the plain bearing 11 is substantially in contact with the rotor 4, and between the rear side block 7. Is provided with a clearance with a predetermined dimension value L3. This clearance is a restoring force generated when the load is pushed into the drive shaft storage space 26 of the rear side block 7 after the drive shaft 3 with the rotor 4 and the plain bearing 11 mounted thereon is pushed in. Can be generated. Because of this clearance, the surface of the plain bearing 11 on the rotor 4 side protrudes, for example, about 20 micrometers from the sliding surface of the rear side block 7, and therefore the Teflon (registered) with respect to the end surface of the rear side block 7 on the rotor 4 side. The effect of eliminating the need for surface treatment such as coating with a trademark) is obtained.

FIG. 1 is a cross-sectional view showing a state in which a rear side block side is viewed from the axial direction of a drive shaft in a vane type compressor according to the present invention. FIG. 2 is a cross-sectional view showing the overall configuration of the first embodiment of the vane type compressor as seen from the side. FIG. 3 is a cross-sectional view showing a state in which the overall configuration in the first embodiment of the vane type compressor is viewed from the side, and is a cross-sectional view showing a configuration cut at a cut end different from FIG. . FIG. 4 shows a lubricating oil throttle passage formed by a plain bearing and a drive shaft, which are main components of the first embodiment of the vane type compressor, and a lubricating oil formed by a rear side block and a drive shaft. It is the principal part expanded sectional view which showed the structure of the supply channel | path. FIG. 5 is a cross-sectional view showing a route through which lubricating oil flows in the first embodiment of the vane type compressor. FIG. 6 is an enlarged cross-sectional view of a main part showing a configuration in which both a lubricating oil throttle passage and a lubricating oil supply passage are formed by a plain bearing and a drive shaft as a modification of the first embodiment of the vane type compressor. It is. FIG. 7 is a cross-sectional view showing a configuration of a lubricating oil throttle portion formed by a plain bearing and a drive shaft in the second embodiment of the vane type compressor. FIG. 8 is a cross-sectional view showing a route through which lubricating oil flows in the second embodiment of the vane type compressor. FIG. 9 is a perspective view showing a configuration in which a groove is formed on the inner surface of a plain bearing as a first modification of the second embodiment of the vane type compressor. FIG. 10 is a plan view showing the configuration of the plate material that has been subjected to press processing for forming the plain bearing same as above and before the final roll is formed. FIG. 11 is a cross-sectional view showing a lubricating oil throttle portion formed by a plain bearing and a drive shaft and having a groove in a first modification of the second embodiment 2 of the vane compressor according to the first embodiment. . FIG. 12A shows a shaft of the drive shaft in a configuration in which a recess is formed by chamfering a part of the outer peripheral surface of the drive shaft as a second modification of the second embodiment 2 of the vane compressor of the above. FIG. 12B is a cross-sectional view showing a state viewed from the direction, and FIG. 12B is a diagram of chamfering a part of the outer peripheral surface of the drive shaft as a second example 2 modified example 2 of the same vane type compressor. It is sectional drawing which shows the state seen from the radial direction of the said drive shaft about the structure which formed the hollow part. FIG. 13 is a cross-sectional view showing a configuration of a lubricating oil throttle portion formed by an extension portion extending from a side block and a drive shaft in a third embodiment of the vane type compressor same as above.

Explanation of symbols

1 Vane Compressor 2 Cam Ring 3 Drive Shaft 4 Rotor 5 Vane Groove 6 Vane 7 Rear Side Block (Rear Side Block)
8 Front side block (front side block)
11 Plain bearing 27 Relay passage 28 Extending portion 29 Lubricating oil throttle passage (lubricant throttle passage)
30 Lubricating oil supply passage (lubricant supply passage)
34 Lubricating oil throttling and supply combined passage (lubricant throttling passage)
35 Groove 37 Plate material 38 Folding allowance 39 Recessed portion 40 Lubricating oil non-throttle passage portion 42 Extension portion

Claims (7)

A cam ring closed by being sandwiched between two side blocks, a rotor housed in the cam ring and formed with a plurality of vane grooves, and housed in the vane grooves of the rotor. A vane that slides on the inner surface of the vane groove and has a tip protruding and retracting from the vane groove and sliding on the inner peripheral surface of the cam ring, and is supported by the both side blocks and connected to the rotor from the outside. In the vane type compressor having at least a drive shaft that transmits the rotational force of the rotor to the rotor and a lubricant chamber that is formed in the side block and in which the lubricant is temporarily stored,
An annular lubricant restricting passage is formed on the outer peripheral side of the drive shaft, and the lubricant restricting passage is communicated with the lubricant chamber through at least a relay passage, and the lubricant restricting passage or the lubricant A lubricant supply passage communicating with the downstream side of the throttle passage is extended at least to a sliding portion between the rotor end surface and the rear side block, so that the lubricant from the lubricant chamber is drawn into the lubricant throttle passage. A lubricant pressure reducing supply structure for a vane compressor, comprising a lubricant moving path capable of supplying pressure to a sliding portion between the rotor end face and the side block. The drive shaft is supported by the rear side block by mounting a plain bearing, which is a separate member from the rear side block, on the outer peripheral side of the drive shaft, and the lubrication. 2. The lubricant pressure reducing supply structure for a vane type compressor according to claim 1, wherein the agent throttle passage is formed by a gap generated by mounting the plain bearing on the drive shaft. The drive shaft is supported by the rear side block by mounting a plain bearing, which is a separate member from the rear side block, on the outer peripheral side of the drive shaft, and the lubricant. The supply passage is formed by a gap formed between the outer peripheral surface of the drive shaft and the inner surface of the plain bearing, and the lubricant throttle passage is formed by the outer block of the drive shaft and the side block on the rear side. Of the extended portion extending in the radial direction of the drive shaft from the surface of the extended portion facing the drive shaft, and the radial width of the drive shaft of the lubricant supply passage is 2. The lubricant decompression and supply structure for a vane compressor according to claim 1, wherein the lubricant throttle passage is smaller than a radial width of a drive shaft. The drive shaft is supported by the rear side block by mounting a plain bearing, which is a separate member from the rear side block, on the outer peripheral side of the drive shaft, and the lubrication. The lubricant supply passage and the lubricant throttle passage are formed by a gap formed between the outer peripheral surface of the drive shaft and the inner surface of the plain bearing, and the radial width of the drive shaft of the lubricant supply passage is 2. The lubricant decompression and supply structure for a vane compressor according to claim 1, wherein the lubricant throttle passage is smaller than a radial width of a drive shaft. 5. The groove according to claim 2, wherein one or more grooves are provided in a portion of the inner surface of the plain bearing facing the outer peripheral surface of the drive shaft. Lubricant decompression supply structure of vane type compressor. The one or two or more parts which oppose the inner surface of the said plain bearing among the outer peripheral surfaces of the said drive shaft were dented rather than the other part of the outer peripheral surface of the said drive shaft, The claim 2 characterized by the above-mentioned. 3. A lubricant decompression supply structure for a vane type compressor according to claim 3 The drive shaft is supported by the rear side block by an extending portion extending in the radial direction of the drive shaft from the rear side block, and the lubricant throttle passage is formed by the drive shaft. 2. The lubricant decompression and supply structure for a vane compressor according to claim 1, wherein the lubricant pressure reduction structure is formed by a gap formed between an outer peripheral surface of the shaft and a surface of the extending portion facing the drive shaft.

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