WO2017094639A1

WO2017094639A1 - Vane-type compressor

Info

Publication number: WO2017094639A1
Application number: PCT/JP2016/085105
Authority: WO
Inventors: 美男廣田; 大沢　仁
Original assignee: 株式会社ヴァレオジャパン
Priority date: 2015-11-30
Filing date: 2016-11-28
Publication date: 2017-06-08
Also published as: JPWO2017094639A1

Abstract

[Problem] To restrain a drive shaft from moving axially relative to a rotor with a simple configuration, even when liquid compression has caused the drive shaft and the rotor mounted thereon to slip in a circumferential direction relative to one another. [Solution] A movement-restraining member, which restrains a drive shaft 2 from moving axially relative to a rotor 3, is provided to an outer peripheral surface on the side opposite of the side where the drive shaft 2 protrudes out of a housing. This movement-restraining member, which is configured from a ring-shaped member 50 and fixed by pressure-fitting to the outer peripheral surface of the drive shaft 2, is preferably accommodated in an annular recessed section 3b provided in the peripheral edge of an open end of an insertion hole 3a of the rotor 3, through which the drive shaft 2 is inserted.

Description

Vane type compressor

The present invention relates to a vane type compressor, and more particularly to a vane type compressor provided with a mechanism for preventing a drive shaft from being displaced in an axial direction with respect to a rotor due to liquid compression at start-up.

In general, as shown in FIG. 4, the vane compressor includes a housing 5 that forms a low-pressure space and a high-pressure space, and a cylinder forming portion 12 that forms a cam surface 11 and forms a part of the housing 5. The cylinder forming part 12 is closed at both ends in the axial direction, and a pair of side

block forming parts

13 and 21 constituting a part of the housing 5, and the pair of side

block forming parts

13 and 21

via bearings

14 and 24. Drive shaft 2 rotatably supported, rotor 3 fixed to drive shaft 2 and rotatably accommodated in cylinder forming portion 12, a plurality of vane grooves 6 formed in rotor 3, and vane grooves 6 and a plurality of vanes 4 that slides on the cam surface 11 with the tip protruding and retracting from the vane groove 6 and closed by the cylinder forming portion 12 and the pair of side

block forming portions

13 and 21. Sky The compression chamber 41 by the rotor 3 and the vanes 4 are defined, it sucks the working fluid from the low pressure space into the compression chamber 41, so as to discharge the high-pressure space after compression.

The drive shaft 2 protrudes from the housing 5 (second side block forming portion 21) to the outside in order to transmit rotational power from the outside. In a clutch type compressor, the drive shaft 2 protrudes from the housing 5 of the drive shaft 2. The clutch plate 35 of the electromagnetic clutch 32 that is opposed to the pulley 31 rotatably provided on the boss portion 23 of the housing 5 with a predetermined gap is fixed to the front end portion. The rotor 3 is firmly fixed to the outer peripheral surface of the drive shaft 2 by shrink fitting or the like.

In such a vane type compressor, when the liquid refrigerant or oil is present in the cylinder forming portion 12, the liquid is compressed, and the pressure in the compression chamber 41 becomes extremely high. Excessive force acts on the vane 4 and the rotor 3 that supports it.
As described above, the rotor 3 and the drive shaft 2 are firmly fixed by shrinkage fitting or the like. However, if excessive pressure due to liquid compression acts on the rotor 3 or the vane 4, the rotor 3 and the drive shaft 2 are separated from each other. The maximum static frictional force is exceeded and the rotor 3 and the drive shaft 2 slip relative to each other in the circumferential direction. Once such a slip occurs, the frictional force between the rotor 3 and the drive shaft 2 becomes a dynamic frictional force that is smaller than the maximum static frictional force. That is, when the rotor 3 and the drive shaft 2 slip relative to each other in the circumferential direction, the frictional force between the rotor 3 and the drive shaft 2 decreases.

On the other hand, the high pressure in the compression chamber 41 during liquid compression is driven through the clearance between the rotor 3 and the side block forming portion 13 and the clearance between the bearing 14 and the drive shaft 2 or the side block forming portion 13. The pressure sneaks behind the shaft 2 and the sneak pressure acts on the rear end of the drive shaft 2. As described above, when the rotor 3 and the drive shaft 2 slip relative to each other in the circumferential direction, the frictional force between the rotor 3 and the drive shaft 2 is reduced. And the drive shaft 2 not only slip in the circumferential direction, but also the drive shaft 2 is urged toward the front end side by the high pressure acting on the rear end of the drive shaft 2 and moves in the axial direction with respect to the rotor 3. Phenomenon occurs.

When such movement of the drive shaft 2 in the axial direction occurs, the distance (clutch gap α) between the clutch plate 35 of the electromagnetic clutch 32 provided at the front end portion of the drive shaft 2 and the pulley 31 (clutch gap α) increases. In this case, it is difficult to reliably attract the clutch plate 35, and there arises a problem that the rotational power cannot be reliably transmitted.

Therefore, in order to deal with such inconvenience, for example, as shown in FIG. 5, after the drive shaft 2 is inserted into the insertion hole 3 a of the rotor 3, the end surface of the rotor 3 is pressurized with a die 100, thereby A configuration in which a part of the rotor 3 is plastically flowed in the outer peripheral groove portion 101 of the drive shaft 2 to integrate the rotor 3 and the drive shaft 2 is also useful (see Patent Document 1).

According to such a configuration, even when the drive shaft 2 and the rotor 3 slip relative to each other in the circumferential direction due to liquid compression, the axial movement of the drive shaft 2 with respect to the rotor 3 is restricted. The distance (clutch gap α) between the clutch plate 35 of the electromagnetic clutch 32 and the electromagnetic clutch 32 facing this is not increased, and the clutch plate 35 can be reliably attracted when the clutch is operated.

JP-A-8-189486

However, in the configuration shown in Patent Document 1, in order to restrict the movement of the drive shaft in the axial direction with respect to the rotor, the end surface of the rotor is pressed with a die and a part of the rotor is formed in the outer circumferential groove formed on the drive shaft. Since the drive shaft and the rotor are integrated by plastic flow, the formation of a structure that restricts the movement of the drive shaft in the axial direction relative to the rotor becomes large, and a part of the rotor is plastic flowed. As a result, the dimensional accuracy has a considerable influence, and strict dimensional management is required.

The present invention has been made in view of such circumstances, and even if the rotor and the drive shaft slip relative to each other in the circumferential direction due to liquid compression, the axial direction of the drive shaft relative to the rotor can be reduced with a simple configuration. The main object is to provide a vane type compressor capable of regulating movement.

In order to achieve the above object, a vane type compressor according to the present invention includes a housing, a cylinder forming portion that forms a cam surface, and that forms part of the housing, and both ends of the cylinder forming portion in the axial direction. A pair of side block forming portions that are closed and constitute a part of the housing, and are rotatably supported by the pair of side block forming portions via bearings, and one end of the side block forming portion from the one side block forming portion to the outside of the housing A projecting drive shaft, a rotor fixed to the drive shaft and rotatably accommodated in the cylinder forming portion, a plurality of vane grooves formed in the rotor, and a slidably inserted into the vane groove , In a space closed by a plurality of vanes whose front end portions protrude and retract from the vane grooves and slide on the cam surface, the cylinder forming portion, and the pair of side block forming portions. In a vane-type compressor including a compression chamber defined by the rotor and the vane, an axial movement of the drive shaft relative to the rotor is restricted on an outer peripheral surface on the other end side of the drive shaft. A movement restricting member is provided.

Therefore, since the movement restricting member for restricting the axial movement of the drive shaft relative to the rotor is provided on the outer peripheral surface of the drive shaft opposite to the side protruding from the housing, the rotor and the drive shaft are assumed to be relatively relative to each other. Even if the frictional force between the rotor and the drive shaft decreases due to slippage in the circumferential direction, the movement restricting member restricts the axial movement of the drive shaft relative to the rotor due to the pressure difference between both ends of the drive shaft. It becomes possible to do.
For this reason, in the compressor provided with the electromagnetic clutch, there is no inconvenience that the distance between the pulley and the clutch plate facing the pulley is widened, and it is possible to maintain a stable suction force.

Here, it is preferable that the drive shaft has an outer diameter of a portion where the rotor is fixedly set smaller than an outer diameter of a portion supported by the bearing on the one end side.
According to such a configuration, since the outer diameter of the rotor can be reduced, it is possible to suppress movement of the drive shaft in the axial direction while responding to a demand for downsizing of the compressor.

The movement restricting member is formed of a ring-shaped member, and is fixed to the outer peripheral surface of the drive shaft by press-fitting, and is provided in an annular recess provided in an inner peripheral wall of an insertion hole through which the drive shaft of the rotor is inserted. It is preferable to be accommodated.

By making the movement restricting member a ring-shaped member, it becomes easy to manage the press-fitting allowance, and the movement restricting member is housed in an annular recess provided in the inner peripheral wall of the insertion hole through which the drive shaft of the rotor is inserted. This eliminates the inconvenience of interference between the movement restricting member fixed to the outer peripheral surface of the drive shaft and the bearing supporting the drive shaft. Also, in order to avoid interference, the position of the bearing is provided far away from the rotor, or the bearing There is no inconvenience of enlarging the diameter and providing it outside the movement restricting member.

Further, in consideration of ease of press-fitting into the drive shaft, the ring-shaped member may be tapered at least at the axial end of the inner peripheral surface facing the rotor.

Further preferably, a retreating portion for avoiding contact with the rotor is formed at least on an axial end of the outer peripheral surface of the ring-shaped member on the side facing the rotor, whereby the radial thickness of the ring-shaped member is increased. A portion closer to the drive shaft than the center may be in contact with the rotor.
When the contact part between the ring-shaped member and the rotor is a part outside the center of the radial thickness (part away from the drive shaft), the part where the axial end surface of the rotor contacts the ring-shaped member However, when the rotor and the ring-shaped member come into contact with each other, the torque generated by the slip in the circumferential direction of the rotor increases, and the possibility that the ring-shaped member rotates together with the rotor increases. With such a configuration, the radial position of the contact portion between the rotor and the ring-shaped member can be moved inward, so even if the ring-shaped member contacts the rotor that slips in the circumferential direction, the ring The torque received by the ring-shaped member can be reduced, and the risk of co-rotation of the ring-shaped member can be suppressed.

The housing of the vane compressor is not particularly limited, but the housing includes a cylinder forming portion having a cam surface formed on the inner peripheral surface and a first end side in the axial direction of the cylinder forming portion. A first housing member integrally formed with one side block forming portion; a second side block forming portion that closes the other axial end of the cylinder forming portion; and You may make it comprise combining the 2nd housing member integrally formed with the shell formation part which covers an outer peripheral surface.

As described above, according to the present invention, the movement restricting member for restricting the axial movement of the drive shaft relative to the rotor is provided on the outer peripheral surface of the drive shaft opposite to the side protruding from the housing. Therefore, even if the frictional force between the rotor and the drive shaft becomes a dynamic frictional force, the axial movement of the drive shaft with respect to the rotor can be restricted by the movement restricting member press-fitted into the drive shaft.
Therefore, in the compressor provided with the electromagnetic clutch, there is no inconvenience that the distance between the pulley and the clutch plate facing the pulley is increased, and a stable suction force can be maintained.

In particular, the movement restricting member is composed of a ring-shaped member, and is fixed to the outer peripheral surface of the drive shaft by press-fitting and accommodated in an annular recess provided in the inner peripheral wall of the insertion hole through which the drive shaft of the rotor is inserted. It becomes easy to manage the press-fitting allowance of the movement restricting member, and there is no inconvenience that the movement restricting member interferes with the bearing. For this reason, in order to avoid interference between the movement restricting member and the bearing, there is no inconvenience that the position of the bearing is provided far away from the rotor or the diameter of the bearing is increased and provided outside the movement restricting member. It becomes possible to achieve downsizing.

FIG. 1 is a view showing a vane type compressor according to the present invention, and (a) is a side sectional view of the compressor. Further, (b) is a cross-sectional view taken along the line AA in (a), and shows the rotor and vanes in phantom lines. FIG. 2A is a side sectional view showing a state in which a rotor is fixed to a drive shaft, FIG. 2A is a diagram showing the entire configuration, and FIG. 2B is a view showing a movement restricting member (link-like member). It is an expanded sectional view showing the neighborhood. 3A and 3B are diagrams showing another example of the movement restricting member (link-like member), where FIG. 3A is a sectional view showing the vicinity of the movement restricting member (link-like member), and FIG. It is an expanded sectional view showing a member (link-like member). FIG. 4 is a side sectional view showing a conventional vane type compressor. FIG. 5 is a diagram for explaining a conventional configuration that regulates axial movement of the drive shaft and the rotor.

Hereinafter, the vane type compressor according to the present invention will be described with reference to the drawings.

FIG. 1 shows a vane compressor 1 suitable for a refrigeration cycle using a refrigerant as a working fluid. The vane compressor 1 includes a drive shaft 2, a rotor 3 that is fixed to the drive shaft 2 and rotates as the drive shaft 2 rotates, a vane 4 attached to the rotor 3, and the drive shaft 2. A housing 5 that supports the rotor 3 and the vanes 4 while supporting the rotor 3 and the vanes 4 is provided. In FIG. 1, the left side is the front side and the right side is the rear side.

The housing 5 is configured by combining two members of a first housing member 10 and a second housing member 20. The first housing member 10 houses the rotor 3 and has a cam surface 11. The cylinder forming portion 12 is formed on the inner peripheral surface, and the first side block forming portion 13 is integrally formed so as to close one end side (rear side) of the cylinder forming portion 12 in the axial direction. ing. The inner peripheral surface (cam surface 11) of the cylinder forming portion 12 is formed in a perfect circle in cross section, and the axial length is substantially equal to the axial length of the rotor 3 described later.

The second housing member 20 includes a second side block forming portion 21 that is in contact with an end face on the other end side (front side) in the axial direction of the cylinder forming portion 12 and closes the other end side. A shell forming portion formed integrally with the side block forming portion 21 and extending in the axial direction of the drive shaft 2 so as to surround the outer peripheral surfaces of the cylinder forming portion 12 and the first side block forming portion 13. 22.

The first housing member 10 and the second housing member 20 are fastened in the axial direction via fastening bolts 9, and the first side block forming portion 13 of the first housing member 10 and the second housing member 10 are fastened. A seal member 7 such as an O-ring is interposed between the shell forming portion 22 of the housing member 20 and the housing member 20 is hermetically sealed.

In addition, the second housing member 20 is integrally formed with a boss portion 23 extending from the second side block forming portion 21 to the front side. A pulley 31 (shown by an alternate long and short dash line) that transmits rotational power to the drive shaft 2 is rotatably mounted on the boss portion 23, and rotational power is transmitted from the pulley to the drive shaft 2 via an electromagnetic clutch 32. It has become.

The drive shaft 2 is rotatably supported by the first side block forming portion 13 and the second side block forming portion 21 via bearings 14 and 24 (for example, plain bearings), and the front end portion is The second housing member 20 protrudes into the boss portion 23 and is hermetically sealed with the boss portion 23 by a seal member 25 provided between the boss portion 23 and the second boss portion 23. Therefore, the atmospheric pressure acts on the front end portion of the drive shaft 2 in a state of protruding to the outside of the housing 5.
Further, the drive shaft 2 has at least one portion having an outer diameter larger than the outer diameter of the portion where the rotor 3 is fixed, on the front side of the portion where the rotor 3 is fixed. In this example, the outer diameter of the portion where the rotor 3 is fixed is smaller than the outer diameter of the portion supported by the front bearing 24 where strength is required.

The electromagnetic clutch 32 is connected to a front end protruding from the second housing member 20 (second side block forming portion 21) of the drive shaft 2 via a leaf spring 34 attached in the axial direction with a bolt 33. The clutch plate 35 is fixed so as to oppose the friction surface 31 a of the pulley 31, and the clutch plate 35 is attracted to the pulley 31 by energization of the excitation coil 36 included in the pulley 31. Is transmitted to the drive shaft 2 via the clutch plate 35 and the plate spring 34.

On the other hand, the rear end portion of the drive shaft 2 is inserted into the bottomed support concave portion 15 formed in the first side block forming portion 13 while leaving a space 15a between the bottom portion and the drive shaft 2 after being inserted. The bearing 14 is provided around the end.

The rotor 3 has a perfect circular cross section, and the drive shaft 2 is inserted through an insertion hole 3a provided at the center of the rotor 3 so that the shaft centers coincide with each other, and the rotor 3 is shrink-fitted or the like. It is fixed by. Further, the axial center O ′ of the inner peripheral surface (cam surface 11) of the cylinder forming portion 12 and the axial center O of the rotor 3 (drive shaft 2) are the outer peripheral surface of the rotor 3 and the inner peripheral surface of the cylinder forming portion 12 ( The cam surface 11) is shifted so as to come into contact with one place in the circumferential direction (offset by a half of the difference between the inner diameter of the cylinder forming portion 12 and the outer diameter of the rotor 3). . In the space closed by the cylinder forming portion 12, the first side block forming portion 13, and the second side block forming portion 21, the inner peripheral surface (cam surface 11) of the cylinder forming portion 12 and the rotor 3 A compression space 40 is defined between the outer peripheral surface and the outer peripheral surface.

The second housing member 20 is formed with a suction port for sucking working fluid (refrigerant gas) from the outside and a discharge port for discharging the working fluid (refrigerant gas) to the outside (not shown), and a cylinder forming portion of the first housing member 10 12, a suction port is provided near the front side in the rotational direction of the rotor 3 with respect to a portion (radial seal portion 45) in which the outer peripheral surface of the rotor 3 is in sliding contact with the inner peripheral surface (cam surface 11) of the cylinder forming portion 12. A suction port 16 that communicates is formed, and a discharge port 17 that communicates with the discharge port is formed in the vicinity of the rear side in the rotational direction of the rotor 3. In FIG. 1B, reference numeral 18 denotes a screw hole for screwing the connector.

The discharge port 17 has a counterbore 17a that is recessed in a curved shape along the circumferential direction at the opening end with the inner peripheral surface (cam surface 11) of the cylinder forming portion 12, and the compressed gas is stored in this seat. It is discharged through the bore 17a. A discharge chamber 37 is formed over a predetermined range in the circumferential direction between the cylinder forming portion 12 of the first housing member 10 and the shell forming portion 22 of the second housing member 20. The discharge chamber 37 is opened and closed by a discharge valve 38 provided in the discharge chamber 37 so as to be opened and closed.

Further, a discharge space 39 to which a discharge port is connected is formed between the first side block forming portion 13 of the first housing member 10 and the shell forming portion 22 of the second housing member 20, and the discharge chamber 37. Communicates with the discharge space 39 via an oil separator 28.
The discharge chamber 37 and the discharge space 39 constitute a high-pressure space that accommodates the fluid discharged from the discharge port 17. Further, the oil separated from the working fluid by the oil separator is provided between the lower portion of the first side block forming portion 13 of the first housing member 10 and the lower portion of the shell forming portion 22 of the second housing member 20. An oil reservoir chamber 18 for storing (having a pressure corresponding to the pressure of the discharge gas) is provided.

A plurality of vane grooves 6 are formed on the outer peripheral surface of the rotor 3, and the vanes 4 are slidably inserted into the respective vane grooves 6. The vane groove 6 is opened not only on the outer peripheral surface of the rotor 3 but also on the end surface facing the first side block forming portion 13 and the second side block forming portion 21, and a back pressure chamber 6 a is formed at the bottom portion. Has been. A plurality of the vane grooves 6 are formed at equal intervals in the circumferential direction, and in this example, the vane grooves 6 are formed so as to be parallel to each other at two positions different in phase by 180 degrees, and a plane including the vane 4; A plane parallel to the vane 4 and including the axis O of the drive shaft 2 is formed (offset) by a predetermined distance.

The vane 4 is formed such that the width along the axial direction of the drive shaft 2 is equal to the axial length of the rotor 3, and the length in the insertion direction (sliding direction) into the vane groove 6 is the length of the vane groove 6. It is formed approximately equal to the length in the same direction. The vane 4 protrudes from the vane groove 6 due to the back pressure supplied to the back pressure chamber 6 a of the vane groove 6, and the tip part can come into contact with the inner peripheral surface (cam surface 11) of the cylinder forming part 12. ing.

Therefore, the compression space 40 is partitioned into a plurality of compression chambers 41 by the vanes 4 slidably inserted into the vane grooves 6, and the volume of each compression chamber 41 changes as the rotor 3 rotates. ing.

The first side block forming portion 13 has an end surface facing the end surface in the axial direction of the rotor 3, and a first recess 42 and a second recess that can communicate with the back pressure chamber 6 a provided at the bottom of the vane groove 6. A recess 43 is formed.

The first recess 42 communicates with the oil reservoir chamber 18, and extends from the position of the radial seal portion 40 to a position just before the discharge port 17 (before the counterbore 17 a). The tip of the vane 4 is communicated with the bottom of the vane groove 6 (the back pressure chamber 6a) in a stroke in front of the discharge port 17 from the radial seal portion 40.

On the other hand, the second recess 43 communicates with the discharge space 39, and the position where the tip end portion of the vane 4 is located at the discharge port 17, in this example, the position approaching the discharge port 17 (the counterbore 17a). From the start end of the vane 4 to the radial seal portion 40, and communicates with the bottom portion of the vane groove 6 (back pressure chamber 6a) in a stroke in which the tip end portion of the vane 4 is in the range from the discharge port 17 to the radial seal portion 40. It is supposed to be.

Accordingly, when the bottom portion (back pressure chamber 6a) of the vane groove 6 communicates with the first recess 42, oil having a pressure corresponding to the discharge pressure supplied from the oil reservoir chamber 18 is sent to the back pressure chamber 6a. When the bottom (back pressure chamber 6a) of the groove 6 communicates with the second recess 42, the discharge gas supplied from the discharge space 39 is directly fed into the back pressure chamber 6a.

In this example, a movement restricting member for restricting the movement of the drive shaft 2 relative to the rotor 3 in the axial direction is provided on the outer peripheral surface that does not interfere with the bearing 14 on the rear end side of the drive shaft 2. In this example, the movement restricting member is constituted by a ring-shaped member 50 fixed to the outer peripheral surface of the drive shaft 2 by press-fitting.
The outer diameter of the drive shaft where the ring-shaped member 50 is press-fitted may be formed to be the same as or slightly smaller than the outer diameter of the part where the rotor is press-fitted. Further, in order to facilitate the attachment of the ring-shaped member 50 to the drive shaft, the outer diameter of the drive shaft on the insertion start end side where the ring-shaped member 50 is press-fitted is slightly reduced, so that the ring-shaped member 50 You may make it function as a guide at the time of press fit.

Further, the ring-shaped member 50 is disposed inside the rotor. Specifically, as shown in FIG. 2, among the inner peripheral wall of the insertion hole 3 a through which the drive shaft 2 of the rotor 3 is inserted, there is a gap between the opening peripheral edge on the rear end side and the outer peripheral surface of the drive shaft 2. An annular recess 3b is formed, and the ring-shaped member 50 is accommodated in the annular recess 3b so that the insertion end thereof faces the rotor.

Here, the outer diameter of the ring-shaped member 50 is larger than the inner diameter of the rotor 3, so that the ring-shaped member 50 can come into contact with the rotor when the drive shaft to which the ring-shaped member 50 is press-fitted and moved moves in the axial direction. ing.
The axial length of the ring-shaped member 50 is set to be shorter than the axial length of the annular recess 3b, and is fixed so as not to contact the first side block forming portion 13. The ring-shaped member 50 may be fixed in a state of being in contact with the rotor 3 in the axial direction, but the drive shaft 2 is displaced in the axial direction with respect to the rotor 3 and is in contact with the end surface of the rotor 3. Even in such a case, it is preferable to leave a slight clearance so that the distance (clutch gap α) between the pulley 31 and the clutch plate 35 of the electromagnetic clutch 32 does not exceed the allowable range.
Further, the outer peripheral surface of the ring-shaped member 50 is set so that a predetermined clearance is formed with respect to the inner peripheral surface of the annular recess 3b of the rotor 3 (so as not to contact the rotor in the radial direction). It is fixed to the outer peripheral surface of the drive shaft 2).

Further, in this example, the ring-shaped member 50 is tapered at both ends in the axial direction of the inner peripheral surface so that it can be smoothly pressed into the outer peripheral surface of the drive shaft.

In the above configuration, when the compressor is started in a state where liquid refrigerant or oil is present in the cylinder forming portion 12, the liquid is compressed. Then, the pressure in the compression chamber 41 becomes extremely high, and an excessive force acts on the vane 4 and the rotor 3 that supports the vane 4. When this force exceeds the maximum static friction force between the rotor 3 and the drive shaft 2, The rotor 3 starts to slip in the circumferential direction of the drive shaft 2.

When the pressure in the compression chamber 41 becomes extremely high, the clearance between the rotor 3 and the first side block forming portion 13 and the clearance between the bearing 14 and the drive shaft 2 or the first side block forming portion 13 are also shown. The pressure in the space 15a behind the drive shaft 2 is increased through the pressure, and a large difference occurs in the pressure acting on both ends of the drive shaft 2.

Once the circumferential slip between the drive shaft 2 and the rotor 3 occurs, the friction force between the drive shaft 2 and the rotor 3 becomes a dynamic friction force smaller than the maximum static friction force. That is, when the rotor 3 and the drive shaft 2 slip relative to each other in the circumferential direction, the frictional force between the rotor 3 and the drive shaft 2 is reduced. For this reason, even if the drive shaft 2 moves in the axial direction (tip direction) relative to the rotor 3 due to the difference in pressure acting on both ends of the drive shaft 2, Since the ring-shaped member 50 having an outer diameter larger than the inner diameter of 3 is press-fitted and fixed, the axial direction of the drive shaft 2 relative to the rotor 3 when the ring-shaped member 50 abuts the rotor 3 in the axial direction. Will be prevented from moving.

Therefore, there is no inconvenience that the distance (clutch gap α) between the clutch plate 35 of the electromagnetic clutch 32 facing the pulley 31 and the pulley 31 is enlarged, and the clutch plate 35 is reliably attracted when the clutch is operated. There is no inconvenience that 35 cannot slip to the pulley 31 and transmit rotational power.

In the above-described configuration, the outer diameter of the portion of the drive shaft 2 where the rotor 3 is fixed is formed smaller than the outer diameter of the portion supported by the front bearing 24. The outer diameter can be reduced, and the axial slip of the drive shaft can be suppressed while meeting the demand for a smaller diameter compressor.

Furthermore, since the ring-shaped member 50 is accommodated in the annular recess 3b formed on the inner peripheral wall of the rotor 3, the position of the bearing 14 is reduced by providing the ring-shaped member 50 without interfering with the bearing 14. The inconvenience of having to change the diameter of the bearing 14 is also eliminated.
In the above configuration, the example in which the annular recess 3b is provided in the inner peripheral wall of the rotor 3 and the ring-shaped member 50 is accommodated therein is shown. However, if the interference with the bearing 14 can be avoided, the rotor The ring-shaped member 50 may be press-fitted and fixed to the outer peripheral surface between the rotor 3 and the bearing 14 without providing the annular recess 3b in FIG.

FIG. 3 shows another configuration example of the ring-shaped member 50.
The ring-shaped member 50 shown here is provided with a taper 50 a for smoothly press-fitting the ring-shaped member 50 into the outer peripheral surface of the drive shaft 2 at both axial ends of the inner peripheral surface of the ring-shaped member 50. This is the same as the above configuration example.

Further, in order to avoid contact with the rotor 3 on the outer peripheral surface of the ring-shaped member 50, retreat portions 50b are further formed at both ends in the axial direction. The retracting portion 50b may be formed in any way as long as the outer peripheral side of the ring-shaped member 50 is not in contact with the rotor 3, but in this example is formed in a tapered shape.

Tapered retracting portions 50b formed at both axial end portions of the outer peripheral surface of the ring-shaped member 50 are formed larger than the taper 50a at both axial end portions of the inner peripheral surface, and the rotor 3 and the ring-shaped member 50 are formed. The position in the radial direction of the abutting portion is brought closer to the inside (the abutting against the rotor 3 at a portion closer to the drive shaft 2 than the center (center line β) of the radial thickness of the ring-shaped member 50) Possible).

In order to bring the radial position of the contact portion between the rotor 3 and the ring-shaped member 50 inward, it is conceivable to reduce the thickness of the ring-shaped member 50, but the thickness of the ring-shaped member 50 is reduced. Then, the rigidity of the ring-shaped member 50 becomes low, and the binding force when the ring-shaped member 50 is press-fitted into the drive shaft 2 is weakened. As a result, the maximum static frictional force between the ring-shaped member 50 and the drive shaft 2 is lowered, and there is a risk of causing an axial slip of the ring-shaped member 50 with respect to the drive shaft 2. On the other hand, as shown in FIG. 3, a retracting portion 50 b that avoids contact with the rotor 3 is provided at the axial end of the outer peripheral surface of the ring-shaped member 50 without reducing the thickness of the ring-shaped member 50. Therefore, while maintaining the rigidity of the ring-shaped member 50 and securing the strong binding force between the ring-shaped member 50 and the drive shaft 2, the radial position of the contact portion between the ring-shaped member 50 and the rotor 3 is set to the inner side. Can be sent to. For this reason, even when the ring-shaped member 50 comes into contact with the rotor 3 slipping in the circumferential direction, the torque received by the ring-shaped member 50 from the rotor 3 can be reduced, and the ring-shaped member 50 can rotate together. It becomes possible to prevent.

In the above-described configuration, the compressor having two vanes 4 has been described. However, the same configuration can be adopted in three or more vane-type compressors. Shows an example in which the housing 5 is configured by combining the first housing member 10 and the second housing member 20, but the side block forming portion (the first side block forming portion 13, the second side block forming) is shown. A similar configuration may also be adopted in a compressor in which the part 21) is formed as a separate member and assembled.
Furthermore, although the example using the ring-shaped member 50 as a movement restricting member has been shown, a key is press-fitted into another structure provided on the outer peripheral surface of the drive shaft 2, for example, a key groove formed on the outer peripheral surface of the drive shaft. You may make it comprise.

1 vane compressor 2 drive shaft 3 rotor 3a insertion hole 3b annular recess 4 vane 5 housing 6 vane groove 10 first housing member 11 cam surface 12 cylinder forming portion 13 first side

block forming portions

14, 24 bearing 20 first Second housing member 21 Second side block forming portion 41 Compression chamber 50 Ring-shaped member (movement restricting member)
50a Taper 50b Retraction part

Claims

A housing;
A cylinder surface forming a cam surface and forming a part of the housing;
A pair of side block forming parts that closes both axial ends of the cylinder forming part and constitutes a part of the housing;
A drive shaft that is rotatably supported by the pair of side block forming portions via a bearing, and has one end projecting out of the housing from one side block forming portion;
A rotor fixed to the drive shaft and rotatably accommodated in the cylinder forming portion;
A plurality of vane grooves formed in the rotor;
A plurality of vanes that are slidably inserted into the vane grooves, and whose front end portions protrude and retract from the vane grooves and slide on the cam surface;
A compression chamber defined by the rotor and the vane in a space closed by the cylinder forming portion and the pair of side block forming portions;
In a vane compressor equipped with
A vane type compressor, wherein a movement restricting member for restricting movement of the drive shaft in the axial direction relative to the rotor is provided on an outer peripheral surface on the other end side of the drive shaft.
2. The vane compressor according to claim 1, wherein an outer diameter of a portion of the drive shaft where the rotor is fixed is smaller than an outer diameter of a portion supported by the bearing on the one end side. .
The movement restricting member is a ring-shaped member, and is fixed to the outer peripheral surface of the drive shaft by press fitting, and is accommodated in an annular recess provided in an inner peripheral wall of an insertion hole through which the drive shaft of the rotor is inserted. The vane type compressor according to claim 1.
4. The vane type compressor according to claim 3, wherein the ring-shaped member has a taper formed at an end portion in an axial direction at least on the side facing the rotor of an inner peripheral surface thereof.
The ring-shaped member is formed with a retracting portion at an axial end portion at least on the side facing the rotor on the outer peripheral surface thereof, and abuts the rotor at a portion closer to the drive shaft than the center of the radial thickness. The vane type compressor according to claim 3 or 4, wherein the compressor is possible.
The housing is a first housing in which a cylinder forming portion having a cam surface formed on an inner peripheral surface and a first side block forming portion that closes one end side in the axial direction of the cylinder forming portion are integrally formed. A member, a second side block forming portion that closes the other axial end of the cylinder forming portion, and a shell forming portion that covers the outer peripheral surface of the first housing member are integrally formed. The vane compressor according to any one of claims 1 to 5, wherein the vane compressor is configured in combination with a housing member.