JP2012026330A - Vane compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vane compressor capable of being easily centered in assembling the vane compressor whose housing is constructed of two members.SOLUTION: The vane compressor 1 includes a housing 2 constructed by combining a first housing member 8 integrally formed with a cylinder forming part 8a and a side block forming part 8b for blocking the axial one end of the cylinder forming part 8a and a second housing member 9 integrally formed with a shell forming part 9b surrounding the circumferential surface of the first housing member 8 and a front side block forming part 9a for blocking the axial other end of the cylinder forming part 8a, a drive shaft 3 rotatably supported by the rear side block forming part 8b of the first housing member 8 and by the front side block forming part 9a of the second housing member 9, a rotor 4 fixed to the drive shaft 3 and rotatably housed in the cylinder forming part 8a, and vanes 6 slidably inserted in a plurality of vane grooves provided on the rotor 4.

Description

  The present invention relates to a technique for improving the accuracy of alignment (centering) of a bearing portion that holds a drive shaft in assembling a vane compressor.

  In a typical vane compressor, a cylindrical rotor that stores a vane is fixed to a drive shaft that rotates by receiving a driving force of an engine or the like, and the rotor is stored in a circular hole in the cylinder. The front and rear end surfaces are configured to be sealed by a sealing member (referred to as a front / rear head or a side block). The clearance between the short diameter portion of the circular hole of the cylinder and the outer diameter of the rotor needs to be set as small as possible in order to reduce the leakage of the compressed gas to the adjacent compression chamber. Bearings for holding the drive shaft are provided in the sealing means before and after the cylinder. Accurate alignment (centering) of the shaft center of the bearing and the cylinder is the performance of the compressor. It is important to increase reliability.

  In order to cope with the above problem, conventionally, an alignment method using a centering dummy rotor has been considered (see Patent Documents 1 and 2). This dummy rotor for centering is a member having a virtual rotor part and a virtual drive shaft part, and when assembling the cylinder and one of the sealing means, this dummy rotor is arranged in the cylinder. Thus, the center of the elliptical hole of the cylinder and the center of the through hole as the bearing portion of the sealing means are prevented from shifting.

  In addition, as a general alignment method for arranging a plurality of mechanical parts at relatively correct positions, positioning holes are provided in the respective target parts (usually two locations), and positioning is performed in each pin hole. Each part is made by inserting a pin to align the position of each part, or by providing a cylindrical boss on one of the opposing parts and a cylindrical hole on the other, and fitting the boss and hole together. A method of aligning the cores (so-called inlay alignment) is also used, and a rotor fixed to the drive shaft, a vane slidably accommodated in a vane groove formed in the rotor, the rotor and the vane are accommodated. Vane type compressor having a cylinder in which a space is formed, a front side sealing member that seals the front side of the cylinder, and a rear side sealing member that seals the rear side of the cylinder In A configuration is also known in which protrusions protruding in the radial direction of the rotor are formed at the joint portion between the cylinder and the front side sealing member and at the joint portion between the cylinder and the rear side sealing member. Yes. (See Patent Document 3).

JP-A-4-58094 JP-A-11-210651 No. 2008/0264494

  However, in the case of using the centering dummy rotor described in Patent Documents 1 and 2, the housing is constituted by a total of three or more members having a cylinder and two sealing members due to its characteristics. When the vane compressor is assembled, it can be used as a sealing member on one side. Therefore, in order to reduce the components of the vane compressor, a member that integrally forms the cylinder and the side block; It cannot be used when assembling a vane type compressor constituting a housing with two members including a member surrounding the outer peripheral surface of the cylinder.

  By the way, when a needle bearing is used for the bearing of the shaft of the vane type compressor, since there is almost no clearance between the shaft and the bearing, the bearing between the bearings can be simply held by the bearing. Centering is performed automatically. However, when a plain bearing is used as a bearing, this method cannot be used because a clearance is required between the shaft and the bearing.

  Moreover, in the centering by the inlay described in Patent Document 3, an inlay portion is provided in each of the cylinder and the front side sealing member, and the cylinder and the rear side sealing member, and the front side sealing member and the rear side sealing are provided. Since the members are joined via the cylinder, there is a concern about misalignment due to accumulation of errors of the three members.

By the way, the vane type compression in which the housing is composed of two members, a member integrally forming the cylinder and one side block, a member surrounding the outer peripheral surface of the cylinder, and a member integrally forming the other side block. In the machine, when one spigot part is provided in the axial direction as in Patent Document 3, the axial dimension in which one member is included in the other member is long, so that the spigot part is used as a fulcrum when joining both members. Tilting (center misalignment) is likely to occur. Although the inclination is corrected by the contact of the joint surfaces of the members, this correction is not sufficient. Therefore, the inclination may cause misalignment between the two members.
And if a misalignment occurs between the two members, the rotor is inclined with respect to the sealing surface and sliding surface of the cylinder and the side member, so the gap between the sealing portions is not properly maintained and the performance deteriorates. In addition, there is a concern that the sliding surface may be unevenly worn and seized.

  Although it is conceivable that the cylinder is not tilted by centering with the inlay, it is difficult to perform the assembly work while keeping the drive shaft vertical or horizontal. Since the work requires a special centering process, there is a disadvantage that the cost increases.

  The present invention has been made in view of the above-described problems, and has as its main object to provide a vane compressor that can be easily centered when the vane compressor is assembled. .

  The vane type compressor of the present invention includes a first housing member integrally formed with a cylinder forming portion and a side block forming portion that closes one end side in the axial direction of the cylinder forming portion, and the first housing member. A housing is configured by combining a shell forming portion that surrounds the outer peripheral surface of the first housing member and a second housing member integrally formed with a side block forming portion that closes the other axial end of the cylinder forming portion. A drive shaft rotatably supported by the side block forming portion of the first housing member and the side block forming portion of the second housing member, and fixed to the drive shaft and rotatable in the cylinder forming portion A rotor housed therein, and a vane that is slidably inserted into a plurality of vane grooves provided in the rotor; Is characterized in that a projection projecting in a radial direction of the rotor at the junction of the housing member in the circumferential direction.

  A housing is constituted by the first housing member and the second housing member, and in the first housing member, a protrusion projecting in the radial direction of the rotor is formed in a circumferential direction at a joint portion with the second housing member. By providing, it becomes alignment only between the 1st housing member (front side sealing member) and the 2nd housing member (rear side sealing member). That is, since the cylinder forming portion is formed integrally with the first housing member, the number of positioning members is smaller than that of the conventional vane type compressor, and the misalignment due to the accumulation of errors of each member is improved. It becomes possible.

  In addition, it is preferable that a plurality of joint portions between the first housing member and the second housing member are provided at predetermined intervals in the drive shaft direction, and a plurality of protrusions are provided in the circumferential direction. It is possible to prevent the housing member from being inclined by the plurality of joint portions, and it is possible to easily perform centering.

  As a result, the rotor can be prevented from being tilted due to misalignment with respect to the first housing member and the second housing member, so that uneven wear and seizure of the sliding member can be prevented, and the rotor can be prevented. It is possible to reduce the clearance at the sliding contact surface with the drive shaft.

  Furthermore, since it becomes possible to perform centering with an inlay without using a dummy rotor, it can be used for a vane-type compressor comprising a housing with two members, and there is also a special centering process in the assembly process. It becomes unnecessary.

  Here, one of the joint portions between the first housing member and the second housing member is preferably a portion close to the radially outer side of the bearing that supports the drive shaft, and the other one of the joint portions. Is preferably arranged in the vicinity of the contact portion between the insertion end of the first housing member and the side block forming portion of the second housing member in order to obtain a stable support structure.

  Furthermore, it is preferable that the protrusions formed in the respective joint portions are press-fitted almost simultaneously when the first housing and the second housing are assembled.

  A plurality of joint portions with the first housing member formed on the second housing member are formed with different diameters, and the insertion end of the first housing member and the second housing member It is preferable that the diameter is successively larger (expanded) than the joint provided in the vicinity of the joint surface with the side block forming section.

  The circumferential positions of the protrusions formed on the first housing member may be in different phases at a plurality of joints. However, in order to suppress the inclination of the housing as much as possible, they should be provided in substantially the same phase. (It is better to align the circumferential position at a plurality of joints).

  Furthermore, it is desirable that the circumferential position of the protrusion formed on the first housing member is provided so as to avoid a position where the rotor and the cylinder forming portion form a minute gap.

  As described above, according to the present invention, the first housing member and the second housing member constitute a housing, and in the first housing member, the joint portion with the second housing member is arranged in the radial direction of the rotor. Since the protruding protrusions are provided in the circumferential direction, only the first housing member (front side sealing member) and the second housing member (rear side sealing member) are aligned. The number of members is smaller than that of the conventional vane type compressor, and it is possible to improve the misalignment due to the accumulation of errors of the respective members, and the centering can be easily performed.

  Further, a plurality of joint portions between the first housing member and the second housing member are provided at predetermined intervals in the axial direction of the drive shaft, and projections protruding in the radial direction of the rotor are provided around each joint portion. Since a plurality of members are provided in the direction, the housing member is prevented from being inclined by the plurality of joints during assembly, and therefore, centering can be easily performed.

  Therefore, the rotor can be prevented from being inclined due to the misalignment between the first housing member and the second housing member, and the clearance can be reduced on the sliding surface with the drive shaft and the rotor. The performance of the mold compressor can be improved.

  Further, since the inclination of the rotor is eliminated, it is possible to prevent uneven wear and seizure of the sliding member, and it is possible to improve the reliability of the vane type compressor.

  Furthermore, since it is possible to perform centering by using an inlay without using a dummy rotor, it is possible to use it for a vane type compressor that constitutes a housing with two members. Assembling can be performed without providing the manufacturing cost, so that the manufacturing cost can be reduced.

FIG. 1 is a cross-sectional view showing the overall configuration of a vane compressor according to the present invention. FIG. 2 is an explanatory diagram illustrating a side of the first housing member according to the first embodiment having a cylinder hole. FIG. 3 is a perspective view illustrating an assembled state of the vane compressor according to the first embodiment before joining. FIG. 4 is a perspective view illustrating an assembled state of the vane compressor according to the first embodiment after joining. FIG. 5 is an enlarged view showing a joining state of the vane type compressor according to the first embodiment. FIG. 6 is a perspective view illustrating an assembled state of the vane compressor according to the second embodiment.

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

  FIG. 1 shows a vane compressor suitable for a refrigeration cycle using a refrigerant as a working fluid. As shown in FIG. 1 and FIG. 2, the vane compressor 1 includes a drive shaft 3, a rotor 4 fixed to the drive shaft 3 and movable as the drive shaft 3 rotates, The first housing member 8 and the second housing member 9 that define a compression space 18 to be described later, and the first housing member 8 and the second housing member 9 together with the drive shaft 3 and the rotor 4. A housing 2 for storing the like is configured.

  The first housing member 8 includes a cylinder forming portion 8a having a cylinder hole 86 for housing the rotor 4, and the cylinder forming portion 8a is located on the rear side in the axial direction of the drive shaft 3 and is a cylinder forming portion. The rear side block forming portion 8b is integrally formed with 8a and closes one end on the rear side.

  The second housing member 9 includes a front side block forming portion 9a that abuts on the front side end surface of the cylinder forming portion 8a, and outer peripheral surfaces of the cylinder forming portion 8a and the rear side block forming portion 8b that extend in the axial direction of the drive shaft 3. And a shell forming portion 9b formed so as to surround it. The second housing member 9 is connected to the first housing member 8 via a connector 7 such as a bolt. Further, a plurality of sealing members such as O-rings are interposed between the shell forming portion 9b of the second housing member 9 and the cylinder forming portion 8a and the rear side block forming portion 8b of the first housing member 8 so as to be airtight. It is sealed. Further, the second housing member 9 has a boss portion 9c integrated with the front side block forming portion 9a, and a pulley (not shown) for transmitting rotational power to the drive shaft 3 is rotatably mounted on the second housing member 9. Rotational power is transmitted to the drive shaft 3 via an electromagnetic clutch (not shown).

  The space surrounded by the cylinder forming portion 8a and the cross section of the rotor 4 are formed in a perfect circle, and the axial center of the cylinder forming portion 8a and the axial center of the rotor 4 are the outer peripheral surface of the rotor 4 and the cylinder forming portion 8a. The inner peripheral surface 8w (side surface of the cylinder hole 86) is provided so as to be shifted so as to form a minute gap (a portion where the inner wall of the cylinder forming portion 8a and the outer wall of the rotor 4 are closest to each other) in one circumferential direction ( The compression space 18 is provided between the inner peripheral surface 8w of the cylinder forming portion 8a and the outer peripheral surface of the rotor 4 by shifting by about 1/2 of the difference between the inner diameter of the cylinder forming portion 8a and the outer diameter of the rotor 4. Is defined. The compression space 18 is partitioned by the vanes 6 that are slidably inserted into the plurality of vane grooves 5 formed in the rotor 4, and is formed in the plurality of compression chambers 19. It changes with rotation.

  The drive shaft 3 is rotatably supported by the front side block forming portion 9a of the second housing member 9 and the rear side block forming portion 8b of the rear side block forming portion 8b via plain bearings 12 and 13.

  The second housing member 9 has a suction space 14 configured with a suction port 16 and a discharge port 11 for the working fluid (refrigerant gas), and a recess 22 formed in the cylinder forming portion 8a. Is formed. A discharge space 24 described later is defined between the cylinder forming portion 8 a and the shell forming portion 9 b of the second housing member 9, and the discharge space 24 is formed on the rear side block forming portion 8 b of the first housing member 8. It communicates with the discharge port 11 through an oil separator 25 formed in

  The second housing member 9 is formed with a suction port 16 and a discharge port 11 for the working fluid, and a space portion (suction space) located on the radially inner side of the drive shaft 3 with respect to the suction port 16. ) 14, and a suction space (low pressure) is formed by the space portion 14 and a hollow portion (concave portion) 22 formed in the cylinder forming portion 8 a of the first housing member 8 and opened to the second housing member 9 side. (Space) 15 is defined. Further, a discharge space (high pressure space) 24 is defined between the cylinder forming portion 8 a of the first housing member 8 and the shell forming portion 9 b of the second housing member 9. Is in communication with the discharge port 11. Further, an oil separator 25 is disposed between the discharge space 24 and the discharge port 11, and the oil separated from the working fluid by the oil separator 25 is temporarily stored in an oil reservoir chamber 17 described later. .

  3 to 5, the assembled state of the first housing member 8 and the second housing member 9 is shown. As a procedure of the assembling work, the rotor 4 integrated with the drive shaft 3 is placed in the cylinder hole 86 of the cylinder forming portion 8a shown in FIG. 2, and the rear end portion of the drive shaft 3 is placed on the rear side block forming portion 8b. The vane 6 is inserted into the vane groove 5 of the rotor 4. Then, the front side block forming portion 9a of the second housing member 9 is joined to the front surface portion of the cylinder forming portion 8a so as to cover the entire first housing member 8, and the front end portion of the drive shaft 3 is formed as a front side block. It is made to pass through the through hole 90 of the portion 9a.

  As shown in FIG. 3, a front flange portion 8c is provided at the front portion (joining surface with the second housing member) of the cylinder forming portion 8a of the first housing member 8, and a rear flange portion is provided at the rear portion. A portion 8d is provided.

  Further, on the inner surface of the shell forming portion 9 b of the second housing member 9, a first inner diameter portion 95 as a joint portion and a second inner diameter portion 96 on the rear end side from the first inner diameter portion 95 are provided. ing.

  Furthermore, on the inner surface of the shell forming portion 9b, an intermediate inner diameter portion is provided between the first inner diameter portion 95 and the second inner diameter portion 96, and each inner diameter portion is formed with a constant diameter. It is formed so that the diameter is enlarged toward the rear end.

  The front flange portion 8c is formed in a shape matching the inner peripheral shape of the second housing member 9, and is fitted inside the second housing member 9 so as to be close to the end surface of the front side block forming portion 9a. The rear flange portion 8d is also formed in a shape that matches the inner peripheral shape of the second housing member 9, and is formed on the inner side of the first inner diameter portion 95. Arranged inside.

  The first housing member 8 and the second housing member 9 are assembled by connecting the front flange portion 8c of the first housing member 8 to the first inner diameter portion 95 of the second housing member 9. This is performed by bringing the rear flange portion 8d into intimate contact with the second inner diameter portion 96 through a later-described protrusion T2 and press-fitting the protrusion T1 into the inner diameter portion 95. The press-fitting of the projection T2 into the inner diameter portion 96 is performed almost simultaneously.

  In the vane type compressor of the present invention, a plurality of projections T1 are integrally provided on the front flange portion 8c of the cylinder forming portion 8a, and a plurality of projections T2 are integrally provided on the rear flange portion 8d. . These projections T1 and T2 are provided, for example, at six locations on the flange portions 8c and 8d at equal intervals. Further, the circumferential positions of the flange portions 8c and 8d provided with the projections T1 and T2 are substantially equal (the same direction so that the projection T1 and the projection T2 are in phase with each other). Are arranged).

The protrusions T1 and T2 are preferably processed at the same time in order to increase the accuracy of the coaxiality.
Such a projection T1 is provided at a location near the insertion end of the first housing member 8, and the projection T2 is provided at a location near the radially outer portion of the bearing 13. In this example, the bearing 12 is provided. And the bearing 13 are provided on the outer peripheral portion of the flange portion. Further, the circumferential positions of the protrusions T1 and T2 are provided so as to avoid the position where the minute gap is formed in order to avoid the deformation of the minute gap.

  In the above configuration, rotational power from a power source (not shown) is transmitted to the drive shaft 3 via the pulley 20 and the electromagnetic clutch 21, and when the rotor 4 rotates, the working fluid flowing into the suction space 14 from the suction port 16 is transferred. The air is sucked into the compression space 18 through the suction port 30. Since the volume of the compression chamber 19 partitioned by the vanes 6 in the compression space 18 changes as the rotor 4 rotates, the working fluid confined between the vanes 6 is compressed and discharged from a discharge port (not shown). It discharges to the discharge space 24 via a valve (not shown). The working fluid protruding into the discharge space 24 moves in the circumferential direction along the outer peripheral surface of the cylinder forming portion 8a (along the inner peripheral surface of the shell forming portion 9b of the second housing member 9), and the flange portion 8d. The oil separator 25 is integrally formed with the rear side block forming portion 8b through the through-hole formed in the nozzle, and after oil separation, the oil is discharged from the discharge port 11 to the external circuit.

  As described above, the inner diameter portions 95 and 96 (joint portions) of the first housing member 8 and the second housing member 9 are provided in a plurality with a predetermined distance in the axial direction of the drive shaft 3. Even in a vane type compressor that forms a housing with two members, the housing member can be easily centered without tilting.

  For this reason, since the margin can be reduced with respect to the clearance of the sliding surface on the outer periphery of the rotor 4 and the front and rear end faces, the performance of the vane compressor 1 can be improved.

  Furthermore, since the inclination between the first housing member 8 and the second housing member 9 is eliminated, uneven wear and seizure can be prevented, and the reliability of the vane compressor can be improved. It becomes possible.

  Furthermore, since it is possible to perform centering by an inlay as in the present embodiment, a special centering process for improving the assembly accuracy is not required, and the manufacturing cost can be reduced.

  Further, in the above-described configuration, since the protrusion T1 is provided at a location near the insertion end of the first housing member 8, it is possible to prevent the first housing member 8 from being inclined during assembly. And since the protrusion T2 is provided in the location near the site | part of the radial direction outer side of the bearing 13, it becomes possible to receive the load concerning a bearing with the 2nd housing member 9 via the protrusion T2, and it is strong. A structure can be secured.

  Further, in the first embodiment, the first housing member 8 in which the cylinder forming portion 8a and the rear side block forming portion 8b are integrally formed, and the front side block forming portion 9a and the shell forming portion 9b are integrally formed. Although the example of the vane type compressor which comprises the housing 2 by fitting with the made 2nd housing member 9 was shown, the cylinder formation part 8a and the front side block formation part 9a are formed integrally. The housing 2 constituted by the housing member 8 and the second housing member 9 in which the rear side block forming portion 8b and the shell forming portion 9b are integrally formed may be applied to the vane compressor.

  Specifically, as shown in FIG. 6, the first housing member 8 is configured by integrally forming a front side block forming portion 9a and a cylinder forming portion 8a, and the second housing member. 9 is configured by integrally forming a rear side block forming portion 8b and a shell forming portion 9b. The second housing member 9 has a cylindrical portion 9m formed by the rear side block forming portion 8b and the shell forming portion 9b so as to close the rear side of the cylinder forming portion 8a. The housing 2 is configured by fitting one housing member 8 so that the front side of the cylinder forming portion 8a is closed.

In assembling the housing 2 formed as described above, the projections T1 and T2 formed on the flange portions 8c and 8d of the first housing portion are used as the inner diameter portion 95 of the second housing member 9 as in the first embodiment. , 96.
In addition, since the other structure is the same as that of the said Example, the same code | symbol is attached | subjected to the same location and description is abbreviate | omitted.

  Also in the vane type compressor 1 having such a configuration, the vane type compressor can be easily centered, and the same effects as the above configuration example can be achieved.

  The vane compressor described above is centered by providing two protrusions T1 and T2. However, the first housing member 8 and the second housing member 9 are joined with a small inclination. If only one of the protrusions T1 or T2 is provided, the centering can be easily performed.

DESCRIPTION OF SYMBOLS 1 Vane type compressor 2 Housing 3 Drive shaft 4 Rotor 6 Vane 8 1st housing member (rear side)
8a Cylinder forming portion 8b Rear side block forming portion 8c Flange portion 9 Second housing member (front side)
Reference Signs List 11 Discharge port 12, 13 Plain bearing 16 Suction port 17 Oil reservoir chamber 19 Compression chamber 25 Oil separator

Claims (8)

A first housing member integrally formed with a cylinder forming portion and a side block forming portion that closes one end side in the axial direction of the cylinder forming portion, and a shell forming portion that surrounds the outer peripheral surface of the first housing member And a second housing member integrally formed with a side block forming portion that closes the other end side in the axial direction of the cylinder forming portion, a housing is configured,
A drive shaft rotatably supported by the side block forming portion of the first housing member and the side block forming portion of the second housing member, and fixed to the drive shaft and rotatable in the cylinder forming portion And a vane that is slidably inserted into a plurality of vane grooves provided in the rotor,
The vane type compressor according to the first housing member, wherein a protrusion protruding in a radial direction of the rotor is provided in a circumferential direction at a joint portion with the second housing member. A plurality of joint portions between the first housing member and the second housing member are provided at predetermined intervals in the drive shaft direction,
The vane compressor according to claim 1, wherein a plurality of the protrusions are provided in the circumferential direction.   3. One of the joint portions between the first housing member and the second housing member is a portion close to a radially outer side of a bearing that supports the drive shaft. Vane type compressor.   The other one of the joint portions is disposed in the vicinity of a contact portion between the insertion end of the first housing member and the side block forming portion of the second housing member. 4. The vane type compressor according to any one of 3.   The protrusions formed on the first housing and disposed on the joint portion on the insertion end side and the protrusions disposed on the joint portion on the side block forming portion side assemble the first housing and the second housing. The vane type compressor according to any one of claims 1 to 4, wherein the press-fitting is performed almost simultaneously.   The plurality of joint portions with the first housing member formed on the second housing member are formed to have different diameters, and the insertion end of the first housing member and the side of the second housing member The vane type compressor according to any one of claims 1 to 5, wherein the vane type compressor is formed so as to sequentially increase in diameter from a joint portion provided in the vicinity of a joint surface with the block forming portion.   The vane compressor according to any one of claims 1 to 6, wherein the circumferential positions of the protrusions formed on the first housing member are substantially in phase at a plurality of joints.   The circumferential position of the protrusion formed on the first housing member is provided so as to avoid a position where the rotor and the cylinder forming portion form a minute gap. The vane type compressor in any one of thru | or 7.

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