JP2621673B2 - Vane compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vane compressor,
More specifically, the present invention relates to an improvement of a vane compressor which prevents interference between a cylinder and a rotor.

[0002]

2. Description of the Related Art A vane compressor is widely used, for example, as a refrigerant compressor for air conditioning. FIGS. 3 and 4 show a fixed displacement vane compressor in particular. As shown in the figure, a cylinder 3 is housed and fixed in a pair of front and rear housings 1 and 2 which are joined, and both ends of the cylinder 3 are closed and sealed by side plates 4 and 5 to form a substantially elliptical column inside. Are formed. A cylindrical rotor 6 is accommodated in the cylinder chamber so as to be rotatable in the direction of arrow P in FIG. 4, and the rotor 6 has a small set gap on the minor axis side of the inner peripheral surface of the substantially elliptical cylinder. And is fitted to the concentric circularly sealed region S opposing locally.

[0003] Support shafts 6a and 6b are integrally formed before and after the rotor 6, and a suction area is provided in the housing 1.2.
The side plate 4 and the rear side plate 5 before defining the frequency and the discharge region, the support shaft 6a, 6b are rotatably supported through bearings 13a, 13b. On the peripheral surface of the rotor 6, a plurality of grooves 7 (four in this example) are substantially concavely formed in the radial direction.
A vane 8 is fitted on the front and rear side plates 4 and 5 so as to be able to protrude and retract. The bottom of the groove 7 communicates with the oil separation chamber 2a at the rear of the rear housing 2, and the lubricating oil stored in the oil separation chamber 2a is formed with annular grooves 4a, 5a formed on the inner side surfaces of the side plates 4, 5. And a passage 5b to the sliding surface relative to the rotor 6 and the bottom of each groove 7. Each vane 8 can be brought into contact with the inner peripheral surface of the cylinder by centrifugal force caused by rotation of the rotor 6 and oil pressure supplied from the oil separation chamber 2a to the bottom of the groove 7. A plurality of hermetically sealed spaces R are defined by the vanes 8 and the sealing regions S facing each other. The angle range of the sealed region S is set to about 10 to 15 ° from the viewpoint of both securing the volume of the sealed air space R and preventing the fluid from leaking from the high pressure region to the low pressure region.

The cylinder 3 has a pair of suction passages 9 extending in the axial direction in alignment with the suction passages 4b formed through the front side plate 4.
The suction chamber 1a is communicated with a sealed air space R of a low-pressure atmosphere (the front side of the sealed area S in the rotation direction of the rotor 6) through both suction passages 4b and 9 and a suction port 10. I have. A pair of discharge chambers 3a are recessed in the outer peripheral portion of the cylinder 3, and a discharge hole 11 that opens in a sealed space R in a high-pressure atmosphere (the rear side of the sealed region S in the rotation direction of the rotor 6) is formed. It is penetrated. Each discharge hole 11 opening to the discharge chamber 3a side is closed by a discharge valve 12 so as to be openable. The discharge chamber 3a is connected to the oil separation chamber 2a through a through hole 5c formed through the rear plate 5. Have been.

[0005]

As described above, the cylinder 3 is sandwiched between the both side plates 4 and 5, and the rotor 6 has the front and rear support shafts 6a and 6a which are supported on both sides via bearings 13a and 13b, respectively. Mounted on plates 4,5. Therefore, if the alignment of the shaft support holes formed in the side plates 4 and 5 is impaired due to a machining error or the like, the shaft of the rotor 6 necessarily becomes stiff (FIG. 5). At this time, in the sealing area S of the cylinder 3 closest to the outer peripheral surface of the rotor 6, the allowable gap C is usually set to a small value of 10 to 15 μm in order to prevent fluid leakage. The squeeze fills the gap C at one of the side ends, causing a serious accident such as contact, interference, and eventually seizure.

Further, depending on the material of the cylinder 3,
Due to the tightening torque of the two side plates 4 and 5 for sandwiching the same, compressive deformation occurs near the side end of the thin sealing region S, which also reduces the gap C at one or both side ends. Then, depending on the case, there is a possibility that the same problem as described above may occur. An object of the present invention is to prevent interference between a cylinder and a rotor in advance.

[0007]

In order to solve the above-mentioned problems, the present invention provides a novel construction in which the gap between the cylinder and the rotor at both ends of the sealing area S is slightly larger than the set gap. Has adopted. As a preferred embodiment of the present invention, the gap at both end portions of the sealing region S is enlarged by cutting the specified inner circumferential portion of the cylinder or the outer circumference of the rotor into an inclined or stepped shape. Achieved. The present invention is applicable to all types of vane compressors regardless of the number of discharges per rotation of the rotor.

[0008]

The alignment of the support shaft (drive shaft) on which the rotor is to be supported is impaired due to machining errors, resulting in a stiffening of the rotor shaft, or the sealing of the cylinder by the clamping force of both side plates. Even if compressive deformation occurs near the end on the side of the region, and even if a phenomenon of narrowing the gap between the cylinder and the rotor occurs at both ends of the sealing region, this was previously formed on the cylinder or the rotor. Since it is absorbed by the local expansion gap, contact and interference between the cylinder and the rotor are reliably prevented.

[0009]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. Since the basic configuration of the vane compressor is not particularly different from the conventional one, the same components are denoted by the same reference numerals and detailed description thereof will be omitted. FIG.
FIG. 5 is a local sectional view of the sealing region S of the cylinder 3 in a longitudinal section. In this embodiment, the center of the outer periphery of the rotor 61 is opposed to the sealing region S of the cylinder 3 with a set gap C therebetween. A required portion at both ends of the outer periphery is cut into the inclined surface P, and a gap with the sealing region S is formed slightly larger than the set gap C.

On the other hand, in another embodiment shown in the cross-sectional view of FIG. 2, required portions at both end portions of the outer peripheral surface of the rotor 62 are cut into step surfaces Q, and the sealing region S is similarly formed. Is set larger than the set gap C in advance. The width of the inclined surface P or the stepped surface Q and the dimensions of the inclined angle or the step shown in both embodiments avoid local interference between the rotors 61 and 62 and the deformation of the cylinder 3 and the like. The selection is made within a range that does not impair the sealability of the part as much as possible.

In each of these embodiments, the above-described gap enlarging operation is performed on the rotors 61 and 62. Similarly, the gap enlarging operation having an inclined shape or a stepped shape is performed by the cylinder 3. May be applied to the sealing region S side, or the step surface Q may be formed in a further subdivided multi-step surface. Therefore, the alignment of the shaft support holes formed in the side plates 4 and 5 is impaired due to a machining error, so that the shafts of the rotors 61 and 62 are locked, or
Due to the tightening force of 5, compression deformation occurs near the end of the cylinder 3 on the sealing area S side, and accordingly, the gap between the cylinder 3 and the rotors 61 and 62 is reduced at one or both ends of the sealing area S. Even if the gasification phenomenon occurs, it is absorbed by the inclined surface P or the stepped surface Q formed in the cylinder 3 or the rotors 61 and 62 in advance, so that the cylinder 3 and the rotors 61 and 6 are absorbed.
Contact and interference of the two can be reliably prevented.

[0012]

As described above in detail, according to the present invention, the gap between the cylinder and the rotor at both end portions of the sealing region S is formed slightly larger than the set gap. The gap narrowing phenomenon that occurs at the side end of the sealing region due to the shape of the rotor and the deformation of the cylinder is skillfully absorbed by the enlarged gap formed in advance, so that the wear due to the interference between the cylinder and the rotor is reduced. Seizure is completely prevented, which has the effect of significantly contributing to extending the life of the compressor and improving its reliability.

[Brief description of the drawings]

FIG. 1 is a sectional view of a main part showing an embodiment of the present invention.

FIG. 2 is a sectional view of a main part showing another embodiment of the present invention.

FIG. 3 is a sectional front view showing a conventional vane compressor.

FIG. 4 is a cross-sectional side view showing a conventional vane compressor.

FIG. 5 is a sectional view of a main part of a conventional vane compressor.

[Explanation of symbols]

3 is a cylinder, 4 is a front plate, 5 is a rear plate, 6a and 6b are support shafts (drive shafts), 61 and 62 are rotors, S is a sealing area,
C is the setting gap

Claims (1)

(57) [Claims] 1. A rotor mounted on a drive shaft, a plurality of vanes fitted on the rotor and capable of protruding and retracting in a substantially radial direction, and accommodating the rotor and the vanes. And a cylinder provided with a locally opposed sealing region with a small set gap between the rotor outer peripheral surface and a sealed air space partitioned inside the cylinder by sandwiching the cylinder. Side plate, and the syringe
And a housing that houses the front and rear side plates.
・ The rear plate defines the suction and discharge areas in the housing.
A vane compressor configured to compress the working fluid by changing the volume of the sealed air space based on the rotation of the rotor, wherein a gap between the cylinder and the rotor at both end portions of the sealed region is provided. Is slightly larger than the set gap.