JP2720067B2 - Compressor - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a vane type compressor for compressing a refrigerant or the like.

2. Description of the Related Art As shown in, for example, Japanese Utility Model Laid-Open Publication No. 61-92778, a vane type compressor has a front and rear side blocks arranged on both sides of a cylinder block having a guide surface of a desired shape. , And a rotor having a number of vanes is housed in the compressor body.

A drive shaft is inserted into the center of the rotor, and the drive shaft is supported by the front and rear side blocks via bearings. An appropriate clearance is provided between the rotor and both side blocks so that the rotation is performed smoothly.

On the front side of the drive shaft, an electromagnetic clutch is attached to transmit torque to the drive shaft. When the electromagnetic clutch is turned on, the clutch plate is attracted to the rotor and the drive force is transmitted, and the vane, rotor, cylinder, and The volume of the compression chamber constituted by the side blocks repeatedly increases and decreases, and the compressed refrigerant is discharged from the discharge port by opening the reed valve.

(Problems to be Solved by the Invention) In the vane-type compressor as described above, the driving noise generated by the rotation of the rotor, especially in the case of the five-vane type, has a torque fluctuation of 10 times per time. The load fluctuates five times, and harmonic vibrations based on these frequencies are generated in the rotor to induce resonance of other components, thereby generating harsh sounds.

This is because the rotor has an appropriate clearance between the front side block and the rear side block in order to smoothly rotate. It becomes noise.

Therefore, an object of the present invention is to reduce the noise by controlling the vibration of the rotor caused by the torque fluctuation and the load fluctuation due to the compression work.

(Means for Solving the Problems) Means for solving the problems of the present invention include:
A compressor body is formed by a cylinder and both side blocks arranged on both sides of the cylinder, a rotor is housed in the compressor body, and a compression chamber is formed by vanes provided in a radial direction of the rotor. In a vane-type compressor in which the volume of a compression chamber is changed by rotation of a rotor so that compressed fluid pushes out each discharge valve from a plurality of discharge ports formed in an axial direction and flows out, the plurality of discharge valves Is gradually increased from one side block side to the other side block side of one of the suction ports.

(Operation) Therefore, the opening degree of the discharge valve provided at each discharge port is
Steps are performed so that the opening degree of the discharge valve located on one side block side of one of the suction ports is the smallest, and the opening degree of the discharge valve located on the other side block side is the largest. Since the pressure in the compression chamber is distributed so that the other side block side is gradually increased, and the rotor is constantly restricted from being pressed to one side block, the axial vibration of the rotor is suppressed. Reduce noise.

(Embodiment) An embodiment of the present invention will be described below in detail with reference to the accompanying drawings.

3 to 5, the compressor body 1 is configured by fixing front and rear side blocks 3a and 3b to both sides of a cylinder 2 having a guide surface of a desired shape. Inside the compressor main body 1, a columnar rotor 5 which is firmly connected to the drive shaft 4 is disposed at the center, and two places on the outer peripheral surface of the rotor 5 have an appropriate clearance with the guide surface of the cylinder. Are located. A drive shaft 4 on which the rotor 5 is fixed.
Are rotatably supported by being inserted into drive shaft holes 7a, 7b formed in the front and rear side blocks 3a, 3b via bearings 8a, 8b. One of the drive shafts 4 is connected to an electromagnetic clutch 21 described below that communicates with the rotation source, and the other is in a drive shaft hole 7b formed in the rear side block 3b, and the hole 7b blocks communication with the high-pressure chamber 19. Cover 10 is fixed to the rear side block 3b.

The electromagnetic clutch 21 includes a rotor 23 having a V-shaped groove 22, an electromagnet 24 for magnetizing the rotor 23, and a clutch plate 25 opposed to the rotor 23 and coupled to the tip of the drive shaft 4.
A rotor having a V-shaped groove 22 by energizing the electromagnet 24
23 is magnetized to couple the clutch plate 25 and the power is applied to the drive shaft 4
Has the effect of communicating to

A vane 13 is slidably fitted in a plurality of vane grooves 12 formed in the rotor 5 in a substantially radial direction.
Is pushed in the distal direction by the back pressure or centrifugal force due to rotation, and rotates along the inner surface of the cylinder 2. Each time each vane 13 passes through suction ports 11a and 11b (described later) formed in the front side block 3a, the refrigerant is sucked and the next vane
13 and between the compression chamber 14 formed. The compression chambers 14 formed by the adjacent vanes 13 and the cylinders 2 and the front and rear side blocks 3a and 3b change in volume from a minimum to a maximum in a suction process and from a maximum to a minimum in a discharge process, and are formed in a line in the axial direction. Are discharged from the plurality of discharge ports 15a to 15d.

In the discharge ports 15a to 15d, reed valves 16a to 1 as discharge valves are provided.
6d is pushed open to discharge the pressurized refrigerant, and this operation is repeated to perform the compression operation. The refrigerant discharged from the reed valves 16a to 16d is guided to the high-pressure chamber 19 formed by the shell 26 via the discharge tube 18 for guiding, and flows out from the discharge port 20.

Four reed valves 16a to 16d are provided corresponding to the plurality of discharge ports 15a to 15d, and valve stoppers 17a to 17b are disposed behind the reed valves 16a to 16d, and a predetermined opening ( (Lift amount) is restricted.

In this case, as shown in FIG.
~17d it is adapted to position from a state where the reed valve 16a~16d is in the closed position of the discharge port with a predetermined distance _{L 1, L 2, L 3} , L 4. As shown in FIG. ₂ , each of the openings L ₁ , L ₂ , L ₃ , and L ₄ is set in a stepwise manner so that the cylinder internal pressure has a substantially proportional relationship in which the rear side increases. , opening L ₁ is about 0.16 mm, L ₂ is about 0.7 mm, L ₃ is about 1.0 mm, L ₄ is set to about 1.5 mm.

By setting such an opening degree stepwise, the discharge hole 15
The discharge amount of the compressed refrigerant differs from a to 15d, and the compression chamber 14
In this case, the pressure on the front side with a smaller outflow is higher than that on the rear side. Since high-pressure refrigerant enters the clearance 31a between the rotor 5 and the front side block 3a and presses the rotor 5 in the direction of the rear side block 3b, the axial vibration of the rotor 5 is restricted, and the vibration noise of the compressor is reduced. Can be achieved.

In addition, since the suction port is formed in the front side block, the opening amount on the rear side is large. Conversely, when the suction port is formed in the rear side block, the configuration is reversed.

Further, even when the number of suction ports is five or three, the opening amount is regulated as described above, and the above-described operation and effect can be obtained.

(Effects of the Invention) According to the present invention, the opening degree of the discharge valves arranged from the front side block side to the rear side block side is gradually increased at a large number of discharge ports. One of the side blocks gradually increases in size, and the rotor is constantly restricted from being pressed by the other side block. Therefore, the axial vibration of the rotor can be suppressed and noise can be reduced.

Further, with the above configuration, the pressure on the high-pressure chamber side of the discharge valve chamber can be reduced, so that the discharge resistance can be reduced. Accordingly, the amount of heat generated during compression is reduced, so that the amount of overcompression can be reduced, and the rise in the temperature of the discharged refrigerant can be suppressed.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of a discharge port according to an embodiment of the present invention, FIG. 2 is a graph showing a relationship between a cylinder width dimension and a cylinder internal pressure, and FIG. Figure,
FIG. 4 is a longitudinal sectional view of the compressor, and FIG. 5 is a sectional view taken along line AA of FIG. 1 Compressor body, 5 Rotor, 11a, 11b Suction port, 13 Vane, 14 Compression chamber, 15a to 15d Discharge port, 16a, 16b, 16c, 16d Reed valve (Discharge valve), 17a, 17
b, 17c, 17d ...... valve _{stopper, L 1, L 2, L} 3, L 4 ...... opening degree of each lead valve (lift).

Claims (1)

(57) [Claims] A compressor body is formed by a cylinder and both side blocks arranged on both sides of the cylinder, a rotor is housed in the compressor body, and a compression chamber is formed by vanes provided in a radial direction of the rotor. Is formed, the volume of the compression chamber changes due to the rotation of the rotor, a vane type compressor in which the compressed fluid pushes out each discharge valve and flows out from a number of discharge ports formed in the axial direction. The compressor according to claim 1, wherein the opening amounts of the plurality of discharge valves are increased stepwise from one side block side to the other side block side of one of the suction ports.