JPS6149187A - Vane type rotary compressor - Google Patents

Abstract

PURPOSE:To aim at reducing variations in the torque of a vane type rotary compressor to prevent vibration and noise from being generated, by biasing the centers of large diameter sections of an elliptic cylinder and the positions of suction and discharge ports toward one small diameter section of the cylinder by a predetermined angle. CONSTITUTION:A vane type rotary compressor comprises elliptic cylinders having large diameter sections 22C, 22D whose centers M, N are biased toward one small diameter section 22B by a predetermined angle. Further, suction and discharge ports 30A, 30B, 31A, 31B are formed being also biased by a predetermined angle. Therefore, the suction and discharge timings of two pump chambers are shifted from each other so that it is possible to shift the phases of variations thereof and to lower the peak value of variations in torque. As a result, the generation of vibration and noise in the vane type rotary compressor may be reduced.

Description

Detailed Description of the Invention (Field of Industrial Application) The present invention relates to a vane-type rotary compressor used in a vehicle cooling system, etc. Regarding rotary compressors.

(Prior Art) As a conventional vane type rotary compressor, for example, those shown in FIGS. 4 and 5 are known. In these figures, reference numeral 1 indicates a compression mechanism section housed in a housing of a compressor, and this compression mechanism section 1 has a cam ring 2 and a rotor 3. The cam ring 2 is shown in Figures 4 and 5.
As shown in the figure, it consists of a cylindrical body with a substantially elliptical cross section, and its inner peripheral surface is composed of two small circular parts and a large circular part 2B. The openings at both ends of the cam ring 20 are sealed by a front plate 4 and a rear plate 5, and the rotor 3 is rotatably supported by these plates 4.5 through bearings 6A and 6B within the cam ring 2, particularly within the small circular portion 2A. ing.

As shown in FIG. 4, the rotor 3 has four slits 8 formed in its axial direction, and each slit 8 is arranged at equal intervals (90'') in the circumferential direction of the rotor 3. Furthermore, each slit 8 extends in a substantially radial direction (radial direction) in a cross section perpendicular to the axis. Vanes 9A to 9D, which are rectangular plate-shaped bodies, are slidably accommodated in these slits 8. When the rotor 3 rotates, the tips of these vanes 98 to 9D slide against the inner peripheral surface of the cam ring 2 due to centrifugal force and vane back pressure.The cam ring 2, the rotor 3, and both plates 4.5 pump chambers 10A and IOB are respectively defined, and each pump chamber 10A and 10B is defined by vanes 9A to 9D.
It expands and contracts and acts as a suction chamber or compression chamber.

Also, on the inner peripheral surface of the cam ring 2, approximately 180° in the circumferential direction is provided.
A pair of suction ports 11A, 11B and discharge ports 12A, 12B, which are separated and communicate with a refrigerant suction port (not shown) and a discharge port (not shown), are open, respectively, and the pump chamber is connected to the pump chamber from the suction ports IIA and IIB. The low-pressure refrigerant sucked into the pump chamber 10A and IOB is compressed by the rotation of the rotor 3 and becomes high-pressure, and is discharged into the discharge bow 1.
-12A and 12B are discharged from the discharge ports. In this case, as shown in FIG. 4, when one vane 9A and the opposite vane 9C are located close to the opening of each discharge port 12A, 12B, the remaining two vanes 9B, 9D are Each is located just before the completion of the journey. That is,
When the suction volume sucked into the pump chamber 10A and IOB by the vanes 9B and 9D reaches its maximum, the vanes 9A and 9D simultaneously
9C, the suction ports 11A and IIB are almost closed. Therefore, each pump chamber? The suction and compression strokes in the OA and IOB are performed at substantially the same timing, and the maximum suction amount (discharge amount) is ensured. Note that a back pressure passage 13 is defined at the bottom of the slit 8, and this back pressure passage 13 extends in the axial direction of the rotor 3 and provides lubrication through a communication groove 14 formed on the end surface of the rotor 3. Oil is supplied.

(Problems to be Solved by the Invention) However, in such a conventional vane type rotary compressor, the strokes in which the refrigerant is sucked and discharged by the vanes 9A to 9D in the two pump chambers 10A and IQB are the same. Because this was done at the correct timing, the following problems occurred. That is, in one pump chamber 10A, the volume is expanded or contracted by the vanes 9A to 9D, and a pressure change occurs due to the refrigerant. Torque fluctuation A occurs. This torque fluctuation A produces one peak every time the rotor 3 rotates 90 degrees, and the rotor 3 peaks once every 90 degrees.
Each rotation produces four peaks. To explain this in detail, as the vanes 9A to 9D proceed from the suction stroke to the compression stroke, the inside of one pump chamber 10A
The refrigerant is compressed by D and becomes high pressure, and due to this high pressure, the torque fluctuation acting on the rotor 3 gradually increases as shown by a in FIG.
The torque fluctuation A reaches its peak just before . When the vanes 9A to 9D pass through the discharge port 12B, as the compressed refrigerant is discharged from the discharge port 12B, the torque fluctuation A gradually decreases from the peak to zero, as already shown in the figure. In this way, four vanes 9A to 9
As D expands and contracts within one pump chamber 10A, four peaks occur for each revolution of the rotor 3. On the other hand, in the other pump chamber 10B, a torque fluctuation B as shown by the broken line B in the figure occurs in the rotor 3 at the same timing as in the one pump chamber 10A. As is clear from the figure, since these torque fluctuations A and B have substantially the same phase, they are combined to form a large torque fluctuation C. As a result, the overall torque fluctuation C acting on the rotor 3
is transmitted to the entire compressor through the rotating shaft of the rotor 3, resulting in an increase in vibration and noise of the compressor.

In order to solve these problems, a vane type rotary compressor as shown in FIG. 7, for example, has been proposed. In this device, slits 8 formed in the rotor 3 are arranged at unequal intervals with respect to the center of the shaft. Therefore, as shown in the figure, for example, the vane 9B and
- Although the vane 9C is more than 90゜ apart from each other, the vane 9
The separation angle between B and the vane 9A is 90° or less. For this reason, one pump chamber 10A and the other pump chamber 1
The timing of suction and compression in 0B is shifted, and as shown in FIG. 8, the rotor 3 in one pump chamber 10A
The phase of the torque fluctuation A' of the rotor 3 in the pump chamber 10B and the torque fluctuation B' of the rotor 3 in the other pump chamber 10B are shifted from each other (the peak is also shifted). As a result, these torque fluctuations A',
Since the overall torque fluctuation C' synthesized by B' is reduced by, for example, 20% compared to the conventional example, vibration and noise of the compressor are reduced.

However, in this example, although the torque fluctuation C' is reduced, the compression efficiency of the compressor is reduced, and as a result,
A new problem arises in that cooling performance deteriorates.

That is, one vane 9A is connected to one suction port 11.
When closing A, the vane 9 ahead of this vane 9A
Since B is still in the middle of the suction stroke, the refrigerant is not sucked in until the volume of one pump chamber 10A reaches its maximum, and the suction amount decreases and the discharge amount also decreases.

Also, when the vane 9C on the opposite side of one vane 9A closes the other suction port 11B, the vane 9D ahead of this vane 9C is in the middle of the compression stroke, so the vane 9D is sucked into the other pump chamber 10B. A part of the refrigerant ends up flowing back from the suction port 11B. In this way, the intake amount of refrigerant decreases, and the discharge amount also decreases accordingly, resulting in a decrease in compression efficiency and, as a result, deterioration in cooling performance.

Therefore, the present invention makes the centers of the pair of large circular parts of the cam ring tilt in a predetermined direction (towards one small circular part) by a predetermined angle in one or both of the centers, and each of the pair of suction ports and the pair of discharge boats By shifting only one or both of them by the same angle as the predetermined angle in the direction of inclination (towards one of the small circles), the phase of each torque fluctuation occurring in the two pump chambers is shifted, and the whole is synthesized. The aim is to reduce torque fluctuations in the air conditioner, thereby reducing vibration and noise of the compressor and machine without deteriorating cooling performance.

(Means to Solve the Problems) The present invention has been made to solve the above-mentioned problems. A cam ring is formed with a pair of suction ports and a pair of discharge ports that are opened on the inner circumferential surface of the cam ring with an interval of . a rotor that is rotatably housed in a cam ring, a vane that is retractably inserted into a slit extending radially in the rotor and whose tip slides into contact with the inner peripheral surface of the cam ring; a pump chamber having a variable volume and defined by the outer circumferential surface of the rotor and the inner circumferential surface of the cam ring;
In a vane-type rotary compressor, which is arranged at symmetrical positions separated by 0 degrees, and in which the center of a short axis that connects the centers of a pair of small circular parts coincides with the center of the rotor, the center of the short axis The center of one or both of the pair of large circular parts is inclined by a predetermined angle in the direction of one of the small circular parts from the long axis that is perpendicular to the long axis, and one or both of the pair of suction ports and discharge boats is shifted in the direction of one of the small circular portions by the same angle as the predetermined angle.

(Function) In the present invention having such a configuration, the timing of suction and discharge of refrigerant in the two pump chambers is shifted, so that each torque fluctuation of the rotor occurring in each pump chamber has a phase difference. It shifts. Therefore, the total torque fluctuation, which is a combination of the two torque fluctuations, is reduced, and the vibration and noise of the compressor are reduced. Further, the refrigerant is sucked into each pump chamber so that the volume of each pump chamber is maximized, and a discharge amount corresponding to the suction is ensured, so that compression efficiency does not decrease.

(Example) Embodiments of the present invention will be described below with reference to the drawings.

1 to 3 are diagrams showing one embodiment of the present invention. First, to explain the configuration, in Figures 1 and 2, 2
Reference numeral 1 indicates a compression mechanism section housed in the housing of the compressor, and this compression mechanism section 21 includes a cam ring 22 and a rotor 23.
It has

As shown in FIGS. 1 and 2, the cam ring 22 is made of a cylindrical body with a non-perfect circular cross section, and openings at both ends thereof are sealed by a pair of front plate 24 and rear plate 25. The rotation axis 23A of the rotor 23 is connected to both plates 24.
The bearing 26A is loosely fitted into the bearing holes 24A and 25A of 25.
, 26B to both plates 24, 25. Therefore, the rotor 23 is rotatably housed within the cam ring 22. As shown in FIG. 1, the rotor 23 has four slits 27 formed in its axial direction.
Further, the slits 27 are arranged at equal intervals (90°) in the circumferential direction of the rotor U, and each slit 27 extends substantially in the radial direction (radial direction) in the cross section in the direction perpendicular to the axis. Rectangular plate-shaped vanes 28A to 28D are slidably inserted into these slits 27 with a predetermined clearance. A back pressure passage 29 is defined by each vane 28A to 28D on the base end (radial inner end) side of the vanes 28A to 28D (at the bottom of the slit 27), and the back pressure passage 29 is lubricated via a communication groove 33. Oil is introduced. Therefore, the vanes 28A to 28
D protrudes radially outward from the slit 27 due to the pressure of the lubricating oil in the back pressure passage 29 (vane back pressure) and the centrifugal force when the rotor 23 rotates, and each tip comes into sliding contact with the inner peripheral surface of the cam ring 22. Become. The inner peripheral surface of this cam ring 22 has a pair of small circular parts 22A, 22B, and these small circular parts 22A,
A pair of large circular parts 22C122D are continuous to 22B, and a pair of small circular parts 22A and 22B are arranged at symmetrical positions separated from each other by 180 degrees.

Here, X in FIG. 1 represents the minor axis that passes through the central axis Z of the rotor 23 and connects the centers of the pair of small circular parts 22A and 22B.
Y indicates a major axis that is perpendicular to this minor axis X and the central axis Z of the rotor 23, respectively. Note 4. The center of the minor axis X coincides with the central axis Z of the rotor 23. The center M of the one large circular portion 22C is inclined clockwise from the major axis Y by a predetermined angle α, for example, 15°, and the center N of the other large circular portion 22D is inclined with respect to the major axis Y. It is inclined counterclockwise by the same angle as the predetermined angle α.

Therefore, the inner circumferential surface of the cam ring 22 has a substantially heart shape that is symmetrical about the minor axis X. Further, in the cam ring 22, one suction port 1-3OA and one discharge port 31B are formed to be shifted clockwise by the same angle as the predetermined angle α, and the other suction port 30B and the other discharge port 31A and are formed counterclockwise by the same angle. Therefore, one suction port 30A and the other suction boat 3
0B is approximately 165 degrees apart clockwise, and similarly, one discharge port 1-31A and the other discharge port 31B
They are also separated by approximately 165°. In FIG. 1, 32A and 32B are pump chambers defined by a pair of large circular parts 22C122D and the outer peripheral surface of the rotor 23, and these pump chambers 32
The volumes of vanes A and 32B are made variable by the vanes 28A to 28D. That is, each suction boat 30A, 30
The low-temperature, low-pressure refrigerant sucked into each pump chamber 32A, 32B from B is transferred to each pump chamber 32A by the rotation of the rotor 23.
,.

It is compressed in 32B and becomes high temperature and high pressure, and each discharge boat 3
It is discharged into the housing from 1A and 31B.

In this case, when one vane 28C is located approximately at the opening of one discharge port 31B in the figure, the vane 28A on the opposite side is closer to the rotor 28 than the other discharge port 31A.
is located at the front in the direction of rotation.

Further, when the other vane 28B is in the middle of the suction stroke,
The vane 28D on the opposite side is in the middle of the compression stroke. Therefore, the timing of sucking and compressing the refrigerant by each of the vanes 28A to 28D in both pump chambers 32A and 32B is not simultaneous, but is staggered.

Next, the effect will be explained.

The centers M and N of the pair of large circular parts 22C122D are the diameter axis Y
Short form from! I! thX direction (one small circular part 22B direction)
a pair of suction boats 30A,
30B and the discharge ports 31A, 31B are shifted in the inclination direction by the same angle as the predetermined angle α, each vane 28A
- Each pump chamber 32A whose volume is expanded or contracted by 28D
, 32B, the refrigerant is supplied to each suction port 1-30 A, 3
After being sucked in from 0B and compressed, each discharge boat 31A,
The timing of each discharge from 31B becomes different. Therefore, the torque fluctuation of the rotor 23 occurring in one pump chamber 32A (indicated by a solid line in FIG. 3)
changes to form four peaks for each rotation of the rotor 23, and the torque fluctuation of the rotor 23 (indicated by the broken line E in the figure) generated in the other pump chamber 32B is With each rotation, the phase changes to form four peaks that are shifted from each other. Therefore, these l-ru fluctuations, E, correspond to the angle α, and are abbreviated as ]5
° Their phases are shifted, and the overall torque fluctuation F, which is synthesized by these two torque fluctuations J and E, is approximately 40% compared to the first conventional example and approximately 40% compared to the second conventional example. Even if it is reduced by about 20%. As a result, the torque fluctuation F transmitted from the rotor 23 to the entire compressor via its rotating shaft 23A is reduced, so there is no increase in vibration or noise. Also,
Each pump chamber 32A by two vanes 2BB and 28D,
When the volume of 32B is maximum, the two rear vanes 2
Since each suction boat 30A, 30B is substantially closed by 8A, 28C, the amount of refrigerant sucked does not decrease.

Therefore, the discharge amount corresponding to the intake amount can be ensured, and compression efficiency does not deteriorate. As a result, cooling performance does not deteriorate. In this way, in this embodiment, it is possible to reduce the vibration and noise of the pressure plate while maintaining cooling performance.

In this embodiment, a case has been described in which the centers M and N of the pair of large circular portions 22C122D of the cam ring 22 are inclined in predetermined directions, but the present invention is not limited to this. Either one of the centers M and N of the portions 22G and 22D may be inclined in a predetermined direction. Further, the inclination angle α is not limited to 15°, and a predetermined angle can be selected within a range that does not cause the possibility that the pump chambers 32A and 32B will communicate with each other.

(Effects) As explained above, according to the present invention, the timing of suction and discharge in the two pump chambers can be shifted, and the phase of each torque fluctuation of the rotor occurring in each pump chamber can be shifted. Overall torque fluctuation can be reduced. As a result, vibration and noise of the compressor can be reduced without deteriorating cooling performance.

[Brief explanation of drawings]

1 to 3 are diagrams showing one embodiment of a vane type rotary compressor according to the present invention, and FIG. 1 is a front sectional view thereof, and FIG.
The figure is a concave side view of the rotor, Figure 3 is a graph showing the relationship between the rotation angle of the rotor and torque, and Figures 4 and 5 are the conventional...
Figure 4 is a front cross-sectional view, and Figure 5 is a side cross-sectional view. FIG. 6 is a graph 1 showing the relationship between rotor rotation angle and torque in this conventional example. FIG. 7 is a sectional view of the working surface of another conventional vane regular rotary compressor, and FIG. 8 is a graph showing the relationship between the rotation angle of the rotor and the torque in the conventional example of FIG. 22...-111 cam ring, 22 A, , 22 B ------1 small circular part, 22
C, 22D----One large circular part, 23...-Rotor, 24-...-Front plate, 25---Rear plate, 27--Slit, 28A-28D ----- Vane, 30A, 30
B ---- One suction board 1-131 A, 31 B-
------Discharge port, 32A, 32B ------
- Pump chamber, X.-- Minor axis, Y-- 111 major axis, α-- Predetermined angle, M, N...-- Each center of each large circle.

Claims (1)

[Claims] A pair of suction ports and a pair of discharge ports, each of which has an inner circumferential surface consisting of a pair of small circular portions and a pair of large circular portions, each opening at a predetermined distance from the inner circumferential surface. A cam ring is formed, a rotor whose rotating shaft is rotatably supported within the cam ring and whose rotating shaft is supported by a front plate and a rear plate that seal openings at both ends of the cam ring, and a rotor that extends in a radial direction from the rotor. A vane that is inserted into the slit so as to be freely protrusive and retractable and whose tip slides into contact with the inner circumferential surface of the cam ring, and a pump chamber whose volume is made variable by the vane and defined by the outer circumferential surface of the rotor and the inner circumferential surface of the cam ring. , the pair of small circular parts are arranged at symmetrical positions separated by 180 degrees from each other, and the center of the minor axis connecting the centers of the pair of small circular parts coincides with the center of the rotor. In the vane type rotary compressor, the center of one or both of the pair of large circular portions is inclined by a predetermined angle in the direction of one of the small circular portions from the major axis perpendicular to the center of the minor axis; A vane type rotary compressor, characterized in that one or both of a pair of suction ports and discharge ports are shifted in the direction of the one small circular portion by the same angle as the predetermined angle.