JP2993299B2 - Rotary 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 rotary compressor used for an air conditioner for cooling and heating, a refrigerator, and the like.

[0002]

2. Description of the Related Art Conventionally, as a rotary compressor, as shown in FIG. 3, a housing 1 having a cylindrical cylinder chamber 1a and a hole 12 opened in the cylinder chamber 1a is arranged in the cylinder chamber 1a. And a cylindrical rotor 2 having a plate-like blade 2a extending in the radial direction, and an eccentric disk 4 fixed eccentrically to the rotating shaft 3 and rotatably fitted to the inner periphery of the rotor 2. There are things. The hole 12 is formed on the circumference of the cylinder chamber 1a and comprises a cylindrical hole 12b extending in the axial direction and a rectangular hole 12a provided at an upper portion of the hole 12b. Oscillating bushes 5 and 6 having a semicircular cross section are arranged in the cylindrical holes 12 b, and the planes of the oscillating bushes 5 and 6 are in sliding contact with both side surfaces of the blade 2 a of the rotor 2. I have to. Blade 2a and rotor 2
Thereby, the cylinder chamber 1a is divided into a suction chamber 10 on the low pressure side and a compression chamber 11 on the high pressure side. The housing 1 has a suction port 1b opening to the suction chamber 10 on the right side of the hole 12 and a discharge port 1c opening to the compression chamber 11 on the left side of the hole 12. The compressed gas refrigerant is discharged from the discharge port 1c via the valve 9. A space 1 partitioned by the oscillating bushes 5 and 6 and the blade 2a.
Numeral 3 communicates with the suction port 1b through the passage 40 to reduce pumping loss.

[0003]

In the conventional rotary compressor, the compressed high-pressure gas refrigerant flows from the compression chamber 11 through the gap between the side surface of the blade 2a and the plane of the oscillating bush 5. Then, the gas refrigerant leaks into the low-pressure side space 13 partitioned by the swing bushes 5 and 6. And
The suction port 1b passes from the space 13 through the passage 40.
Gas refrigerant leaks into

As described above, the conventional rotary compressor has a disadvantage that the gas refrigerant leaks from the high pressure side to the low pressure side, resulting in a large power loss.

An object of the present invention is to provide a rotary compressor which can prevent a gas refrigerant from leaking from a compression chamber to a suction chamber.

[0006]

According to a first aspect of the present invention, there is provided a rotary compressor, comprising: a housing having a cylinder chamber and a hole opened to the cylinder chamber; A rotor having an extending blade, an eccentric disk fixed eccentrically to a rotating shaft, rotatably fitted to the inner periphery of the rotor, and provided swingably in the hole, allowing the blade to swing and A rotary compressor having an oscillating bush that is supported to move forward and backward, wherein the blade and the oscillating bush are configured to be in sliding contact with each other on flat surfaces, A closed space is formed in the housing outside the bush, and the tip of the blade is opened in the closed space.

A rotary compressor according to a second aspect of the present invention is provided with a cylinder chamber arranged at intervals in the axial direction, a housing having holes respectively opened in the cylinder chambers, and arranged in the cylinder chambers, respectively. A rotor having blades extending in the radial direction, and an eccentric disk fixed eccentrically to the rotation shaft, rotatably fitted to the inner periphery of each of the rotors, and fixed to the rotation shaft with a fixed phase different from each other. When,
A rotary bush that is provided in each of the holes so as to be swingable and supports each of the blades so as to be able to swing and move forward and backward. Each of the blades is configured to be in sliding contact with each other, and on the side facing the tip of each of the blades, and on the housing that is outside of each of the oscillating bushes, sealed spaces that communicate with each other are formed. It is characterized in that the tip of each blade is opened individually.

[0008]

According to the structure of the first aspect, the blade and the oscillating bush are brought into sliding contact with each other on a flat surface, and are on the side facing the tip of the blade and outside the oscillating bush. Since the closed space in which the tip of the blade is opened is formed in the housing, the path through which the gas refrigerant leaks is from the high pressure side of the cylinder chamber → the closed space at the tip of the blade → the low pressure side of the cylinder chamber. That is, the gas refrigerant passes through the gap between the side surface of the blade and the plane of the oscillating bush from the cylinder chamber on the high pressure side, enters the closed space on the blade tip side, and further oscillates from the closed space with the side surface of the blade. It leaks to the low pressure side of the cylinder chamber through the gap between the moving bush and the plane. For this reason, the gas refrigerant is sealed by a reciprocating path between the planes on both sides of the swing bush and both sides of the blade. Therefore, the length of the seal for sealing the gas refrigerant can be substantially doubled as compared with the conventional rotary compressor, and the leakage of the gas refrigerant can be reduced. If the volume of the closed space is increased, the pumping loss due to the reciprocating motion of the blade can be reduced.

According to the second aspect of the present invention, each of the blades and each of the swinging bushes are brought into sliding contact with each other on a flat surface.
In addition, in the housing outside each swinging bush, closed spaces that communicate with each other are formed, and the tips of the blades are respectively opened in each closed space. Side → closed space at blade tip → low pressure side of cylinder chamber. For this reason, the gas refrigerant is sealed by a reciprocating path between the planes on both sides of the swing bush and both sides of the blade. Therefore, the length of the seal for sealing the gas refrigerant can be substantially doubled as compared with the conventional rotary compressor, and the leakage of the gas refrigerant can be reduced. Further, the respective eccentric disks in the rotor are fixed to the rotating shaft so that their phases are different from each other. For this reason, the entire closed space on the tip side of each of the blades has a substantially constant volume or a small change in volume. Therefore, even if each of the blades reciprocates, the gas refrigerant hardly compresses in the closed space even when the blades reciprocate, so that pumping loss can be eliminated. Damage can be prevented.

[0010]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a rotary compressor according to the present invention.

FIG. 1 is a sectional view of a rotary compressor according to an embodiment of the present invention, wherein 1 is a cylindrical cylinder chamber 1a.
A suction port 1b opening into the cylinder chamber 1a,
A housing 2 having a discharge port 1c and a hole 12 is disposed in the cylinder chamber 1a, a cylindrical rotor having a blade 2a extending in a radial direction, and 3 is an eccentric which is rotatably fitted to the inner periphery of the rotor 2. The rotating shafts 5 and 6 to which the disk 4 is fixed are swingably provided in the hole 12 and are semicircular swinging bushes that support the blade 2a swingably and reciprocally. The hole 12 is open on the circumference of the cylinder chamber 1a and has a cylindrical hole 12b extending in the axial direction and a hole 12a having a rectangular cross section provided above the hole 12b. In the cylindrical hole 12b, swing bushes 5 and 6 having a semicircular cross section are arranged.
Slidably contact both side surfaces of the blade 2a.

FIG. 2 is a sectional view taken along the line AA of FIG. 1, in which rotors 102 having the same structure as the rotor 2 are arranged at intervals in the axial direction. That is, the rotor 102 is arranged in a cylinder chamber 101a having the same shape as the cylinder chamber 1a, and both side surfaces of a plate-like blade 102a of the rotor 102 are arranged in a hole 112 in a semicircular swing bush (not shown). ) Is swingably supported by the flat part. An eccentric disk 104 fixed to the rotating shaft 3 is rotatably fitted on the inner periphery of the rotor 102. The eccentric disk 104
Is fixed to the rotating shaft 3 with a phase difference of 180 degrees from the eccentric disk 4 described above. Both side surfaces of the rotor 2, 102 and the eccentric disks 4, 104 are slidably in contact with the housings 1, 7, 8. Each of the spaces 13 and 113 on the tip side of the blades 2a and 102a is a closed space that communicates only with each other.

One end of the rotary shaft 3 of the rotary compressor is connected to a motor (not shown), and an arrow R in FIG.
, The eccentric disk 4 fixed to the rotating shaft 3 is eccentrically rotated inside the rotor 2. According to the eccentric disk 4, the rotor 2
It moves in the radial direction while sliding inside the cylinder chamber 1a, and swings about the blade 2a. At this time,
The tip surface of the blade 2a is moved to the hole 12a by the swinging motion.
Reciprocating up and down while slightly swaying left and right inside. When the eccentric disk 4 rotates about the rotation shaft 3, the cylinder chamber 1 a is divided into a suction chamber 10 and a compression chamber 11 by the blade 2 a and the rotor 2. The suction chamber 10 sucks the gas refrigerant from the suction port 1b, and
Compresses the gas refrigerant, and discharges the gas refrigerant from the discharge port 1c via the valve 9 when the pressure of the gas refrigerant reaches a predetermined pressure or more in the compression step. In this way, by repeating the above rotation operation, the rotary compressor continuously performs suction, compression, and discharge. In addition, the suction, compression and discharge operations of the other rotor 102 are performed in the manner shown in FIG.
4 is the same except that the phase with the phase No. 4 is different by 180 degrees.
Therefore, the suction, compression, and discharge operations of each cylinder are performed with a phase difference of 180 degrees.

The high-pressure gas refrigerant in the cylinder chamber 1a flows from the compression chamber 11 to the blade 2a facing the compression chamber 11 side.
The gas refrigerant leaks into the space 13 on the tip side of the blade 2a via a gap between the side surface of the blade 2 and the plane of the swinging bush 5. The gas refrigerant leaking into the space 13 leaks into the low-pressure suction chamber 10 via a gap between the side surface of the blade 2a facing the suction chamber 10 and the plane of the swing bush 6. Since the space 13 on the tip side of the blade 2a is a closed space, the path through which the gas refrigerant leaks is the blade 2a.
, And only the gap between the two side surfaces of the rocking bushes 5 and 6 forms the compression chamber 11 (high pressure side) → the space 13 → the suction chamber 1
0 (low pressure side). Further, the path through which the gas refrigerant of the other cylinder leaks is only a gap between both side surfaces of the blade 102a in FIG. 2 and the plane of the swinging bush (not shown). Therefore, the seal length for sealing the gas refrigerant is about 2 times longer than the conventional compression chamber (high pressure side) → blade tip side space → passage → suction port of the conventional rotary compressor.
And the leakage of the gas refrigerant can be reduced. Therefore,
Power loss can be reduced.

Further, as shown in FIG.
Each of the eccentric disks 4 and 104 in the 102 is fixed to the rotating shaft 3 so that the phases thereof are different from each other by 180 degrees. The total enclosed space has a constant volume at all times. Therefore, even if the blades 2a and 102a move up and down, the gas refrigerant is not compressed in the spaces 13 and 113, and the pumping loss can be eliminated.
Further, the compression of the lubricating oil and the liquid refrigerant in the spaces 13 and 113 can be prevented, and damage can be prevented.

In the above embodiment, a rotary compressor having a two-cylinder structure is used. However, a rotary compressor having a one-cylinder structure can be used similarly to the rotary compressor having a two-cylinder structure, in which a seal length for sealing a refrigerant is provided. Can be approximately doubled, and leakage of gas refrigerant can be reduced. The pumping loss due to the reciprocating motion of the blade can be reduced by increasing the volume of the space at the tip of the blade.

In the above embodiment, the number of cylinders constituting the rotary compressor is two, and each eccentric disk is one
The phase is fixed to the rotating shaft by changing the phase by 80 degrees, but the number of cylinders and each phase of the eccentric disk are of course not limited to those described above. For example, in a configuration with three cylinders,
The phase of the eccentric disk may be different by 120 degrees, and the number of cylinders may be four, and the phase of the eccentric disk may be different by 90 degrees.

[0018]

As is apparent from the above description, the rotary compressor according to the first aspect of the present invention has a structure in which the blade and the oscillating bush are brought into sliding contact with each other on a flat surface. In addition, a sealed space is formed in the housing outside the swing bush, and the tip of the blade is opened in the sealed space. Therefore, according to the present invention, the path through which the gas refrigerant leaks is a gap between both side surfaces of the blade and both planes of the swinging bush, so that the seal length for sealing the gas refrigerant is smaller than that of the conventional rotary compressor. Therefore, the leakage of the gas refrigerant can be significantly reduced, and the power loss due to the leakage can be reduced. Further, the volume of the closed space can be increased, and the pumping loss due to the reciprocating motion of the blade can be significantly reduced.

In the rotary compressor according to the present invention, the eccentric disks fixed eccentrically to the rotating shaft and rotatably fitted to the inner periphery of each rotor are made to have a fixed phase different from each other. And fixed to the rotating shaft, each blade and each swinging bush are configured to be in sliding contact with each other with a flat surface, and on the housing facing the tip of each blade and outside of each swinging bush, Sealed spaces that communicate with each other are formed, and the tips of the blades are opened in each of the sealed spaces. Therefore, according to the present invention, in addition to the effect of reducing the leakage of the gas refrigerant, the pumping loss by the blade can be reduced, and the compression of the lubricating oil and the liquid refrigerant by the blade is eliminated, thereby preventing the damage. it can.

[Brief description of the drawings]

FIG. 1 is a sectional view of a rotary compressor according to one embodiment of the present invention.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is a sectional view of a conventional rotary compressor.

[Explanation of symbols]

1, 7, 8 ... housing, 2, 102 ... rotor, 2a,
102a: blade, 3: rotary shaft, 4, 104: eccentric disk, 5, 6: swing bush, 10: suction chamber, 11: compression chamber, 12, 112: hole, 13, 113: space.

Claims (2)

(57) [Claims] 1. A housing (1) having a cylinder chamber (1a) and a hole (12) opening into the cylinder chamber (1a), and a blade (2a) disposed in the cylinder chamber (1a) and extending in a radial direction. (2) rotor having
And an eccentric disk (4) eccentrically fixed to the rotating shaft (3) and rotatably fitted to the inner periphery of the rotor (2).
A rotary bush (5, 6), which is swingably provided in the hole (12) and supports the blade (2a) so as to be able to swing and advance and retreat. (2a) and the oscillating bush (5, 6) are configured to be in sliding contact with each other with flat surfaces, and the blade (2
A closed space (13) is formed in the housing (1) on the side facing the tip of (a) and outside the swing bushes (5, 6), and the blade (2a) is formed in the closed space (13). A rotary compressor characterized in that the tip of () is opened. 2. The cylinder chambers (1a, 101a) arranged at intervals in the axial direction and the cylinder chambers (1).
a, 101a) and housings (1, 7, 8) having holes (12, 112) respectively opening therewith, and radially extending blades (2a, 102a) disposed in the cylinder chambers (1a, 101a), respectively. (2, 1)
02), and is eccentrically fixed to the rotating shaft (3), and rotatably fitted to the inner periphery of each of the rotors (2, 102),
An eccentric disk (4, 104) fixed to the rotating shaft with a fixed phase different from each other, and a swingably provided in each of the holes (12, 112), and each of the blades (2a, 102)
a) a rotary compressor having swing bushes (5, 6) for swingably and advancing and retreating, wherein each blade (2a, 102a) and each swing bush (5, 6) are connected to each other. The flat surfaces are in sliding contact with each other, and the housing (1) on the side facing the tip of each of the blades (2a, 102a) and the outside of each of the swing bushes (5, 6) is mutually connected. The closed spaces (13, 113) communicating with the respective closed spaces (13, 113) are formed respectively.
113) The rotary compressor characterized in that the blades (2a, 102a) each have an open end.