JP2002115674A - Rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary compressor capable of eliminating a defect related to a discharge valve. SOLUTION: A hole 2 communicating with a face opposing to a front head 6 from a side face on a compression chamber H side of a blade 1 joined with a rotary piston 3 is formed in the blade 1. A discharge port 6a communicating with a discharge space from a cylinder chamber 4a is formed in the front head 6. The hole 2 is communicated with the discharge port 6a only when the hole 2 and the discharge port 6a are overlapped mutually.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor, and more particularly to a rotary compressor for eliminating a problem related to a discharge valve.

[0002]

2. Description of the Related Art FIG. 15 is a schematic sectional view showing an arrangement of a discharge valve in a conventional swing type rotary compressor.
Referring to FIG. 15, cylinder chamber 104 of cylinder 104
The rotary piston 103 externally fitted to the eccentric portion 108a of the crankshaft 108 is disposed in a. A blade 101 is joined to and integrated with the outer periphery of the rotating piston 103. This blade 101 is a cylinder 1
Oscillator (bush) 105 rotatably arranged at 04
It is supported so that it can move forward and backward.

[0003] With such a configuration, in a so-called swing type compressor, the rotating piston 103 revolves without rotating in the cylinder chamber 104a by receiving the rotating force of the crankshaft 108. Due to the revolution of the rotating piston 103, the refrigerant gas sucked into the suction chamber L from the suction port 104b is compressed. After completion of the compression, the compressed refrigerant gas is supplied to the valve plate 1.
11 is opened to be discharged from the compression chamber H to the outside through the discharge port 104a.

[0004]

In a conventional rotary compressor of the so-called swing type, which has no specific volume ratio, a discharge valve 111 is required as shown in FIG. Will occur.

[0005] In terms of efficiency, since the discharge valve 111 needs to be opened, an over-compression loss always occurs under any operating conditions, and the efficiency of the compressor decreases. If the spring constant of the discharge valve 111 is reduced in order to reduce the over-compression loss, the closing delay of the discharge valve 111 occurs particularly when the crankshaft 108 rotates at a high speed. As a result, the compressed refrigerant gas once discharged from the compression chamber H flows back into the cylinder chamber 104a, causing a re-expansion loss to increase significantly.

[0006] Also, in terms of reliability, the discharge valve 11
Because of the presence of 1, there is a problem that the valve cracks occur in the discharge valve 111 at the time of liquid compression in which the valve collision speed of the discharge valve 111 increases, and that an increase in noise due to the collision sound cannot be avoided.

It is therefore an object of the present invention to provide a rotary compressor which can solve the problems related to the discharge valve.

[0008]

According to a first aspect of the present invention, there is provided a rotary compressor which revolves along an inner peripheral surface of a cylinder chamber to compress a refrigerant, and a rotary piston joined to an outer peripheral surface of the rotary piston. A rotary chamber comprising a blade for partitioning a compression chamber and a suction chamber, and a head for partitioning a cylinder chamber and a discharge space, wherein the blade faces the head from the side of the blade on the compression chamber side. The head has a discharge port that communicates from the cylinder chamber to the discharge space, and the hole provided in the blade and the discharge port provided in the head overlap, so that the hole is connected to the discharge port. The refrigerant compressed in the compression chamber is discharged to the discharge space.

In this way, since the hole provided in the blade communicates with the discharge port provided in the head, it is possible to discharge the compressed refrigerant from the compression element to the discharge space only at the discharge timing without the discharge valve. it can. Therefore,
Discharge valve is not required, excessive compression loss due to valve opening operation,
Problems related to the discharge valve, such as a remarkable increase in re-expansion loss due to a delay in closing the valve, cracking of the valve, and noise due to valve collision, are eliminated.

The head provided with the discharge port may be a front head or a rear head.

According to a second aspect of the present invention, there is provided a rotary compressor including a bush that rotatably supports a blade and allows the blade to retreat.
The hole is formed from the root of the blade to the rotating piston, and has a length equal to or less than the length of the bush in the reciprocating direction.

Thus, the compressed refrigerant can be discharged from the compression element to the discharge space only at the proper discharge timing.

In the rotary compressor according to the third aspect, the blade revolves around the rotation center of the bush due to the revolution of the rotary piston, and the shape of the discharge port starts at the apex of the rotation center of the bush. At the time of the swing angle position of the blade and the minimum swing angle position at which the blade swings most toward the discharge space side.

Thus, the compressed refrigerant can be discharged from the compression element to the discharge space only at the proper discharge timing.

[0015]

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

FIG. 1 is an enlarged partial sectional view showing a compression element portion of a swing type rotary compressor according to an embodiment of the present invention. FIG. 2 is a schematic sectional view taken along line II-II in FIG.

Referring mainly to FIG. 1, a motor M serving as an electric element is disposed at an upper portion in a closed container 10, and a compression element CF is disposed at a lower portion.

The motor M has a stator 9b and a rotor 9a. The stator 9b is mounted on the inner wall of the closed casing 10, and the rotor 9a is arranged with an air gap from the stator 9b. The crankshaft 8 is press-fitted into the rotor 9a, and the motor M and the compression element CF are connected via the crankshaft 8.

Referring mainly to FIG. 2, the compression element CF is of a so-called swing type, and includes a blade 1, a rotary piston 3, a cylinder 4, a bush 5, and a front head 6.
And a rear head 7.

The rotary piston 3 is fitted on the eccentric portion 8a of the crankshaft 8, and is disposed in the cylinder chamber 4a of the cylinder 4. The blade 1 is joined to the outer peripheral surface of the rotary piston 3 and divides the cylinder chamber 4a into a compression chamber and a suction chamber. The bush 5 supports the blade 1 so as to be able to advance and retreat, and is supported by the cylinder 4 so as to be rotatable. The cylinder 4 is provided with a suction port 4b for sucking the refrigerant gas into the cylinder chamber 4a.

Referring mainly to FIG. 1, the front head 6 and the rear head 7 are arranged at both the upper and lower ends of the cylinder 4 so as to close the cylinder chamber 4a. I have.

In the rotary compressor of the present embodiment, it should be particularly noted that the blade 1 is provided with the hole 2 and the front head 6 is provided with the discharge port 6a as shown in FIG. Is not provided.

The holes 2 provided in the blade 1 are provided so as to pass from the side of the blade 1 on the compression chamber side to the surface facing the front head 6 as shown in FIGS.
Therefore, the hole 2 has an opening 2 a opened on the side surface of the blade 1 on the compression chamber side, and an opening 2 b opened on the surface facing the front head 6. The opening 2a of the hole 2 on the front head 6 side is located at the center line D of the blade 1.
Is located closer to the suction chamber. The hole 2 has a length L from the root of the blade 1 to the rotary piston 3 in the direction in which the blade 1 advances and retreats, as shown in FIG.
It has the following length:

The discharge port 6a provided on the front head 6 is provided on the blade 1 only from the time when the refrigerant reaches the discharge pressure to the time when the discharge of the refrigerant is completed, as shown in FIGS. It is positioned so as to communicate with the hole 2. Further, the shape of the blade 1 at the time when the refrigerant reaches the discharge pressure with respect to a straight line C connecting the rotation center of the bush 5 (the bush center) and the rotation center of the crankshaft 8 as shown in FIG. The blade 1 has a fan shape sandwiched between an angle of the center line (oscillation angle at the start of ejection) and an angle (minimum oscillation angle) at which the blade 1 swings most toward the ejection space.

Next, the operation of compressing and discharging the refrigerant in the rotary compressor according to the present embodiment will be described.

FIGS. 8 to 14 are sectional views showing the operation of the rotary compressor according to one embodiment of the present invention.

First, when the crankshaft 8 is rotated from the state shown in FIG. 2, the rotating piston 3 revolves in the cylinder chamber 4a. At this time, the bush 5 rotates along with the revolving motion of the rotary piston 3, and the blade 1
It moves forward and backward with respect to and swings. In this state, the hole 2 of the blade 1 and the discharge port 6a of the front head 6 are not in communication.

Referring to FIG. 8, when crankshaft 8 rotates 40 ° from the state shown in FIG. 2, rotating piston 3 closes refrigerant gas inlet 4b.

Referring to FIG. 9, when the crankshaft 8 rotates 78 ° from the state of FIG. 2, the blade 1 is in the state of swinging most toward the suction chamber L side.

Referring to FIG. 10, blade 1 has suction chamber L
From the side to the compression chamber H side. Referring to FIG.
When the crankshaft 8 rotates by 180 ° from the state described above, the rotating piston 3 reaches the bottom dead center.

Referring to FIG. 12, when the crankshaft 8 rotates 200 ° from the state of FIG. 2, the compressed refrigerant reaches the discharge pressure. The hole 2 of the blade 1 and the discharge port 6a of the front head 6 communicate with each other. As a result, the compressed refrigerant that has reached the discharge pressure starts to be discharged into the discharge space through the hole 2 and the discharge port 6a. The angle between the straight line C and the center line of the blade 1 in this state is the swing angle at the start of discharge.

Referring to FIG. 13, when the crankshaft 8 rotates 282 ° from the state of FIG. 2, the blade 1 is in a state of swinging most toward the compression chamber H side. Also in this state, the hole 2 of the blade 1 and the discharge port 6a of the front head 6 are in communication. Straight line C and blade 1 in this state
Is the minimum swing angle.

Referring to FIG. 14, blade 1 has a compression chamber H
From the side to the suction chamber L side, and returns to the state of the top dead center shown in FIG. Thereby, the communication between the hole 2 of the blade 1 and the discharge port 6a of the front head 6 is released, and the discharge of the compressed refrigerant is completed.

As described above, the hole 2 of the blade 1 and the discharge port 6a of the front head continue to communicate from the discharge start point shown in FIG. 12 to the state shown in FIG.
During this time, the compressed refrigerant in the compression chamber H continues to be discharged into the discharge space, and the discharge ends in the state of FIG.

In this embodiment, the compressed refrigerant in the compression chamber H is discharged by the overlap of the hole 2 provided in the blade 1 and the discharge port 6a provided in the front head 6.
No discharge valve is required. Therefore, problems caused by providing the discharge valve, such as excessive compression loss due to opening operation of the valve, remarkable increase in re-expansion loss due to delay in closing the valve,
Problems such as valve cracking and noise due to valve collision are eliminated.

In the present embodiment, a one-cylinder type rotary compressor has been described, but the present invention can also be applied to a rotary compressor having two or more cylinders.

The position of the hole 2 provided in the blade 1 and the position of the discharge port 6a provided in the front head 6 are not limited to the positions described above, and the compressed refrigerant is supplied only when the hole 2 and the discharge port 6a overlap. The hole 2 and the discharge port 6a may be arranged at any position as long as the position can be appropriately discharged into the discharge space.

In particular, the discharge port 6a may have a fan shape that extends from the minimum swing angle position to an angular position on the compression chamber H side.

In this embodiment, the discharge port 6a
Has been described in the case where is provided in the front head 6,
The discharge port may be provided in the rear head 7. In this case, the hole 2 provided in the blade 1 needs to be opened on the surface facing the rear head 7.

As described above, the configuration of the present invention is not limited to the configuration of the above-described embodiment, but includes the meaning equivalent to the claims and all modifications within the scope.

[0041]

In the rotary compressor according to the first aspect, the hole provided in the blade communicates with the discharge port provided in the head, so that the compression element can be compressed only at the discharge timing without a discharge valve. The refrigerant can be discharged into the discharge space. Therefore, a discharge valve is not required, and problems related to the discharge valve such as excessive compression loss due to opening of the valve, re-expansion loss due to delay in closing the valve, remarkable increase in valve cracking, and noise due to valve collision are eliminated. .

According to a second aspect of the present invention, there is provided a rotary compressor including a rotatable bush that supports a blade so as to be able to move forward and backward,
The hole is formed from the root of the blade to the rotating piston and has a length that is less than or equal to the length of the bush in the direction of blade retraction. Thus, the compressed refrigerant can be discharged from the compression element to the discharge space only at the proper discharge timing.

In the rotary compressor according to the third aspect, the blade revolves around the rotation center of the bush due to the revolution of the rotary piston, and the shape of the discharge port starts at the vertex of the rotation center of the bush. At the time of the swing angle position of the blade and the minimum swing angle position at which the blade swings most toward the discharge space side. Thus, the compressed refrigerant can be discharged from the compression element to the discharge space only at the proper discharge timing.

[Brief description of the drawings]

FIG. 1 is an enlarged partial sectional view showing a compression element of a rotary compressor according to an embodiment of the present invention.

FIG. 2 is a schematic sectional view taken along line II-II in FIG.

FIG. 3 is a perspective view for explaining a shape of a hole provided in a blade.

FIG. 4 is a plan view for explaining a shape of a hole provided in a blade.

FIG. 5 is a side view for explaining the shape of a hole provided in the blade.

FIGS. 6A and 6A are plan views for explaining the shape of a discharge port provided in a front head, and AA in FIG.
It is a schematic sectional view (b) which follows along.

FIG. 7 is an enlarged view of a region B in FIG.

FIG. 8 is a first process diagram for describing a compression / discharge operation of the rotary compressor in one embodiment of the present invention.

FIG. 9 is a second process diagram for describing a compression / discharge operation of the rotary compressor in one embodiment of the present invention.

FIG. 10 is a third process diagram for describing a compression / discharge operation of the rotary compressor in one embodiment of the present invention.

FIG. 11 is a fourth process diagram for describing a compression / discharge operation of the rotary compressor in one embodiment of the present invention.

FIG. 12 is a fifth process diagram for describing a compression / discharge operation of the rotary compressor in one embodiment of the present invention.

FIG. 13 is a sixth process diagram for describing the compression / discharge operation of the rotary compressor in one embodiment of the present invention.

FIG. 14 is a seventh process diagram for describing the compression / discharge operation of the rotary compressor in one embodiment of the present invention.

FIG. 15 is a schematic sectional view showing a configuration of a rotary compressor having a conventional discharge valve.

[Explanation of symbols]

Reference Signs List 1 blade, 2 holes, 3 rotating pistons, 4 cylinders, 4a cylinder chamber, 5 bush, 6 front head, 6a discharge port, 7 rear head, 8 crankshaft, 8a eccentric part, 9a rotor, 9b stator, 10
Closed container, CF compression element, M motor.

Claims (3)

[Claims] 1. A rotary piston (3) for compressing refrigerant by revolving along an inner peripheral surface of a cylinder chamber (4a), and a cylinder chamber (4a) mounted on an outer peripheral surface of the rotary piston (3). A rotary compressor comprising: a blade (1) for partitioning a cylinder into a compression chamber (H) and a suction chamber (L); and a head (6) for partitioning the cylinder chamber (4a) and a discharge space. The blade (1) has a hole (2) extending from a side surface of the blade (1) on the compression chamber (H) side to a surface facing the head (6), and the head (6) A discharge port (6a) communicating from the cylinder chamber (4a) to the discharge space, the hole (2) provided in the blade (1), and the discharge port (6) provided in the head (6). 6a) and the hole (2) is Out port (6a)
And the refrigerant compressed in the compression chamber (H) is discharged to the discharge space. 2. A bush (5) rotatably supporting and removably supporting the blade (1), wherein the hole (2) is provided to allow the blade (1) to be connected to the rotary piston (3). The rotary compressor according to claim 1, wherein the rotary compressor is formed from a base and has a length equal to or less than a length of the bush (5) in the retreating direction. 3. The revolution of said rotary piston (3)
The blade (1) swings about a rotation center of the bush (5) as a fulcrum, and the shape of the discharge port (6a) is the shape of the bush (5).
The rotation center of the blade (1) is sandwiched between the swing angle position of the blade (1) at the start of discharge and the minimum swing angle position at which the blade (1) swings most toward the compression chamber (H), with the rotation center of the blade as the apex. 3. The rotary compressor according to claim 2, wherein the rotary compressor has a sector shape.