JPH07117054B2 - Rotary compressor - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a rotary compressor used in a refrigerating device such as a refrigerator or a showcase.

2. Description of the Related Art In a device that cools the inside of a refrigerator by cycling a compressor, when stopped, the high temperature refrigerant present on the high pressure side in the system flows into the low pressure cooler and becomes a heat load. Will increase. In order to prevent this phenomenon, a technique has been proposed in which the low-pressure side and high-pressure side refrigerant passages are closed in the compressor when stopped.

The conventional compressor described above will be described below with reference to FIG.

In FIG. 6, 1 is a rotary compressor, 2 is a closed container, 3 is a cylinder plate, 3a is a cylinder, 4 is a crankshaft, and a roller 5 is slidably arranged on an eccentric portion 4a thereof. Reference numeral 6 is a vane that partitions the interior of the compression chamber 7 into high and low pressure chambers. Reference numeral 8 is a suction valve that serves as a check valve, and closes a suction port that communicates with a suction pipe (not shown). Further, 9 is a discharge valve, and the refrigerant gas compressed in the compression chamber 7 passes through the discharge valve 9 and is discharged into the closed container 2. Reference numeral 10 is a high pressure valve that is opened when the rotary compressor 1 is operating and closed when the rotary compressor 1 is stopped. The high-pressure valve 10 includes a high-pressure side outlet port 12 that communicates with a discharge pipe 11 that penetrates the closed vessel 2 and a high-pressure side inlet port 13 that always communicates with the closed vessel 2. Further, a low pressure side port 16 is provided which communicates with the suction passage 15 through the pressure guiding pipe 14. A ball valve 17 alternately opens and closes the high pressure side outlet port 12 and the low pressure side port 16. Reference numeral 18 is a bias spring that always biases the ball valve 17 toward the high pressure side outlet boat 12 side.

In such a configuration, when the compressor 1 is stopped, the pressure in the pressure guiding tube 14 and the pressure in the closed container 2 are balanced, and the force of the bias spring 18 and the difference between the pressure in the closed container 2 and the pressure on the cooling system side. Ball valve by force generated by
17 closes the outlet port 12 on the high pressure side. Therefore, the high-pressure high-temperature gas filling the space of the closed container 2 is discharged into the discharge pipe 11
It does not flow out to the cooling system via. At this time, the suction valve 8 that operates as a check valve is also closed, and the outflow to the cooling system via the suction pipe (not shown) is also prevented.

Next, the startup will be described. Due to the start-up, the pressure in the low pressure chamber in the compression chamber 7 decreases and the pressure in the suction passage 15 and the pressure guiding pipe 14 decreases, causing a pressure difference between the high pressure side inlet port 13 side and the low pressure port 16 side of the high pressure valve 10, resulting in a high pressure. The ball valve 17 adsorbed to the side outlet port 12 is pulled against the force of the bias spring 18, the high pressure side outlet boat 12 is opened, and the ball valve 17 is adsorbed and sealed to the low pressure side boat 16 for normal operation. It is something that enters.

DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention However, in the above-mentioned configuration, the pressure guiding pipe 14 is a separate component, the number of assembling operations increases, and the low pressure port 16
However, there was a problem that it was difficult to check the sealing performance.

Means for Solving the Problems In view of the above problems, the rotary compressor of the present invention is configured by forming a groove portion in the cylinder plate of the pressure guiding path and closing the groove portion with the side plate. By forming a substantially cylindrical recess in a part of the groove portion, a rubber plug for closing the pressure guide passage can be easily fitted at the time of checking the seal of the low pressure port, and the check can be performed efficiently.

Operation According to the present invention, the pressure guide passage is formed at the same time when the side plate and the cylinder plate are superposed and assembled. Further, the pressure guiding path can be closed by pressing the plug into the substantially cylindrical recess when checking the seal of the low pressure port.

Embodiment One embodiment of the present invention will be described below with reference to the drawings.

In FIG. 1, 50 is a rotary compressor, 51 is a closed container, 52 is an electric element including a rotor 52a and a stator 52b, and 53 is a compression element. Reference numeral 54 is a crankshaft press-fitted and fixed to the rotor 52a, and is rotatably supported by bearings 55a and 56a formed on the first and second side plates 55 and 56. 57 is a cylinder plate on which a rotor 58 mounted on the eccentric portion 54a of the crankshaft 54 is rotatably mounted. Reference numeral 59 is a vane that partitions the compression chamber 60 defined by the outer periphery of the rotor 58, the inner periphery of the cylinder 59, and the side plates 55, 56 into a low pressure chamber 61 and a high pressure chamber 62, and 59a is a vane groove. 63 is a bolt for fixing the first and second side plates 55, 56 and the cylinder plate 57 together. This bolt 63 has a clearance C for assembling with the bolt hole 63a, and therefore, the side plate 55 can be moved in the circumferential direction, though slightly. Reference numeral 64 is a suction pipe that guides the refrigerant gas from the evaporator 65 to the compression chamber 60, and is press-fitted and fixed to the press-fitting bore 65 of the first side plate 55.
An end plate end surface of the press-fitting bore 65 on the cylinder plate 57 side constitutes a valve seat surface of a disc-shaped intake valve 66. In the suction passage 67 connected to the press-fitting bore 65 and communicating with the vane 59, the suction valve 66 is housed and a bias spring 68 for keeping the valve 66 closed with a weak force is housed. Reference numeral 69 is a stepped portion that restricts the movement of the suction valve 66 when it is opened. Reference numeral 70 denotes a closed container for the compressed refrigerant gas in the compression chamber 60 directly or via a precooler pipe (not shown).
It is a discharge valve leading out into 51 (Fig. 2). Reference numeral 71 is a high-pressure valve device, which is arranged at substantially the same height as the crankshaft 54. The high-pressure valve 71 has a high-pressure side inlet port 72 that extends to the side plate 55 in the axial direction of the crankshaft 54 and a high-pressure side outlet port that communicates with a discharge pipe 73 that penetrates the sealed container 51.
Equipped with 74. As is clear from FIGS. 3 and 4, the inlet and outlet ports 72 and 74 are arranged side by side in the normal direction of the side plate 57, with the outlet port 74 inside and the inlet port 72 outside. is doing. However, the center of the crankshaft is represented by O in the figure. Further, the cylinder plate 57 is provided with a common valve cylinder 75 formed corresponding to each of the adjacent ports 72 and 74, and a low pressure side port 76 is formed at the bottom of the valve cylinder 75. 77 is a disk-shaped high pressure valve, and the inlet and outlet ports 72 and 7 are provided on one side.
4 can be closed and the low pressure side port 76 can be closed on the other side. 78 is a bias spring that always biases the high pressure side inlet and outlet ports 72 and 74 to close. Reference numeral 79 is a pressure guide passage that directly communicates with the low pressure chamber 61 of the cylinder 59 through the low pressure side port 76 and the opening 76a on the side of the second side plate 56. The groove portion 79a is machined or sintered alloy on the end surface of the cylinder plate 57. It has been processed and applied. Reference numeral 79b is a substantially cylindrical recess formed at an intermediate position of the groove portion 79a. As shown in FIG. 6, when checking the sealing property of the low pressure port 76, the substantially cylindrical recess 79b is formed.
By pressing the plug A made of rubber or the like into b and setting the cylinder plate 57 on the jig B, the gas leaking from the sealing surface of the low pressure port 76 flows from the pressure guiding path 79 to another place. Instead, it can lead to the check channel C.

Further, the upper surface openings of the groove portion 79a and the substantially cylindrical recess 79b can be closed by superposing and assembling the cylinder plate 57 on the second side plate 56 to form the pressure guide 79.

The operation of the rotary compressor configured as described above will be described below.

FIG. 1 shows a stopped state, in which the low-pressure valve 66 acting as a check valve is closed, and the high-pressure valve 77 simultaneously closes both the high-pressure side inlet port 72 and the high-pressure side outlet port 74. There is. At this time, the high pressure valve 77 is connected to the high pressure side outlet port 74.
By the pressure difference between the upstream and the downstream of the, i.e., the pressure difference between the condensation saturation pressure at the temperature of the cooling chamber where the evaporator 65 is arranged and the saturation pressure at the temperature of the closed vessel 51, and a slight bias spring 78 force. It is closed.

Therefore, the high-temperature high-pressure gas in the closed container 51 is prevented from flowing into the condenser 80 and the evaporator 65, and the heat load invading the evaporator 65 is reduced.

Next, the startup will be described.

The crankshaft 54 rotates when the electric element 52 is energized, and the compression chamber
A pressure drop occurs in the low pressure chamber 61 of 60. This pressure drop is reliably performed in an extremely short time even in the relatively rough clearance (for example, about 0.1 mm) between the high pressure valve 77 and the valve cylinder 75 because the high pressure side inlet port 72 is closed. This pressure drop naturally occurs in the pressure guiding path 79, the low pressure side port 76,
The pressure in the valve cylinder 75 decreases, and the pressure difference in the high pressure side inlet port 72, that is, the pressure in the closed container 51 and the pressure in the valve cylinder 75 acts on the high pressure valve 77, and the high pressure side outlet port 72 is strongly
The high pressure valve 77 adsorbed on the side is released. After the initial pull-out operation of the high pressure valve 77, the dynamic pressure of the gas flow is also added, and the high pressure valve 77 closes the low pressure side port 76 against the force of the bias spring 78 and completes the valve opening operation. On the other hand, the suction valve 66 is also opened, and the normal cooling operation is performed.

Next, the operation when stopped will be described.

When the rotation of the crankshaft 54 is stopped, the suction valve 66 is closed by stopping the gas flow in the suction pipe 64. Further, the oil seal that divides the inside of the cylinder 60 into the high pressure chamber 63 and the low pressure chamber 61 is broken,
The high-pressure gas in the closed container 51 is, for example, a vane 59 and a vane groove 59.
The pressure in the low pressure chamber 61 is increased by the clearance of a or the like. This pressure increasing action extends to the low pressure side port 76 through the pressure guiding path 79 and the volume of the pressure guiding path 79 can be made small, so that the pressure increasing time can be shortened. When the pressure in the low-pressure side port 76 and the pressure in the closed container 51 are equalized, the high-pressure valve 77 leaves the low-pressure side port 76 by the force of the bias spring 78 and simultaneously closes the high-pressure side inlet port 72 and the high-pressure side outlet port 74. To do.

Therefore, the high-pressure high-temperature gas in the closed container 51 is prevented from flowing out to the condenser 80 and the evaporator 65 while the compressor is stopped.

Although not shown, the pressure guiding path 79 may be formed by forming a groove in the second side plate.

EFFECTS OF THE INVENTION As described above, according to the present invention, the high-pressure side inlet port which always communicates with the inside of the closed container and the high-pressure side outlet port which always communicates with the discharge pipe are formed in the first side plate and the second side plate. And a low pressure side port that directly communicates with the low pressure chamber of the compression chamber by means of a pressure guiding path formed by forming a groove on one side of the cylinder plate, and the high pressure side inlet port and the low pressure port are closed simultaneously on one side surface. Since the disk-shaped high-pressure valve capable of closing the low-pressure side port on the other end surface is provided, it is not necessary to reduce the clearance between the ball valve and the valve cylinder on which the valve slides as in the conventional example, and the high-pressure valve is not required. The pressure drop at the low-pressure side port, which is the valve opening driving force, can be reliably performed in an extremely short time. Therefore, not only a stable valve opening operation can be obtained, but also machining accuracy and assembly accuracy can be relaxed and productivity can be improved. Furthermore, the locking phenomenon of the valve due to foreign matter does not occur. Further, the effective area of the valve is not increased, the valve can be made compact, and the operating noise is not increased. On the other hand, in the valve opening operation, since the pressure guiding path that directly communicates with the low pressure chamber of the compression chamber is formed, not only the parts such as the pressure guiding tube are unnecessary but also the pressure guiding path volume is reduced, and the low pressure side after the stop. Shorten the time to increase the pressure in the port,
The time required to close the high pressure side exit port can be shortened.

In addition, when checking the low-pressure port for leaks, it is possible to easily prevent the test gas from flowing to other places through the pressure guiding path by press-fitting the sealing material into the substantially cylindrical recess formed in the groove. Is improved.

[Brief description of drawings]

FIG. 1 is a sectional view of a rotary compressor showing an embodiment of the present invention, and FIGS. 2 and 3 are II-II 'lines and III- lines in FIG.
A sectional view taken along line III ', FIG. 4 is a sectional view taken along line VI-VI' in FIG. 3, FIG. 5 is a perspective view of a main portion of a cylinder plate, and FIG. 6 is a diagram showing a state of leak check of a low pressure port. FIG. 7 is a sectional view of a conventional rotary compressor. 51 …… closed container, 53 …… compression element, 52 …… electric element, 54
…… Crankshaft, 55 …… First side plate, 56 ……
Second side plate, 57 ... Cylinder plate, 60 ...
… Compression chamber, 61 …… Low pressure chamber, 62 …… High pressure chamber, 59 …… Vane, 66 …… Suction valve, 70 …… Discharge valve, 72 …… High pressure side inlet port, 74 …… High pressure side outlet port, 73 …… Discharge pipe, 79 ……
Pressure guiding path, 77 ... high pressure valve, 79a ... groove, 79b ... substantially cylindrical recess.

Claims (1)

[Claims] 1. A hermetically sealed container, a compression element and an electric element housed in the hermetically sealed container, wherein the compression element has first and second side plates each having a bearing portion for pivotally supporting a crankshaft. A cylinder plate accommodating the rotor rotatably, a compression chamber configured by superposing the first and second side plates and the cylinder plate, and a vane partitioning the compression chamber, the low pressure chamber and the high pressure chamber, A high pressure side inlet port communicating with the low pressure chamber and the high pressure chamber and provided with a suction valve and a discharge valve which are arranged close to the vane and have a check valve action, and a high pressure side inlet port which always communicates with the closed container; The high-pressure side inlet port and the high-pressure side outlet port, which are always in communication with the pipe, and the low-pressure side port, which directly communicates with the low-pressure chamber of the compression chamber through the pressure guiding path, and which are formed in the first side plate. And one side closed at the same time And a disk-shaped high pressure valve capable of closing the low pressure side port at the other end surface,
A rotary compressor in which the pressure guiding path is formed by forming a groove portion having a substantially cylindrical recess in one of the second side plate and the cylinder plate.