JPH0713518B2 - 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, the high temperature refrigerant existing on the high pressure side in the system flows into a low pressure cooler and becomes a heat load when the system is stopped. 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 constantly biases the ball valve 17 toward the high pressure side outlet port 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 port 12 is opened, and the ball valve 17 is adsorbed and sealed to the low pressure side port 16 for normal operation. It is something that enters.

DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention However, in the above configuration, the ball valve 17 is pulled out from the high pressure side outlet port due to the existence of the clearance between the ball valve 17 and the valve cylinder 19 on which the ball valve 17 slides. It is difficult to reduce the pressure in the low-pressure side port, which is the valve opening force, and it is necessary to keep the clearance to a minimum, but this not only increases the processing accuracy and processing costs such as matching assembly, but also increases the operation. In the worst case, foreign matter such as abrasion powder generated from the rotating and sliding parts inside will enter the clearance, and in the worst case, the ball valve 17 will also develop a phenomenon similar to the hydraulic lock phenomenon found in general spool valves. May cause 17 inoperability. Further, in order to avoid the reduction of the clearance, it is conceivable to increase the effective pressure receiving area of the ball valve 17, but this not only increases the space for assembling the high pressure valve 10, but also the impact during operation due to the increase in weight. There are also problems such as sound generation.
Further, in the illustrated conventional example, since a soft metal such as brass that can easily form a three-dimensional curved surface is used as the port of the ball valve 17, the number of parts and the number of assembling steps are increased. Further, the same applies to the pressure guiding tube 14, and an increase in cost cannot be avoided.

In view of the above-mentioned problems, the present invention makes it possible to obtain the necessary pressure difference at the time of startup without reducing the clearance or increasing the effective pressure receiving area of the valve, and also to reduce the mounting space and the number of parts. Reduces the manufacturing cost and expands the allowable size of the sealing surface caused by dimensional variations during assembly, making it easier to assemble and
The purpose of the present invention is to reduce unnecessary behavior of the high-pressure valve due to a sudden gas flow pressure at the time of starting the compressor (for example, sheeting delay to the low-pressure side port due to inclination).

Means for Solving the Problems A rotary compressor of the invention for solving the above problems includes a closed container, a compression element and a motor housed in the closed container, and the compression element includes a crankshaft. A side plate having a bearing portion that supports the shaft, a cylinder plate that rotatably accommodates the rotor, and the side plate and the cylinder plate are polymerized to form a compression chamber, and the compression chamber is partitioned into a low pressure chamber and a high pressure chamber. A high pressure side inlet port that communicates with the vane, the low pressure chamber and the high pressure chamber, respectively, and a suction valve and a discharge valve that are arranged close to the vane and perform a check valve action, and that are in constant communication with the sealed container. And a high-pressure side outlet port that always communicates with the discharge pipe and a low-pressure side port that directly communicates with the low-pressure chamber of the compression chamber, and simultaneously closes the high-pressure side input port and the low-pressure port on one side surface. A structure in which a disc-shaped high-pressure valve that can be closed at the other end surface and the low-pressure side port is provided, and the inlet port is formed on the side plate by inclining from the outside toward substantially the center of the high-pressure valve. belongs to.

Effect The present invention has the above-described configuration, and at the time of startup, the high pressure inlet port and the outlet port are closed at the same time, so that the pressure drop of the low pressure side port can be realized very sharply.
Therefore, it is possible to open the high pressure valve that is strongly adsorbed to the high pressure outlet port by the force generated by the difference between the system internal pressure that is reduced when stopped and the internal pressure of the closed container that is maintained at a substantially high pressure. Even if the gas flow flows into the low pressure side port from the high pressure side inlet after the initial separation, the inclination due to the extreme gas flow pressure hardly occurs, and the low pressure side port is quickly closed. Immediately after the stop, the pressure in the cylinder rapidly balances with the pressure in the closed container via, for example, the clearance between the vane and the cylinder. on the other hand,
Since it is a low-pressure side port, the volume can be set to the minimum, so the pressure balance between the low-pressure side port and the closed container can be achieved in a short time, and therefore the separation from the low-pressure side port can also be done in a short time, and the bias spring force can be used. Rapidly close the high pressure side inlet and outlet ports.

Example An example 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 denotes a crankshaft press-fitted and fixed to the rotor 52a, and bearing portions 5 formed on the side plates 55 and 56.
It is rotatably supported by 5a and 56a. 57 is a cylinder plate on which a rotor 58 mounted on the eccentric portion 54a of the crankshaft 54 is rotatably mounted. 59 is a vane that divides the compression chamber 60, which is fixed 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.
a is a vane groove. Reference numeral 63 is a bolt for fixing the side plates 55, 56 and the cylinder plate 57 together. 64 is an evaporator
A suction pipe that guides the refrigerant gas from the compression chamber 60 from 65, and is press-fitted and fixed in the pressure bore 65 of the side plate 55. Press fit bore 65
The end surface of the end plate on the cylinder plate 57 side is configured as the valve seat surface of the disc-shaped intake valve 66. This press fit bore 65
In the suction passage 67 communicating with the cylinder 59 and adjacent to the vane 59, the suction valve 66 is housed, and a bias spring 68 for keeping the valve 66 closed by a weak force is housed. There is. 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 discharge valve for discharging the compressed refrigerant gas in the compression chamber 60 directly or via a precooler pipe (not shown) into the closed container 51 (Fig. 2). Reference numeral 71 is a high-pressure valve device, which is arranged at substantially the same height as the crankshaft 54. This high pressure valve 71 is a side plate
55 High-pressure side inlet port 72 that extends in the axial direction of the crankshaft 54
And a high-pressure side outlet port 74 communicating with the discharge pipe 73 penetrating the closed container 51. The discharge pipe 73 is press-fitted and fixed in the press-fitting hole 73a. As is clear from FIGS. 3 and 4, the inlet and outlet ports 72 and 74 are formed so that the inlet port 72 is slanted from the outside toward the substantial center of the high pressure valve 71.
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 outside.
72 are arranged. However, O in the figure represents the center of the crankshaft. Further, the cylinder plate 57 has a common valve cylinder 7 formed corresponding to each of the adjacent ports 72 and 74.
5, a low pressure side port 76 is formed at the bottom of the valve cylinder 75. Reference numeral 77 is a disk-shaped high pressure valve which can close the inlet and outlet ports 72 and 74 on one side and can close the low pressure side port 76 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. 79 indicates the low pressure chamber 6 of the cylinder 59 from the low pressure side port 76 and the opening 76a on the side plate 56 side.
1 is a pressure guiding path that directly communicates with 1, and the opening 76a is closed by the side plate 56.

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.
Of the pressure difference between the upstream and downstream of the condenser, that is, the pressure difference between the condensation saturation pressure at the temperature of the cooling chamber in which 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 a 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 high pressure valve 77 has not been pulled initially, the high pressure valve 77
The high pressure valve 77 resists the force of the bias spring 78, and the low pressure side port 76
Is closed and the valve opening operation is completed. 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 high pressure chamber 63 and the low pressure chamber 61 in the cylinder 60 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. Further, as is clear from FIG. 4, the inclined inlet port 72 can alleviate the uneven thickness of the discharge pipe 73 at the time of press-fitting, and the sealing property by press-fitting can be improved.

EFFECTS OF THE INVENTION As described above, according to the present invention, the high pressure side inlet port which is always in communication with the closed container, the high pressure side outlet port which is always in communication with the discharge pipe, and the low pressure side which is directly communicated with the low pressure chamber of the compression chamber through the pressure guiding passage are provided. A high pressure side inlet port and a low pressure port simultaneously closed on one side surface, and a disc-shaped high pressure valve capable of closing the low pressure side port on the other end surface, wherein the inlet port is the high pressure valve. Since it is formed to incline from the outside toward the approximate center, it is not necessary to reduce the clearance between the ball valve and the sliding valve cylinder of this valve as in the conventional example, and the valve opening drive force of the high pressure valve The pressure drop in the low-pressure side port 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. The time for increasing the pressure in the port can be shortened, and the time for closing the high-pressure side outlet port can be shortened. Further, since the high pressure side inlet port is arranged to be inclined as described above, the gas flow from the inlet port to the low pressure port at the time of startup collides with the center of the high pressure valve almost. The number of seats can be reduced and seating can be done smoothly.

[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.
Fig. 4 is a sectional view taken along line III ', Fig. 4 is a sectional view taken along line III-IV', Fig. 5 is a perspective view of a main portion of a cylinder plate, and Fig. 6 is a sectional view of a conventional rotary compressor. 51 …… closed container, 53 …… compression element, 52 …… electric element, 54
...... Crankshaft, 55,56 …… 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, 76 ...... Pressure passage, 77 ...... High pressure valve.

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 rotatably rotates a side plate having a bearing portion for supporting a crankshaft. A cylinder plate to be housed, a compression chamber is formed by superposing the side plate and the cylinder plate, and a vane for partitioning the compression chamber, the low pressure chamber and the high pressure chamber,
A suction valve and a discharge valve that communicate with the low-pressure chamber and the high-pressure chamber, respectively, and that are arranged in the vicinity of the vane and that perform a check valve action; a high-pressure side inlet port that always communicates with the closed container; A high-pressure side outlet port that always communicates with the pipe and a low-pressure side port that directly communicates with the low-pressure chamber of the compression chamber via a pressure guide path are provided, and the high-pressure side inlet port and the outlet port are simultaneously closed on one side surface. A rotary plate formed on the side plate, which includes a disk-shaped high-pressure valve capable of closing the low-pressure side port at the other end surface, and in which the high-pressure side inlet port is inclined outward from approximately the center of the high-pressure valve. compressor.