JPH0713519B2 - 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. 7, 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 the 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. In addition, the cost of the pressure guiding tube 14 is unavoidably increased, and the reduction of the required pressure due to the pressure loss of the passage deteriorates.

In view of the above-mentioned problems, the present invention makes it possible to obtain the required pressure difference at the time of startup without reducing the clearance or increasing the effective pressure receiving area of the valve, and also reducing the mounting space and the number of parts. Reduces the manufacturing cost and expands the allowable dimension of the seal surface caused by dimensional variations during assembly, making it easier to assemble and
The purpose 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, a seating delay to the low-pressure side port due to inclination).

Means for Solving the Problems In order to solve the above problems, a rotary compressor of the present invention includes a closed container, a compression element and a motor housed in the closed container, and the compression element is a crankshaft. A side plate having a bearing portion that axially supports, a cylinder plate that rotatably houses the rotor, and the side plate and the cylinder plate are polymerized to form a compression chamber,
A vane for partitioning the compression chamber into a low-pressure chamber and a high-pressure chamber, and an intake valve and a discharge valve that communicate with the low-pressure chamber and the high-pressure chamber and that are arranged close to the vane and 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 constantly communicates with the discharge pipe, and a low-pressure side port that directly communicates with the low-pressure chamber of the compression chamber, and the high-pressure side inlet port, A low pressure port is closed on one side at the same time, and a cup-shaped high-pressure valve that can close the low-pressure side port on the other end is provided, and the high-pressure valve has a peripheral edge with sealing surfaces on both sides and a notch-shaped degassing passage. The flange is formed.

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 presence of the peripheral flange makes it difficult to cause an inclination due to the extreme gas flow pressure, and quickly closes the low pressure side port. 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 that 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 be performed in a short time, and the bias spring The force rapidly closes the high pressure side inlet and outlet ports.
At this time, the pressure generated by the movement of the valve is easily equalized before and after the valve by the gas vent passage in the flange portion. Also, since the high pressure side port is arranged as described above, the lap margin with the valve does not easily change due to the circumferential play due to the presence of the clearance between the side plate and the bolt that secures it, and the seal It is possible to secure the surface without improving the assembly accuracy.

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. 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.
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 65 to the compression chamber 60 is press-fitted and fixed to the press-fitting bore 65 of the side plate 55. Press fit bore
The end face of the end plate of the cylinder 65 on the cylinder plate 57 side constitutes the valve seat surface of the disc-shaped intake valve 66. This press fit bore
The suction passage 67 connected to the vane 59 and connected to the vane 59 and communicating with the cylinder 59 accommodates the suction valve 66 and a bias spring 68 for keeping the valve 66 closed with a weak force. ing. 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). 71
Is a high-pressure valve device and is arranged at substantially the same height as the crankshaft 54. This high-pressure valve 71 is a high-pressure side inlet port that extends in the side plate 55 in the axial direction of the crankshaft 54.
72, and a high-pressure side outlet port 74 communicating with a discharge pipe 73 penetrating the closed container 51. This entrance and exit port 72,7
As is clear from FIGS. 3 and 4, 4 are arranged side by side in the normal direction of the side plate 57, and the outlet port is provided inside.
74 and the inlet port 72 on the outside. However, 0 in the figure represents the center of the crankshaft. Further 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 cup-shaped high-pressure valve, in which the inlet / outlet ports 72, 74 can be closed on one side and the double-sided sealing surface 77a that can close the low-pressure side port 76 on the other side, and the peripheral flange 77b are integrally squeezed. It is formed by processing. Reference numeral 77c is a cutout-shaped gas vent passage formed in the peripheral flange 77b. 78 is a bias spring that always biases the high pressure side inlet and outlet ports 72 and 74 to close. 79 is the low pressure side port
Cylinder 5 from the opening 76a on the side of 76 and one side plate 56
9 is a pressure guiding path that directly communicates with the low pressure chamber 61, 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 double-sided sealing surface 77a of the high-pressure valve 77 has a high-pressure side inlet port 72 and a high-pressure side outlet port 74. Both are closed at the same time. At this time the high pressure valve
Reference numeral 77 denotes a pressure difference between the upstream side and the downstream side of the high pressure side outlet port 74, that is, a force due to a 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. It is closed by a slight force of bias spring 78.

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. At this time, the peripheral flange 77b allows smooth operation without excessive inclination. On the other hand, the suction valve 66 is also opened, and the normal cooling movement 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. At this time, the notch-shaped gas vent passage 77c of the peripheral edge flange 77b can equalize the pressure difference between the front and rear of the valve 77, which occurs when the valve 77 moves, in a short time, so that the closing time becomes short.

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, since the high pressure side inlet port 72 and the high pressure side outlet port 74 are juxtaposed in the normal direction, even if the side plate 57 is moved in the radial direction during assembly, the inlet and outlet ports 72,74
The amount of change in the lap margin with the valve 77 can be remarkably reduced as compared with the case where are arranged in the circumferential direction.

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 double-sided seal part capable of closing the low pressure side port on the other end surface, and a peripheral flange having a notched gas vent passage Since a cup-shaped high-pressure valve having a portion is provided, unlike the conventional example, it is not necessary to reduce the clearance between the ball valve and the valve cylinder on which this valve slides, and the low-pressure side that becomes the valve opening drive force of the high-pressure valve. The pressure in the port can be reduced reliably and 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.

In addition, the peripheral flange prevents excessive tilting when the compressor is started and enables smooth operation, and when the compressor is stopped, the gas vent passage quickly equalizes the pressure when moving the valve, shortening the closing time. At the same time, there is an effect that processing is easy at the time of molding the valve.

[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.
Sectional view taken along line III ', FIG. 4 is sectional view taken along line IV-IV' of FIG. 3, FIG. 5 is a perspective view of essential parts of the cylinder plate, FIG. 6 is a perspective view of a high pressure valve, and FIG. FIG. 3 is a sectional view of the rotary compressor of FIG. 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, 77a…
… Double sided seal part, 77b …… peripheral flange part, 77c …… gas vent passage.

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 compressor having a cup-shaped high-pressure valve capable of closing the low-pressure side port at the other end surface, the high-pressure valve having sealing surfaces on both sides and a peripheral flange having a notch-shaped gas vent passage.