JPH063194B2 - 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 disposed 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 denotes a high pressure valve that is opened when the rotary compressor 1 is in operation and closed when it is stopped. This high pressure valve 10
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 are provided. In addition, the suction passage 1 is connected to the pressure guiding pipe 14.
5 is provided with a low-pressure side port 16. A ball valve 17 alternately opens and closes the high pressure side outlet port 12 and the low pressure side port 16. A bias spring 18 always 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. The ball valve 17 closes the high pressure side outlet port 12 by the force generated by Therefore, the high-pressure high-temperature gas filling the space of the closed container 2 does not flow out to the cooling system via the discharge pipe 11.
At this time, the suction valve 8 that operates as a check valve is also closed,
It is also prevented from flowing out to the cooling system via an intake pipe (not shown).

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 pressures in the suction passage 15 and the pressure guiding pipe 14 decrease, 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 attached to the side outlet port 12 is attached to the bias spring 18
The high pressure side outlet port 12 is opened, the ball valve 17 is adsorbed and sealed to the low pressure side port 16,
It is a normal operation.

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. The pressure of the low pressure side port, which is the valve opening force, is difficult to reduce and it is necessary to keep the clearance to a minimum, but this not only increases the processing cost of processing accuracy, matching assembly, etc. In the worst case, foreign matter such as abrasion powder generated from the rotating and sliding parts inside the clearance enters the clearance, and in the worst case, the ball valve 17 also has a phenomenon similar to the hydraulic lock phenomenon found in general spool valves. 17 may cause inoperability. In order to avoid the decrease in clearance,
It is conceivable to increase the effective pressure receiving area of the ball valve 17, but this not only increases the space for incorporating the high pressure valve 10, but also causes a problem such as the generation of impact noise during operation due to the increase in weight. 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. In addition, the cost of the pressure guiding pipe 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 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 dimension of the seal surface caused by dimensional variations during assembly, making it easier to assemble and
The purpose is to reduce the flow resistance by increasing the port diameter in a limited space.

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 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 the high-pressure side inlet port, A low pressure port is simultaneously closed on one side surface, and a disk-shaped high pressure valve capable of closing the low pressure side port on the other end surface is provided, and the high pressure side outlet,
The inlet ports are arranged side by side in a substantially normal direction and formed on the side plate.

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. After the initial separation, the low pressure side port is closed immediately. 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. 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. Further, since the port diameter can be increased, the loss can be reduced.

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 an airtight container, 52 is an electric element including a rotor 52a and a stator 52b, and 53 is a compression element. 54 is the rotor 5
The side plate 55 by the crank shaft press-fitted and fixed to 2a,
The bearings 55a and 56a formed on the shaft 56 are rotatably supported. Reference numeral 57 denotes 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 a compression chamber 60 defined by the outer periphery of the rotor 58, the inner periphery of the cylinder 59, and the side plates 55 and 56 into a low pressure chamber 61 and a high pressure chamber 62.
59a is a vane groove. 63 is a side plate 55,
56 is a bolt for superimposing and fixing the cylinder plate 57. The bolt 63 has a clearance C for assembling with the bolt hole 63a, so that the side plate 55 can be moved in the circumferential direction, though slightly. Reference numeral 64 denotes a suction pipe that guides the refrigerant gas from the evaporator 65 to the compression chamber 60, which is press-fitted and fixed to the press-fitting bore 65 of the side plate 55. An end plate end surface of the press-fitting bore 65 on the cylinder plate 57 side forms a valve seat surface of a disc-shaped intake valve 66. The suction valve 66 is accommodated in a suction passage 67 which is connected to the press-fitting bore 65 and is close to the vane 59 and communicates with the cylinder 59.
A bias spring 68 for keeping the closed state is stored.
Reference numeral 69 is a step portion that regulates 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. The high-pressure valve 71 includes a high-pressure side inlet port 72 extending in the axial direction of the crankshaft 54 on the side plate 55, and a high-pressure side outlet port 74 communicating with a discharge pipe 73 penetrating the hermetic container 51. 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, O in the figure represents the center of the crankshaft. 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. Reference numeral 77 is a disc-shaped high pressure valve, which has the inlet and outlet ports 7 on one side.
2, 74 can be closed, and the low pressure side port 76 can be closed on the other side. 78 is always the high pressure side inlet and outlet port 7
It is a bias spring that urges 2, 74 to be closed. 79 is the low pressure side port 76 and one side plate 5
The opening 76a is a pressure guiding path that directly communicates with the low pressure chamber 61 of the cylinder 59.
Closed by 6.

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 controls the pressure difference between the upstream side and the downstream side of the high pressure side outlet port 74, that is, the evaporator 6
5 is closed by the force due to the pressure difference between the condensing saturation pressure at the temperature of the cooling chamber in which 5 is arranged and the saturation pressure at the temperature of the closed container 51 and a slight bias spring 78 force.

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 is rotated by energization of the electric element 52, and the pressure in the low pressure chamber 61 of the compression chamber 60 is reduced. This pressure decrease is surely 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 pressure in the low pressure side port 76 and 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 side is strongly pushed. The high pressure valve 77 adsorbed 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, completing the valve opening operation. On the other hand, intake valve 66
Is also opened and 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. Also cylinder 6
The oil seal that divides the inside of 0 into the high pressure chamber 63 and the low pressure chamber 61 is broken, and the high pressure gas in the closed container 51 is discharged from the low pressure chamber 61 due to the clearance between the vane 59 and the vane groove 59a.
Boost inside. 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. Low pressure side port 7
When the pressure in 6 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.

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 sunpressor is stopped.

Further, the high pressure side inlet port 72 and the high pressure side outlet port 74
Are arranged side by side in the normal direction, the side plate 57
Even if the radial movement occurs at the time of assembling, the change amount of the lap margin with the valve 77 can be significantly reduced as compared with the case where the inlet and outlet ports 72 and 74 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. Since it is provided with a side port, the high pressure side inlet port and the low pressure port are simultaneously closed on one side surface, and a disk-shaped high pressure valve capable of closing the low pressure side port on the other end surface is provided.
As in the conventional example, there is no need to reduce the clearance between the ball valve and the valve cylinder on which this valve slides, and the pressure drop at the low pressure side port, which is the opening driving force for the high pressure valve, can be reliably performed in an extremely short time. I can do it. 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.

Also, since the arrangement of the high pressure side inlet and outlet ports is arranged in a substantially normal direction, there is little change in the lap margin of the port and valve due to the variation in the circumferential direction that occurs when the side plate is assembled. Never improve. Furthermore, since it is not necessary to set the amount of change in the lap allowance excessively, there is an effect that a high pressure side valve with a low pressure loss can be configured in a limited space.

[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 'and III lines in FIG.
-III 'sectional view, FIG. 4 shows IV-IV' of FIG.
5 is a sectional view of the cylinder plate, and FIG. 6 is a sectional view of a conventional rotary compressor. 51 ... airtight 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 ...
Intake 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 high-pressure side inlet port that communicates with each of the low-pressure chamber and the high-pressure chamber and that includes a suction valve and a discharge valve that are arranged close to the vane and that perform a check valve action; A high pressure side outlet port which is always in communication with the discharge pipe, and a low pressure side port which is in direct communication with the low pressure chamber of the compression chamber through a pressure guiding path, and the high pressure side inlet port and the low pressure port are simultaneously provided on one side surface. It is provided with a disk-shaped high-pressure valve that is closed and can close the low-pressure side port at the other end surface, and the high-pressure side inlet port and the high-pressure side outlet port are arranged side by side in a substantially normal direction to form the side plate. Rotary compressor.