JPS62199994A - Rotary compressor - Google Patents

Abstract

PURPOSE:To operate smoothly a high pressure valve by providing the high pressure side inlet port opening to a high pressure valve section for closing the high pressure side refrigerant path in stoppage to make gas flow jet toward the generally central portion of said valve. CONSTITUTION:A disk-like high pressure valve 77 for closing the low pressure side port 76 with one end face and interrupting communication between the high pressure side inlet and outlet ports 72, 74 with the other end face to close the high pressure side refrigerant path in stoppage is disposed in a valve cylinder 75 formed in a cylinder plate 57. And the high pressure side inlet port 72 is formed inclined from the outside in a side plate 55 to jet gas toward the generally central portion of the high pressure valve 77. By such constitution, gas flow jetted from the high pressure side inlet port 72 in start collides with the generally central portion of high pressure valve 77 to prevent said valve 77 from excessive inclination so that said valve 77 can be smoothly operated.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a rotary compressor used in refrigeration equipment such as refrigerators and showcases.

[Conventional technology] In a system that cools the inside of a refrigerator by cycling a compressor, when the system is stopped, high-temperature refrigerant existing on the high-pressure side of the system flows into the low-pressure cooler, creating a heat load, which reduces the power consumption of the system. Expenses increase. In order to prevent this phenomenon, a technique has been proposed in which the refrigerant passages on the low-pressure side and the high-pressure side are closed in the compressor when the compressor is stopped.

The conventional compressor mentioned above will be explained 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 6 is slidably disposed on an eccentric portion 4a of the cylinder plate. 6 is a vane that partitions the inside of the compression chamber γ into high and low pressure chambers.

Reference numeral 8 denotes a suction valve that functions as a check valve, and closes a suction port that communicates with a suction pipe (not shown). Also, 9 is a discharge valve,
The refrigerant gas compressed within the compression chamber γ passes through the discharge valve 9 and is discharged into the closed container 2 .

10 is a high-pressure valve that opens when the rotary compressor 1 is in operation and closes when it stops. This high pressure valve 10 is
It is provided with a high-pressure side outlet port 12 communicating with a discharge pipe 11 penetrating the closed container 2, and a high-pressure side inlet port 13 constantly communicating with the inside of the closed container 2. In addition, the suction path 1 is connected to the pressure impulse pipe 14.
A low pressure side port 16 communicating with 5 is provided. 17 is a ball valve that alternately opens and closes the high pressure side outlet port 12 and the low pressure side port 16. 18 is a bias spring that always biases the ball valve 17 toward the high pressure side outlet port 12.

In this configuration, when the compressor 1 is stopped, the pressure inside the impulse pipe 14 and the pressure inside the closed container 2 are balanced, and the force of the bias spring 18, the pressure inside the closed container 2, and the cooling system side pressure are balanced. The force caused by the difference causes the ball valve 17 to close the high pressure side outlet port 12. Therefore, the high pressure and high temperature gas filling the space of the closed container 2 is
There is no leakage to the cooling system via the discharge pipe 11.

At this time, the suction valve 8, which operates as a check valve, is also closed.
Outflow to the cooling system via the suction pipe (not shown) is also prevented.

Next, the startup time will be explained. Upon activation, the pressure in the low pressure chamber in the compression chamber Y decreases, which lowers the pressure in the suction passage 16 and the pressure guide pipe 14, creating 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 attached to the bias spring 18.
is pulled against the force, the high-pressure side outlet port 12 is opened, and the ball valve 17 is suction-sealed to the low-pressure side port 16.
This is normal operation.

Problems to be Solved by the Invention However, in the above configuration, due to the existence of a clearance between the ball valve 17 and the valve cylinder 19 in which the ball valve 17 slides, the ball valve 17 is pulled out from the high pressure side outlet port. It is difficult to avoid pressure drop in the low-pressure side port, which is the opening force of the valve, and it is necessary to minimize the clearance. However, this not only increases processing costs such as machining accuracy and matching assembly, but also increases operational In the worst case, foreign matter such as abrasion powder generated from the rotating sliding part inside the ball valve 17 may enter the clearance, causing a phenomenon similar to the hydraulic lock phenomenon seen in general spool valves. 17 may become inoperable. Furthermore, in order to avoid a reduction in clearance, it is conceivable to increase the effective pressure receiving area of the ball valve 17, but this not only increases the installation space of the high pressure valve 10, but also increases the weight and causes shock during operation. There are also problems such as noise generation. Furthermore, in the illustrated conventional example, a soft metal such as brass, which can be easily formed into a three-dimensional curved surface, is used for the port of the ball valve 17, which increases the number of parts and the number of assembly steps. Furthermore, the same applies to the impulse pipe 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 required pressure difference at startup without reducing the clearance or increasing the effective pressure-receiving area of the valve, and also reduces the installation space and the number of parts. This not only reduces manufacturing costs, but also increases the allowable dimensions of the sealing surface caused by dimensional variations during assembly, making it easier to assemble.

The purpose is to reduce unnecessary behavior of the high-pressure valve (for example, delay in seating to the low-pressure side port due to obliqueness) due to sudden gas flow pressure at the time of starting the compressor.

Means for Solving the Problems In order to solve the above problems, the 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 connected to a crankshaft. a side plate having a bearing portion that pivotally supports the rotor, a cylinder plate that rotatably houses the rotor, and a compression chamber formed by overlapping the side plate and the cylinder plate,
a vane that partitions the compression chamber into a low-pressure chamber and a high-pressure chamber; a suction valve and a discharge valve that communicate with the low-pressure chamber and the high-pressure chamber, respectively, and function as check valves and are disposed in close proximity to the vane; The high-pressure side inlet port and the low-pressure port are provided with a high-pressure side inlet port that constantly communicates with the inside of 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 a disk-shaped high pressure valve that can simultaneously close the low pressure side port on one side and close the low pressure side port on the other end, and the inlet port is inclined from the outside toward approximately the center of the high pressure valve. With the above-described structure, the high-pressure inlet port and the outlet port are closed simultaneously at startup, so the pressure drop in the low-pressure side port is extremely steep. It can be realized,
Therefore, it is possible to open the high-pressure valve that is strongly adsorbed to the high-pressure outlet port using the force generated by the difference between the pressure inside the 7 stem, which decreases when stopped, and the pressure inside the closed container, which is maintained at a nearly high pressure state. Even if the gas flow flows into the low-pressure side port from the high-pressure side inlet after this initial separation, an inclination due to extreme gas flow pressure is unlikely to occur, and the low-pressure side port is quickly closed. Immediately after stopping, the pressure inside the cylinder quickly balances with the pressure inside the closed container through, for example, the clearance between the vane and the cylinder. on the other hand,
Because it is a low-pressure side port, the volume can be set to a minimum, so the pressure in the low-pressure side port and the closed container can be balanced in a short time.Therefore, the separation from the low-pressure side port can be done in a short time, and the bias spring force can be reduced. by high pressure side inlet.

Rapidly close the exit port.

EXAMPLE An example of the present invention will be described below with reference to the drawings.

In Figure 1, 6o is a rotary compressor, 51
52 is an electric element consisting of a rotor 62a and a stator 52b, and 53 is a compression element. 54 is rotor 5
The side plate 65.2a is press-fitted into the crankshaft and fixed to the side plate 65.2a.
It is rotatably supported by bearing parts 55a and 56a formed at 56. Reference numeral 57 denotes a cylinder plate, on which the rotor 58 attached to the eccentric portion 64a of the crankshaft 64 is rotatably attached. 59 is a vane that partitions the compression chamber 6o, which is fixed by the outer circumference of the rotor 68, the inner circumference of the cylinder 59, and the side plates 55 and 56, into a low pressure chamber 61 and a high pressure chamber 62;
69a is a vane groove. 63 is the side plate 55,
56, a bolt for overlapping and fixing the cylinder plate 57; Reference numeral 64 denotes a suction pipe that guides refrigerant gas from the evaporator 66 to the compression chamber 6o, and is press-fitted into the press-fit bore 66 of the side plate 55. The end surface of the end plate of the press-fit bore 66 on the cylinder plate 67 side constitutes a valve seat surface of the disk-shaped suction valve 66. The vane 5 is connected to this press-fit bore 65.
In the suction passage 67 which is close to the cylinder 9 and communicates with the cylinder 69,
The suction valve 66 is housed, as well as a bias spring 68 that always keeps the valve 66 closed with a weak force. Further, 69 is a stepped portion that restricts the movement of the suction valve 66 when it is opened. Reference numeral 7o designates a discharge valve that discharges the compressed refrigerant gas from the compression chamber 6o into the closed container 51 directly or via a precooler pipe (not shown) (FIG. 2).

Reference numeral 71 denotes a high-pressure valve device, which is arranged at approximately the same height as the crankshaft 64. This high-pressure valve 71 includes a high-pressure side inlet port 72 extending in the axial direction of the crankshaft 64 on the side plate 55, and a discharge pipe 7 passing through the closed container 61.
3. The discharge pipe 73 is press-fitted into the press-fit hole 73&. This entrance,
As is clear from FIGS. 3 and 4, the outlet ports 72 and 74 are formed so that the inlet port 72 is diagonally opened from the outside toward the approximate center of the high-pressure valve 71.

In addition, each port 72°7 is located in the normal direction of the side plate 57.
4 are arranged in parallel, and an outlet port 74 is arranged on the inside and an inlet port 72 is arranged on the outside. However, 0 in the figure represents the center of the crankshaft. Further, the cylinder plate 67 is provided with a common valve cylinder 75 formed correspondingly to each of the adjacent ports 72, 74, and a low pressure side port 76 is formed at the bottom of this valve cylinder 75. 7
7 is a disk-shaped high-pressure valve, and the negative side is connected to the inlet and outlet ports 72. 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. 79 is a low pressure chamber 61 of the cylinder 59 from the low pressure side port 76 and the opening arrow a on one side plate 66 side.
The opening A is a pressure guiding path that directly communicates with the Aro, and the opening A is closed by the side plate 56.

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

FIG. 1 shows the stopped state, in which the low pressure valve 66 that acts 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 and downstream of the high pressure side outlet port 74, that is, the evaporator 6
It is closed by the force due to the pressure difference between the condensation saturation pressure at the temperature of the cooling chamber 51 and the saturation pressure at the temperature of the closed container 51 and a slight force of the bias spring 78.

Therefore, the high-temperature, high-pressure gas in the closed container 51 is prevented from flowing to the condenser 8o and the evaporator 66, and the heat load entering the evaporator 65 is reduced.

Next, the startup time will be explained.

The crankshaft 54 rotates due to the energization of the electric element 52, causing a pressure drop in the low pressure chamber 61 of the compression chamber 60. This pressure reduction is reliably achieved in a very short time even in a relatively rough clearance between the high pressure valve 77 and the valve cylinder 76 (for example, about 0.111) because the high pressure side inlet port 72 is closed. This pressure drop naturally
, the pressure in the low-pressure side port 76 and the valve cylinder 76 decreases, and the pressure difference between the high-pressure side inlet port 72, that is, the pressure inside the closed container 51 and the pressure inside the valve cylinder 75, acts on the high-pressure valve 77, and the high-pressure side volume is strongly reduced. Pull out the high pressure valve 77 adsorbed on the side. After this initial pull-off operation of the high-pressure valve 77, the dynamic pressure of the gas flow flowing toward the approximate center of the high-pressure valve 77 is also taken into account, and the high-pressure valve 77 resists the force of the bias spring 78 and closes the low-pressure side port 76. Close and complete the valve opening operation. On the other hand, the suction valve 66 is also opened, and normal cooling operation is performed.

Next, the operation when stopped will be explained.

When the crankshaft 54 stops rotating, the gas flow in the suction pipe 64 is stopped, and the suction valve 66 is closed.

Further, the oil seal that divides the inside of the cylinder 60 into a high pressure chamber 63 and a low pressure chamber 61 is broken, and the high pressure gas inside the closed container 61 increases the pressure inside the low pressure chamber 61 due to, for example, the clearance between the vane 59 and the vane groove 59a.

This pressure increasing effect extends to the low pressure side port 76 through the pressure guiding path 79, and since the volume of the pressure guiding path 79 can be formed small, the pressure increasing time can be shortened. When the pressure inside the low-pressure side port 76 and the pressure inside the closed container 51 are equalized, the high-pressure valve 77 leaves the low-pressure side port 76 due to the force of the bias spring 78, closing the high-pressure side inlet port 72 and the high-pressure side outlet port 74 at the same time. do.

Therefore, when the compressor is stopped, the high pressure and high temperature gas in the closed container 61 is prevented from flowing out to the condenser 80 and the evaporator 65. Further, as is clear from FIG. 4, the inclined inlet port 72 can reduce the uneven wall thickness of the discharge pipe 73 when it is press-fitted, and the sealing performance due to press-fitting can be improved.

Effects of the Invention As described above, the present invention has a high-pressure side inlet port that is always in communication with the inside of the closed container, a high-pressure side outlet port that is always in communication with the discharge pipe, and a pressure passage that directly communicates with the low-pressure chamber of the compression chamber. a disk-shaped high-pressure valve capable of simultaneously closing the high-pressure side inlet port and the low-pressure port on one side and closing the low-pressure side port on the other end side; Since the valve is formed so as to be inclined from the outside toward the center of the valve, there is no need to reduce the clearance between the ball valve and the valve cylinder on which this valve slides, unlike in conventional examples, and the opening drive of the high-pressure valve is improved. The pressure of the low-pressure side port, which is the main source of power, can be reduced reliably and in an extremely short time. Therefore, not only can a stable valve opening operation be obtained, but also the machining accuracy and assembly accuracy can be relaxed, and productivity can be improved. Furthermore, there is no possibility of valve locking due to foreign matter. Further, the effective area of the valve is not increased, the valve can be constructed compactly, and there is no increase in operating noise.

On the other hand, in the case of valve operation, a pressure path is formed that directly communicates with the low pressure chamber of the compression chamber, so parts such as a pressure pipe are not only unnecessary, but also the volume of the pressure path is reduced, and the low pressure side after stopping. The time required to increase the pressure inside the port can be shortened, and the time required to close the high-pressure side outlet port can be shortened.

In addition, because the high-pressure side inlet port is arranged at an angle as described above, the gas flow from the inlet port to the low-pressure port during startup collides with the center of the high-pressure valve, which prevents the high-pressure valve from tilting excessively. This makes it easier to sit down.

[Brief explanation of drawings]

Figure 1 is a sectional view of a rotary compressor showing an embodiment of the present invention, Figures 2 and 3 are the n/ line and m-m in Figure 1.
4 is a sectional view taken along the third line IV-IV', FIG. 6 is a perspective view of a main part of a cylinder plate, and FIG. 6 is a sectional view of a conventional rotary compressor. 61...Airtight container, 63.River...Compression element, 6
2... Electric element, 54 Old... Crankshaft, 5
5.56...Sight Freight, 57...
・Cylinder plate, 60...Compression chamber, 61・
River: low pressure chamber, 62 River: high pressure chamber, 59: old vane, 66: suction valve, 70 tap: discharge valve, 72
...High pressure side inlet port, 74...High pressure side outlet port, 73...Discharge pipe, 76...
Pressure path, 77... High pressure valve.

Claims (1)

[Claims] The compressor includes a closed container, a compression element and an electric element housed in the closed container, and the compression element includes a side plate having a bearing portion that pivotally supports a crankshaft, and a cylinder plate that rotatably houses a rotor. , a compression chamber is formed by overlapping the side plate and the cylinder plate, and a vane partitions the compression chamber, a low pressure chamber, and a high pressure chamber, and a vane that communicates with the low pressure chamber and the high pressure chamber, and is adjacent to the vane. A suction valve and a discharge valve that function as check valves are arranged in the airtight container, a high-pressure side inlet port that constantly communicates with the airtight container, a high-pressure side outlet port that constantly communicates with the discharge pipe, and A disc-shaped high-pressure valve is provided with a low-pressure side port that directly communicates with a low-pressure chamber of the chamber, and is capable of simultaneously closing the high-pressure side inlet port and the outlet port on one side and closing the low-pressure side port on the other end side. The rotary compressor further comprises: the high-pressure side inlet port being formed on the side plate so as to be inclined from the outside toward substantially the center of the high-pressure valve.