JPH066954B2 - 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 refrigerant passage on the low pressure side and the high pressure side is 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 is
It 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, 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 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. In addition to reducing the manufacturing cost, the permissible size of the sealing surface caused by the dimensional variation at the time of assembling is enlarged to facilitate the assembling and to improve the workability.

Means for Solving the Problems In order to solve the above problems, a rotary compressor of the present invention includes a closed container and a compression element motor housed in the closed container, and the compression element includes a crankshaft. First and second side plates having bearing portions that support the shaft, a cylinder plate that rotatably accommodates the rotor, and the first and second side plates 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 a suction valve and a discharge valve that communicate with the low pressure chamber and the high pressure chamber, respectively, and that are arranged close to the vane and that perform a check valve action, A high pressure side inlet port which is always in communication with the closed container formed in the first side plate, 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. A high pressure valve in the form of a disk is provided, which is capable of simultaneously closing the high pressure side inlet port and the inlet port on one side surface and closing the low pressure side port on the other end surface, and also has a pressure guiding path at the second side.
A groove is formed in one of the side plate and the cylinder plate.

Operation According to the present invention, since the high-pressure inlet port and the outlet port are simultaneously closed at the time of start-up by the above-mentioned configuration, the pressure drop of the low-pressure side port can be realized extremely rapidly,
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. Further, since the pressure guiding path is formed on the overlapping surface of the first side plate and the cylinder plate, the workability is good.

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, 53 is a compression element, and 54 is the rotor 5
A crankshaft press-fitted and fixed to 2a is rotatably supported by bearings 55a and 56a formed on the first and second side plates 55 and 56. 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, 56 into a low pressure chamber 61 and a high pressure chamber 62, and 59a is a vane groove. Reference numeral 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 bolt hole 63
a and a clearance C are provided for assembling, so that 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 forms a valve seat surface of a disc-shaped intake valve 66. The suction valve 67 is connected to the suction passage 67 which is connected to the press-fitting bore 65 and communicates with the vane 59.
6 is stored, and a bias spring 68 for keeping the valve 66 closed by a weak force is also stored. Further, 69 is a stepped portion that restricts the movement of the intake valve 66 when opened. Reference numeral 70 denotes a discharge valve for discharging the compressed refrigerant gas in the compression chamber 60 directly or via a bricooler 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. The inlet and outlet ports 72 and 74 are arranged in parallel in the normal direction of the side plate 57, as is clear from FIGS. 3 and 4.
The outlet port 74 is arranged inside and the inlet port 72 is arranged outside. However, O in the figure represents the center of the crankshaft. Further, the cylinder plate 57 is provided with the ports 7 adjacent to each other.
A common valve cylinder 75 formed corresponding to 2, 74 is provided, and a low pressure side port 76 is formed at the bottom of this 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. Reference numeral 78 is a bias spring that always biases the high pressure side inlet and outlet ports 72 and 74 to be closed. 79 is an opening 76 on the low pressure side port 76 and the second side plate 56 side.
It is a pressure guiding path directly communicating with the low pressure chamber 61 of the cylinder 59 from a, and a channel is machined or processed with a sintered alloy on the end surface of the second side plate 56.
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, the low pressure valve 66 acting as a check valve is closed, and the high pressure valve 77 closes both the high pressure side inlet port 72 and the high pressure side outlet port 74 at the same time. 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 the 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 pressurizes the low-pressure chamber 61 by the clearance between the vane 59 and the vane groove 59a, for example. 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 76
When the internal pressure and the internal pressure of the sealed container 51 are equalized, the high pressure valve 77 causes the low pressure side port 76 by the force of the bias spring 78.
The high pressure side inlet port 72 and the high pressure side outlet port 74 are simultaneously closed.

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, a groove may be formed in the pressure guiding path 79 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 stopping Shorten the time to increase the pressure in the port,
The time required to close the high pressure side exit port can be shortened.

Further, since the pressure guiding path is formed by forming the groove portion on one of the second side plate or the cylinder plate, it can be easily machined, sintered alloy or the like.

[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 ... 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, 76 ... Pressure guiding path, 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 includes 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 at the same time on one side A rotary compressor having a disk-shaped high-pressure valve that is closed and can close the low-pressure side port at the other end surface, and the pressure guide path is formed by forming a groove portion on one of the second side plate and the cylinder plate. .