KR20000017022A - Rotary compressor, refrigerating cycle using the compressor, and refrigerator using the compressor - Google Patents

Abstract

PURPOSE: A rotary compressor integrated with a blade is provided to secure the high reliability and the high efficiency without increasing sliding loss of a blade by preventing sludge from accumulating on a circuit. CONSTITUTION: The rotary compressor installs:a cylinder(5) having an inlet(3) and a vent outlet(14) in a cylinder chamber(4); a piston(15a) revolving in the cylinder chamber; a blade(15b) integrally placed on the piston to partition the inside of the cylinder chamber into a high pressure chamber(10) and a low pressure chamber(9); a compressing instrument unit having a driving shaft which revolves the piston; a closed container(13) accepting an electromotor unit which revolves the driving shaft; and a closed cabin accepting the compressing instrument unit and the electromotor unit.

Description

ROTARY COMPRESSOR, REFRIGERATING CYCLE USING THE COMPRESSOR, AND REFRIGERATOR USING THE COMPRESSOR}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor having a piston integrally provided with a blade and a refrigeration cycle such as a refrigerating device or an air conditioner using the compressor, and further to a refrigerator using the compressor.

5 and 6 are conventional rolling piston rotary compressors (in this example, two cylinder rotary compressors) disclosed in, for example, Japanese Patent No. 2502756, FIG. 5 is a longitudinal sectional view and a refrigeration cycle, and FIG. Cross section of the compression mechanism. A description with reference to FIGS. 5 and 6 is as follows. Conventional rotary compressors are driven by an electric motor unit 50 consisting of a stator 1 and a rotor 2 and the electric motor unit 50, and the frame 19, the suction port 3 and the discharge port (not shown) A cylinder 5 having an open cylinder chamber 4, a partition plate 34 which partitions between two cylinders, a cylinder head 20, and an eccentric shaft portion 7 of the drive shaft 6 are fitted freely and rotated. A vane 11 partitioning the piston 8 disposed in the cylinder 5 and the cylinder chamber 4 into a low pressure chamber 9 communicating with the suction port 3 and a high pressure chamber 10 communicating with a discharge port (not shown). And the compression mechanism part 60 which consists of the vane spring 12 and the drive shaft 6 for pressing (pressing) to the piston side so that the vane 11 may not move away from the piston 8. These electric motor parts 50 and the compression mechanism part 60 are directly attached in the airtight container 13 of a discharge pressure atmosphere or a suction pressure atmosphere by means of welding, shrink fitting, or the like. 5 is a discharge pressure atmosphere. In addition, the operation of the piston 8 revolves along the inner wall of the cylinder chamber 4 by the rotation of the drive shaft 6, and compresses a compressive fluid such as refrigerant gas sucked in the suction port 3 according to this revolving. It is made to discharge from a discharge port (not shown).

7 and 8 are longitudinal cross-sectional views and a cross-sectional view of a compression mechanism of the conventional blade-integrated piston compressor as described in, for example, Japanese Patent Application Laid-Open No. Hei 10-047278. 7, FIG. 8 is comprised by the electric motor part 50 which consists of the stator 1 and the rotor 2, and the compression mechanism part 60 driven by this electric motor part 50. As shown in FIG. These electric motor parts 50 and the compression mechanism part 60 are accommodated in the airtight container 13.

The compression mechanism (60) comprises a cylinder (5) having a cylinder chamber (4) with a frame (19), an inlet (3) and an outlet (14) open, a cylinder head (20), and an eccentric shaft (7) of a drive shaft (6). Piston 15a, which is freely fitted in the cylinder 5 and disposed in the cylinder 5, integrally provided in the piston 15a, and the low pressure chamber 9 and the discharge port, which communicate the cylinder chamber 4 with the suction port 3; Guide (guide) freely inserted into the blade (15b) partitioned by the high-pressure chamber (10) communicating with the (14), the cylindrical hole portion 16 formed in the cylinder (5) to support the blade (15b) slide and swing freely. Member) 17 and drive shaft 6.

By rotation of the drive shaft 6, the piston 15a revolves along the inner wall of the cylinder chamber 4 so as to oscillate with the rotational center position 18 of the guide 17 as the point via the blade 15b. Compressive fluids, such as refrigerant gas, sucked in the suction port 3 at each revolution, are compressed and discharged from the discharge port 14.

In addition, in Fig. 373 on page B5-159 of the "Mechanical Engineering Handbook" (published on April 15, 62, Japan) and its description, the piston and the blade are integrated and the piston swings inside the cylinder. A structure similar to that of the eccentric rotating blade integrated piston type rotary compressor is described.

In addition, in the conventional rotary compressor of the blade-integrated piston type, the electric motor unit 50 and the compression mechanism unit 60 are fixed in the airtight container 13 by means of shrinkage fitting, welding, or the like. Inside it was a discharge pressure atmosphere.

In the conventional rolling piston rotary compressor, as described above, the compression mechanism consists of a cylinder 5, a piston 8, a vane 11, a vane spring 12, and the space in the cylinder is defined by a piston 8, Since the vane 11 is partitioned into the low pressure chamber 9 communicating with the inlet port 3 and the high pressure chamber 10 communicating with the discharge port 14, the vane 11 tip and the outer peripheral surface of the piston 8 are always applied to a suitable force. It is necessary to make contact. When the inside of the sealed container 13 is a discharge pressure atmosphere, the force caused by the differential pressure in the compression chambers 9 and 10 and the sealed container 13 presses (presses) the vane 11 against the piston 8. Since the vane 11 can be pressed against the piston 8 using this differential pressure, the pressing force by the vane spring 12 may be set small in consideration of the degree to which the differential pressure can be used. . In this case, since the inside of the compressor is in a pressure balanced state immediately before starting, and the vane 11 is pressed against the piston 8 with a force smaller than the pressing force required during normal operation, the piston 8 is excessive. The load is not applied, and stable starting can be performed by the motor having the minimum starting torque required.

On the other hand, since the suction pressure in the sealed container 13 is a part of the low pressure chamber 9 in the suction pipes 24 to 3, the cylinder 5, and the other part is filled with the discharge pressure atmosphere, During the stop when the ON / OFF operation is performed, such as for a refrigerator, the high temperature and high pressure gas refrigerant in the sealed container 13 is stored in the cylinder 5, the frame 19, the cylinder 5, and the cylinder head 20. Gas leaked from the contact surfaces 21, 23, and 35 between the cylinder 5 and the partition plate 34 to the low pressure chamber 9 through the suction pipe 24 due to a pressure difference. Since the backflow from the suction pipe 24 to the evaporator 36 and the cooler such as a refrigerator tend to cause a temperature rise, a check valve or the like is not provided in a circuit between the suction pipe 24 and the evaporator 36 to prevent this. There was a problem that the cost must be raised.

On the other hand, in the case where the inside of the sealed container is configured to be the suction pressure atmosphere, the discharge pressure in the sealed container is the portion of the high pressure chamber, the discharge port, the discharge pipe, and the other part is filled with the suction pressure atmosphere. Since the discharge valve provided on the discharge side serves as a check valve, the gas of high temperature and high pressure is separated and separated, so that no leakage to the suction pressure portion occurs during the stop of ON / OFF operation, and the gas does not need to be provided with a check valve in the circuit. Does not flow back to the evaporator.

In the rotary compressor, when the inside of the hermetic container 13 is a suction pressure atmosphere, the vane 11 has a force due to the pressure difference between the compression chamber and the hermetic container 13 to separate the vane 11 from the piston 8. Since the pressure of the vane spring 12 which presses the vane 11 against the piston 8 needs to be set as large as the maximum differential pressure in the assumed operating range, the inside of the sealed container 13 The vane spring 12 which has a larger pressing force than the discharge pressure atmosphere should be used. In the pressure balance state just before starting, since the pressing force of the vane spring 12 does not cancel by the differential pressure, the vane 11 is pressed against the piston 8 with a force greater than the pressing force necessary during normal operation. Therefore, a motor with a large starting torque was required in order to start the excess load by acting on the piston 8.

Designing the motor to increase the starting torque at the expense of motor efficiency in normal operation has led to a decrease in compressor performance. Also, since the pressing force of the vane spring is set to the maximum value in the assumed operating range, the vane pressing cannot be performed according to the operating conditions (pressure difference between suction and discharge), and the pressing force is always strong. Sliding (sliding) of the situation is excessive. Strict sliding conditions cause sludge generation as well as wear of the vane tip. Since the inside of the sealed container has the configuration of the suction pressure atmosphere, the generated sludge is discharged from the discharge tube into the circuit without being trapped in the space in the sealed container, and accumulated in the circuit to close the capillary tube.

In addition, even if the pressure of the vane is reduced in the sealed container as the discharge pressure atmosphere, when HFC refrigerants such as R134a are used, the refrigerant does not contain chlorine atoms, so the extreme pressure effect obtained by the CFC refrigerants can be expected. As a result, the lubricity of the sliding portion is deteriorated, and the sliding situation of the vane tip and the outer peripheral surface of the piston becomes strict.

On the other hand, in the conventional rotary blade type piston compressor, since the inside of the hermetic container 13 is a discharge pressure atmosphere, and the blade portion 15b corresponding to the vane as described above is integrally formed with the piston 15a, The starting force is not applied to the piston 15a at the time of starting, and stable starting can always be performed without excessively increasing the starting torque of the motor, and there are no problems such as abrasion and sludge clogging due to sliding of the vane tip.

On the other hand, since the inside of the sealed container is configured to be the discharge pressure atmosphere, similarly to the rolling piston rotary compressor having the discharge pressure atmosphere, the gas refrigerant of the high temperature and high pressure in the sealed container 13 is stopped during the operation of the cylinder 5 and the frame. (19) In the compression chamber, the suction pipe (24), which becomes a lower pressure in the sealed container (13) of high pressure due to the pressure difference through the contact surfaces (21) and (23) of the cylinder (5) and the cylinder head (20). Back to the evaporator 36 side, and the temperature of a cooler such as a refrigerator rises, so that a check valve or the like must be provided in a circuit between the suction pipe 24 and the evaporator 36 in order to prevent this. there was.

In the case where the compression mechanism portion and the electric motor portion are elastically supported in the hermetic container and a gap is formed between the compression mechanism portion and the electric motor portion and the inner wall of the hermetic container, a space between the pipe and the compression mechanism portion attached to the hermetic container is provided. It is necessary to isolate and seal either the discharge side or the suction side from the atmosphere inside the sealed container. If the inside of the sealed container is discharge pressure atmosphere, the suction pipe is placed in the sealed container so as to maintain the suction pressure by sealing the inlet port of the suction pipe to the compression mechanism cylinder attached to the sealed container according to the discharge pressure in the sealed container. In the case where I is the suction pressure atmosphere, it is necessary to arrange the discharge pipe in the sealed container so as to maintain the discharge pressure by sealing the discharge pipe attached to the sealed container to a part of the discharge port of the cylinder of the compression mechanism part in accordance with the suction pressure in the sealed container. Pipes arranged in a sealed container should be designed so that the rigidity is low so as not to be deformed, fatigued or damaged by vibration of the compression mechanism and the motor part elastically supported in the sealed container. Since the suction tube portion through which the gas before compression flows has a larger volume flow rate and a higher flow rate than the discharge tube portion through which the gas flows through compression, the diameter of the tube cannot be reduced in view of pressure loss, so the arrangement of the suction tube is not a realistic choice. That is, if the motor portion is elastically supported in the hermetic container and the interior of the hermetic container is the discharge pressure atmosphere, the suction pipe disposed in the hermetic container has a problem in that the pressure loss is large to prevent deformation and damage.

Therefore, in the configuration in which the sealed container is discharge pressure atmosphere, since the motor unit 50 and the compression mechanism unit 60 are directly attached to the sealed container 13, the vibration and noise inside the compressor are directly transmitted to the outside, thereby necessarily low vibration. It wasn't low noise. Therefore, in order to reduce the vibration transmitted from the compressor to the piping system constituting a refrigeration cycle such as a refrigerator, and to prevent the pipe from being broken by deformation due to the vibration even when delivered, the diameter of the pipe to the compressor is increased. It is necessary to make the length of the movable part thin and long, and the efficiency decrease by the pressure loss, the cost increase by the complicated pipe | pipe, and the complexity of the piping design were brought about.

In addition, when the inside of the sealed container 13 is a discharge pressure atmosphere, the force by the differential pressure acting on the guide 17 concentrates on the narrow portion of the planar sliding portion between the guide 17 and the blade 15b. It also led to increased sliding loss and lower reliability.

Usually, the space 5a in which the vane (blade) moves is opened and equalized to the space in the sealed container 13 as shown in FIG. 9A, regardless of whether the vane (blade) is integral with the piston. As shown in FIG. 9B, when sealed, vanes (blades) enter and exit the enclosed space 5a, and the increase and decrease of the space volume due to the entry and exit of the vanes (blades) is lost, so that the inside of the sealed container 13 is discharged. Regardless of whether it is a pressure atmosphere or a suction pressure atmosphere, it is better to open it to the space in the sealed container 13.

In addition, when the two-cylinder structure is used as a single-piece blade, the volume increase and decrease of the two blade movement spaces 5a can be canceled, so that it is not possible to open it into the sealed container. However, in this case, there is a problem of causing instability in the guide behavior. there was. As shown in FIGS. 10A and 10B, the curvature of the cylindrical surface of the guide 17 and the curvature of the cylindrical hole portion 16 into which the guide is inserted are not the same, and the curvature difference is minute from the viewpoint of assemblability, sliding property, and the like. It is necessary to have. For this reason, the support point S which the guide 17 abuts on a cylindrical hole is determined by the balance of the force acting on the guide 17. When the blade movement space 5a is not opened into the sealed container, the pressure becomes a pressure Pm between the suction pressure Ps and the discharge pressure Pd due to leakage between the compression chambers 9 and 10. At this time, when the pressure Pc of the high-pressure chamber 10 is lower than Pm, the support point of the guide on the discharge side becomes a point close to the inner circumference of the cylinder as shown in FIG. 10A. As the compression progresses, the pressure Pc of the high-pressure chamber 10 rises to Pm. If higher, it becomes a point close to the blade movement space as shown in FIG. As described above, the support point between the state of FIG. 10A and the state of 10B, not the one point of support, causes instability, causing problems in sliding and reliability of the guide 17.

When the blade movement space 5a is opened into the sealed container 13, both the loss due to the increase and decrease of the blade movement space volume and the instability of the guide support point can be avoided. However, when the inside of the sealed container 13 is discharge pressure, it is shown in FIG. As described above, the pressure in the blade movement space 5a becomes the discharge pressure Pd, and the support points S and S 'of the guide 17 are both in the vicinity of the inner circumference of the cylinder, and the loads F ₃ and F ₃ ′ of the guide plane and the blade side are the inner circumference of the cylinder. Since it concentrates on the narrow part in the vicinity, it also led to the increase of sliding loss and the fall of reliability.

When the inside of the sealed container 13 is a discharge pressure atmosphere, when a flammable refrigerant such as a hydrocarbon refrigerant (HC refrigerant) is used, the space in the sealed container becomes a high pressure, so that the discharge pressure portion of the circuit volume during the operation is increased. Since the oil accumulated in the sealed container is exposed to the discharge pressure, the amount of refrigerant dissolved in the oil is increased and the amount of refrigerant contained in the circuit is increased, compared with the suction pressure atmosphere, so that it is safer in relation to ignition or explosion. It was not desirable from a viewpoint. From the viewpoint of reducing the amount of encapsulated refrigerant, it is preferable that the space volume in the sealed container is as small as possible. However, in the reciprocating compressor in which the sealed container is the suction pressure atmosphere, as shown in Fig. 12, the motor 1, ( 2) and the piston 15a and the cylinder 5 are arranged in only one direction with respect to the center of the drive shaft 6, so that an asymmetrical configuration has resulted in an increase in the space volume in the absence of the compression mechanism.

An object of the present invention is to solve the above problems of the prior art, it is possible to always carry out a more stable start without using the motor of the excessive starting torque, the gas refrigerant of high temperature and high pressure during the stop during the on / off operation Reverse flow to the side can be prevented without providing a check valve, etc. in the circuit, and noise can be reduced by preventing the internal vibration and noise from being directly transmitted to the outside without damaging or damaging the suction pipe. In addition, it is possible to use HFC refrigerants that do not lead to ozone depletion as a refrigerant, and further increase the safety against ignition and explosion even when using flammable refrigerants such as hydrocarbon refrigerants that do not adversely affect the global environment. The sludge of the blade is prevented by the occurrence of sludge caused by It is to provide a high reliability, high efficiency blade integrated piston type rotary compressor without increasing ding loss.

Another object of the present invention is to provide a refrigeration cycle utilizing the characteristics of the compressor using this compressor.

Still another object of the present invention is to provide a refrigerator utilizing this compressor utilizing the characteristics of the compressor.

1 is a longitudinal sectional view and a refrigerating cycle diagram of a rotary compressor according to the first embodiment of the present invention;

2 is a cross sectional view of a compression mechanism of a rotary compressor according to the first embodiment of the present invention;

3 is a schematic diagram showing the relationship between the force acting on the guide in the case of opening the blade movement space of the rotary compressor in the airtight container in the suction pressure atmosphere according to the first embodiment of the present invention;

Fig. 4A is a longitudinal sectional view of the blade integral piston type compressor of the second embodiment showing the elastic support member;

4B is a longitudinal sectional view and a refrigeration cycle diagram of the same compressor of the second embodiment showing a suction path and a discharge path;

5 is a longitudinal sectional view and a refrigeration cycle of a conventional rotary compressor,

6 is a cross-sectional view of a compression mechanism of the conventional rotary compressor,

7 is a longitudinal sectional view of a conventional rotary compressor integrated blade,

8 is a cross-sectional view of a compression mechanism of the conventional rotary compressor integrated blade;

9A is a perspective view from the cylinder head side in the case of opening the blade movement space into the closed container;

9B is a perspective view from the cylinder head side when the blade movement space is not opened into the sealed container;

10A and 10B are schematic diagrams showing the relationship between the forces acting on the guide when the blade movement space is not opened into the sealed container;

FIG. 11 is a schematic diagram showing the relationship between the forces acting on the guide when the blade movement space is opened into the sealed container in the discharge pressure atmosphere; FIG.

12 is a longitudinal sectional view of the reciprocating compressor;

The rotary compressor according to the first aspect of the present invention is a cylinder having an inlet and an outlet in a cylinder chamber, a piston eccentrically revolving in a cylinder, a blade integrally provided in the piston, and partitioning the cylinder into a high pressure chamber and a low pressure chamber, and In a rotary compressor including a compressor mechanism having a drive shaft for revolving the piston, an electric motor portion for rotating the drive shaft, and a sealed container for housing the piston, the inside of the sealed container for storing the compressor mechanism and the motor portion is a suction pressure atmosphere.

The rotary compressor according to the second aspect of the present invention, in the first aspect, maintains the compression mechanism portion and the motor portion by means of an elastic support member in the hermetic container, between the compression mechanism portion and the inner wall of the hermetic container, and the motor portion and the hermetic seal. A gap is provided between the inner walls of the container.

The rotary compressor according to the third aspect of the present invention uses the HFC refrigerant in the first aspect or the second aspect.

The rotary compressor according to the fourth aspect of the present invention, in the third aspect, encloses a lubricating oil having a small incompatibility or compatibility with the HFC refrigerant in the sealed container.

The rotary compressor according to the fifth aspect of the present invention uses the hydrocarbon refrigerant as the refrigerant used in the first aspect or the second aspect.

The rotary compressor according to the sixth aspect of the present invention, in the fifth aspect, encloses a lubricating oil having a small incompatibility or compatibility with a hydrocarbon-based refrigerant in a sealed container.

The rotary compressor according to the seventh aspect of the present invention encloses a lubricating oil having compatibility with the HFC refrigerant in the hermetically sealed container according to the third aspect.

The rotary compressor according to the eighth aspect of the present invention encloses a lubricating oil having compatibility with the hydrocarbon-based refrigerant in the hermetically sealed container according to the fifth aspect.

A refrigeration cycle according to a ninth aspect of the present invention is a refrigeration cycle comprising a compressor, an evaporator, a decompression device, and a condenser, wherein the compressor is the rotary compressor of any one of the first to eighth aspects. will be.

A refrigerator according to a tenth aspect of the present invention is a refrigeration cycle including a compressor, an evaporator, a decompressor, and a condenser, wherein the compressor is the rotary compressor of any one of the first to eighth aspects. .

According to the first aspect, in the contact surface between the cylinder and the frame and the contact surface between the cylinder and the cylinder head, the high-temperature, high-pressure gas refrigerant is prevented from flowing back to the low pressure side with the evaporator, and is stopped even without providing a check valve in the circuit. The temperature rise of the cooler can be prevented.

The inside of the sealed container is a suction pressure atmosphere, which prevents the reverse flow of the high-temperature and high-pressure gas refrigerant to the low pressure side where the evaporator is located, and avoids the temperature rise of the stopped cooler without providing a check valve in the circuit. Although there is a compressor, the rotary type is more efficient in terms of the compression mechanism than the reciprocating type.

In addition, since the blade is integrated with the piston, even when the inside of the airtight container is the suction pressure, it is necessary to solve the problem of starting due to the large pressure of the vane spring, that is, a motor with a large starting torque, such as a rolling piston type rotary compressor. There is no limit in the efficiency of the motor.

In addition, it is possible to prevent abrasion and sludge generation due to excessive sliding of the vane tip with respect to the piston outer circumferential surface due to the large pressure of the vane spring, and to prevent the sludge from being discharged or deposited into the refrigerant circuit. .

In addition, since the blade is integrated with the piston and the inside of the airtight container is a suction pressure atmosphere, concentration of the load acting on the blade side during the sliding of the blade can be avoided, and an increase in the sliding loss due to the sliding of the blade can be prevented. As a result, a highly reliable and highly efficient rotary compressor can be obtained.

As described above, the rotary compressor according to the first aspect has a suction pressure atmosphere inside the sealed container and a blade integrated with the piston, so that the vane spring for pressurizing the vane against the piston becomes unnecessary and the vane spring has an excessive pushing force. Sludge generation and leakage into the circuit by eliminating the vane tip and the sliding part of the piston outer peripheral surface without severely deteriorating the original high efficiency while avoiding the reduction of motor efficiency due to inadequate starting or increasing the starting torque. The deposition can be suppressed, and the leakage of the high pressure gas to the evaporator in the stop can be avoided without providing a check valve or the like in the circuit, and the sliding loss of the blade can also be reduced.

Therefore, a highly reliable rotary compressor can be obtained without compromising the original high efficiency of the rotary type.

According to the second aspect, the vibration inside the compressor is absorbed by the elastic support member to make it difficult to transmit to the outside, so that low noise and low vibration can be achieved without compromising the inherent high efficiency of the rotation, and the compressor freezes the refrigerator. The vibration transmitted to the piping system which comprises a cycle can be reduced. In addition, when the electric motor part and the compression mechanism part are directly attached to the hermetic container, the diameter of the pipe to the compressor is thinner to prevent the pipe from being deformed or damaged due to the vibration transmitted from the compressor having high vibration to the piping system. Although the length of the movable part is configured to be long, the external vibration is reduced so that such a necessity is eliminated, thereby reducing the efficiency caused by pressure loss, increasing the cost due to complicated pipes, and further avoiding complicated piping designs. .

In addition, since the inside of the sealed container is a suction pressure atmosphere instead of the discharge pressure atmosphere, even if the compressor mechanism and the electric mechanism are elastically supported in the sealed container, there is no need to arrange the suction pipe in the sealed container. In order to avoid deformation and breakage, the problem of an increase in pressure loss caused by lowering rigidity can be solved.

Therefore, by utilizing the characteristics of the highly efficient rotary compressor, it is possible to obtain a low noise, low vibration, low-period and high efficiency rotary compressor.

According to the third aspect, since the refrigerant does not contain chlorine and the extreme pressure effect cannot be expected, since the vanes and the piston are integrally formed, the conditions are strict sliding when the conventional rotary compressor is used together with the HFC refrigerant. Since the vane tip and the piston outer circumferential surface are eliminated, sludge generation, outflow into the circuit, and deposition can be suppressed. In the reciprocating type, the suction pressure loss caused by the presence of the intake valve when the volumetric flow rate R134a or the like is used for the same capacity as that of the R12 can be reduced because there is no intake valve. By these effects, a high reliability and long life rotary compressor can be obtained without using the HFC refrigerant that does not lead to ozone layer destruction, without compromising the original high efficiency of the rotary type.

According to the fourth aspect, since the refrigerant is not dissolved in the lubricating oil, the lubricating oil is supplied to the sliding portion with a stable viscosity, so that abnormal wear and burning of the sliding portion are less likely to occur. Therefore, it is possible to obtain a rotary compressor that does not impair the inherent high efficiency of the rotary type, and has high reliability, long life and no contribution to ozone layer destruction.

According to the fifth aspect, as compared with the compressor having the discharge pressure atmosphere, the discharge pressure portion in the circuit volume which is operated by the space in the sealed container decreases by the space in the sealed container and the oil accumulated in the sealed container is sucked in. Since it is in a pressure atmosphere, the amount of refrigerant dissolved in oil is reduced, so that the initial amount of refrigerant can be reduced, and it is more safe in that it is difficult to reach the explosion limit even when the sealed refrigerant leaks into the room. Even though the sealed container has the same suction pressure atmosphere, since the reciprocating compressor has an asymmetrical compression mechanism, the rotating compressor of the blade-integrated piston type of the symmetrical arrangement has a smaller space volume in the sealed container, which is more advantageous in terms of reducing the amount of encapsulated refrigerant. . In the reciprocating type, if the capacity is the same as that of using R134a, the suction pressure loss caused by the presence of the suction valve when using R600a or the like of hydrocarbon refrigerant with increased volume flow rate can be reduced because there is no suction valve. These effects allow rotational inherent safety while safely using CFC refrigerants containing chlorine as ozone depleting substances, HCFC refrigerants, or hydrocarbon refrigerants that do not contribute to ozone layer destruction and global warming, rather than HFC refrigerants with high global warming coefficients. High reliability and long life rotary compressor can be obtained without compromising high efficiency.

According to the sixth aspect, since the refrigerant is not dissolved in the lubricating oil, the lubricating oil is supplied to the sliding portion with a stable viscosity, so that abnormal wear and sintering of the sliding portion are less likely to occur. Therefore, it is possible to obtain a rotary compressor that does not adversely affect the global environment by contributing to high reliability, long life, ozone layer destruction, global warming, etc. without compromising the inherent high efficiency of the rotary type.

According to the seventh or eighth aspect, since the returnability of the lubricating oil circulated in the circuit is better than that of the incompatible lubricating oil, the lubricating oil is stabilized and supplied to the sliding portion without depleting the lubricating oil in the compressor, and abnormal wear of the sliding portion is achieved. , Sintering, etc. are less likely to occur. In low pressure vessels, the gas after compression is discharged directly into the circuit without opening it into the container. However, since the amount of lubricating oil does not need to be kept extremely low, it is possible to expect a gap sealing effect by the lubricating oil in the compression chamber. Therefore, it is possible to obtain a rotary compressor that does not impair the inherent high efficiency of the rotary type, and has high reliability, long life, and no contribution to the breakdown of the morning layer.

According to the ninth or tenth aspect of the present invention, a low-cost, high-efficiency refrigeration system or an air conditioner that prevents a rise in the temperature of the cooler by preventing a reverse flow to the low pressure side of a stopped high-pressure gas refrigerant without providing a check valve or the like in the circuit. , Vanes and pistons are integrally formed, so a high-efficiency, high-reliability refrigeration unit or air conditioner that avoids a decrease in motor efficiency due to unstable starting or excessive starting torque due to excessive pressure on the vane spring is excessive. Since there is no sliding of vane tip and piston outer circumferential surface under sliding condition, the highly reliable refrigeration unit, air conditioning unit, motor part and compressor part which suppressed sludge generation and leakage into the circuit are elastically supported in the sealed container. And the vibration generated by the compressor section is hard to be transmitted to the outside, so the compressor is further lowered in vibration and low noise. No need to complicate the piping around the compressor, simplifying the pipe design and reducing the efficiency loss caused by pressure loss, so there is no extreme pressure effect because it does not contain low-cost, high efficiency, low vibration, low noise refrigeration equipment, air conditioning equipment and chlorine. The use of HFC refrigerants such as R134a prevents sludge generation and outflow and deposition into the circuit because the lubrication conditions are not strict. Therefore, a refrigerating device or air conditioner that has high reliability, long life, and does not contribute to ozone layer destruction, Since the sealed container has a suction pressure atmosphere, it is possible to reduce the initial filling amount of the refrigerant without compromising the inherent high efficiency of the rotary type. Therefore, it is safer to use a refrigeration device or an air conditioning device that does not contribute to ozone layer destruction or global warming using hydrocarbon refrigerants. You can get it.

In particular, when incompatible oils are used as lubricating oils, the refrigerant does not dissolve in the lubricating oils, so that the lubricating oil is supplied to the sliding parts with a stable viscosity, so that abnormal wear and sintering of the sliding parts are less likely to occur. And an air conditioner, etc., on the other hand, in the case of using a compatible oil as a lubricant, a high reliability, long-life refrigeration unit or air conditioner, etc., with good return of lubricating oil circulated in the circuit and no depletion of lubricating oil in the compressor Obtained.

<Example>

Example 1

1 is a longitudinal sectional view and a refrigerating cycle view of a rotary compressor of a blade integral piston type according to an embodiment of the present invention, and FIG. 2 is a cross sectional view showing a compression mechanism of a compressor.

In the figure, the rotary compressor of the blade integral piston type is constituted by an electric motor part 70 consisting of a stator 1 and a rotor 2 and a compression mechanism part 80 driven by the electric motor part 70. . The compression mechanism (80) is freely fitted to the cylinder (5) having the cylinder chamber (4) with the suction port (3) and the discharge port (14) open, the eccentric shaft portion (7) of the drive shaft (6) and the cylinder (5). Of the compression chamber communicating with the low pressure chamber 9 and the discharge port 14 of the compression chamber, which is integrally provided with the piston 15a and the piston 15a, and which communicates the cylinder chamber 4 with the inlet port 3. It consists of a blade 15b partitioned by the high-pressure chamber 10 and a guide 17 freely fitted in the cylindrical hole portion 16 formed in the cylinder 5 and supporting the blade 15b freely in slide and swing. By rotation of the drive shaft 6, the piston 15a revolves along the inner wall of the cylinder chamber 4 so as to oscillate with the rotational center position 18 of the guide 17 as the point via the blade 15b. The refrigerant gas sucked in the suction port 3 is compressed at each idle and discharged from the discharge port 14.

Further, the blade movement space 5a in which the tip of the blade 15b swings is opened to the space in the sealed container 13 as shown in FIG. 9A or communicated through the hole in the space in the sealed container 13 so as to communicate with the blade 15b. And an oil storage space to enable sliding and sealing of the guide 17. The supply of lubricating oil to the oil storage space is carried out between the inlet port 3, the compression chambers 9 and 10, the cylinder 5 and the frame 19, and the cylinder head 20 by the injection pipe 30 described later. It runs through the gap. When the blade 15b moves in the direction of compressing the lubricating oil and refrigerant in the space in the blade movement space 5a, the blade movement space 5a is placed in the sealed container 13 as shown in FIG. 9A to smooth the movement. Opening to the space or communicating through the hole into the space in the sealed container 13 to discharge the lubricant and refrigerant. Since the inside of the airtight container 13 is a suction pressure atmosphere, discharge of lubricating oil etc. is easy and it is made possible for the blade 15b to perform a slide or rocking motion smoothly.

In FIG. 1, the refrigerant gas introduced from the suction pipe 24 is separated into the refrigerant gas and the lubricating oil 26 by the suction muffler 25 which suppresses the suction pulsation, and the separated lubricating oil 26 is the suction muffler 25. Return from the hole 27 provided in the lower portion to the oil storage portion of the bottom of the sealed container 13, the refrigerant gas is sent from the suction port (3) to the low pressure compression chamber (9) through a pipeline communicating with the suction port (3). Lose. The refrigerant gas compressed in the compression chamber is discharged from the discharge port 14 and discharged to the discharge tube 22 by suppressing the pulsation of the refrigerant gas by the discharge muffler 28 which suppresses the pressure pulsation. The separated lubricating oil 26 is returned to the oil storage part from the microhole 29 provided in the lower portion of the discharge muffler 28.

In addition, the refrigerant gas introduced from the suction pipe 24 reaches the suction port 3 through the suction path (such as the suction muffler 25) and generates a pressure loss in the course of passing through the suction path. Therefore, the pressure in the airtight container 13 becomes higher than the pressure in the suction port 3. Thus, the inlet port 3 is equipped with a spray pipe 30 for supplying the lubricating oil 26 by using the differential pressure in the compression chamber and the sealed container 13, and the lubricating oil flowing into the compression chamber from the spray pipe 30. Is supplied to the contact surface 21 of the cylinder 5 and the frame 19 and the contact surface 23 of the cylinder 5 and the cylinder head 20, and the sealing property of these contact surfaces becomes high.

In addition, the oil supply from the oil storage part below the sealed container 13 to the bearing part of the drive shaft 6 and the bearing part of the cylinder head 20 is performed by the oil hole provided in the drive shaft 6.

These electric motor part 70 and the compression mechanism part 80 are accommodated in the airtight container 13, and the electric motor part 70 and the compression mechanism part 80 are contracted-fit to the airtight container 13, and a means, such as welding, is used. Is attached directly.

In the compressor configured as described above, since the inside of the sealed container 13 is a suction pressure atmosphere, the contact surface 21 between the cylinder 5 and the frame 19 and the contact surface between the cylinder 5 and the cylinder head 20. At 23, the high-temperature, high-pressure gas refrigerant is prevented from flowing back to the low pressure side where the evaporator 36 is located, so that the temperature rise of the stopped cooler can be prevented without providing a check valve or the like in the circuit.

By preventing the back flow to the low pressure side of the high-temperature and high-pressure gas refrigerant to the evaporator by using the inside of the sealed container as an intake pressure atmosphere, it is possible to avoid the temperature rise of the stopped cooler without providing a check valve in the circuit. In addition, there is a reciprocating compressor, but the reciprocating type has a larger dead volume than the rotary type, and thus a larger loss in use, and a larger suction pressure loss due to the need of a suction valve, and a shorter discharge time. 1/2) The discharge flow rate is fast and the discharge pressure loss is large. ④ The fluctuation of the compression torque is large (approx. 2 times that of the rotary type). Therefore, a motor with a large maximum torque is required and compression is limited due to the limited efficiency of the motor. The rotary side is excellent in terms of the efficiency of the mechanism.

In order to prevent the reverse flow of the gas refrigerant to the evaporator side while avoiding the rise of the temperature of the cooler while it is stationary, while utilizing the superiority in terms of rotational efficiency, the pressure atmosphere in the sealed container is sucked by a conventional rotary piston type rotary compressor. In this case, since the force of the differential pressure in the compression chamber and the sealed container acts in the direction of separating the vane from the piston, the pressing force of the vane spring must be set large, and the vane spring is pressed when the pressure is balanced. Since the force acts as it is without being canceled by the differential pressure, the vane is pressed against the piston with a force greater than the pressing force necessary during normal operation, and an excessive load is applied to the piston. In order to start, a motor with a large starting torque is required, which causes a limitation in increasing the efficiency of the motor.

In addition, since the pressing force of the vane spring is set to be large, a strong pressing force always acts so that the sliding situation with the piston outer circumferential surface of the vane tip becomes excessive, and strict sliding conditions cause not only the vane tip wear but also sludge generation. Since the inside of the sealed container has the configuration of the suction pressure atmosphere, the generated sludge is discharged from the discharge tube into the circuit without being trapped in the space in the sealed container and accumulates in the circuit, causing the capillary to be closed.

In this embodiment, since the piston 15a and the blade 15b are integrally formed, the vane spring 12 for pressing the vane 11 against the piston 8 becomes unnecessary as shown in FIG. It is possible to avoid the deterioration of the motor efficiency due to inadequate starting or excessive starting torque of the vane spring 12 and to increase the starting torque. Occurrence, outflow into the circuit, and deposition can be suppressed.

In addition, since the blade movement space 5a is opened or communicated in the sealed container 13 of the suction pressure atmosphere, the pressure in the blade movement space 5a becomes the suction pressure Ps, which is smaller than the pressure Pc of the high pressure chamber 10 and low pressure. As shown in Fig. 3, the support point S of the guide 17 on the discharge side is close to the blade movement space 5a, and the support point S of the guide 17 on the suction side, as shown in FIG. 'Is the point near the center of the guide, and as shown in FIG. 11, the load is not concentrated in a narrow range, and the reliability decreases due to the increase of the sliding loss between the side surface of the blade 15b and the flat portion of the guide 17. Does not occur.

By these effects, the efficiency of the compressor can be improved, the reliability can be improved, and the service life can be extended. Further, the refrigeration cycle using the compressor can be reduced in price.

Example 2

In the present embodiment, the same parts as those in the above-described first embodiment will be denoted by the same reference numerals, and the description thereof will be omitted. Fig. 4A is a longitudinal sectional view of the blade-integral piston compressor of the present embodiment showing the elastic support member, and Fig. 4B is a longitudinal sectional view and a refrigeration cycle diagram of the same compressor of the present embodiment showing the suction path and the discharge path. In FIG. 4A and FIG. 4B, the blade integral piston type compressor is comprised by the motor part 70 which consists of the stator 1 and the rotor 2, and the compression mechanism part 80 driven by this motor part 70. As shown in FIG. do. As shown in FIG. 2 of the first embodiment, the compression mechanism 80 includes a cylinder 5 having a cylinder chamber 4 with an inlet 3 and an outlet 14 opened, and an eccentric shaft 7 of a drive shaft 6. Piston 15a, which is freely fitted in the cylinder 5 and disposed in the cylinder 5, integrally provided in the piston 15a, and the low pressure chamber 9 and the discharge port, which communicate the cylinder chamber 4 with the suction port 3; A guide that freely slides into the blade 15b partitioned by the high pressure chamber 10 communicating with the 14 and the cylindrical hole 16 formed in the cylinder 5, and supports the blade 15b freely and swing freely ( 17) and the inner wall of the cylinder chamber 4 so that the piston 15a is oscillated by the rotation of the drive shaft 6 with the rotational center position 18 of the guide 17 as the point via the blade 15b. Along with each other, compresses the refrigerant gas sucked from the suction port 3 at each discharge time, It is adapted to. In FIG. 4B, the refrigerant gas introduced from the suction pipe 24 is separated into the refrigerant gas and the lubricating oil 26 by the suction muffler 25, and the separated lubricating oil 26 is separated from the hole 27 provided in the suction muffler. It is returned to the sealed container 13, and only refrigerant gas is sent to the compression chamber from the suction port 3. In addition, the compressed refrigerant gas is discharged from the discharge port 14, the pulsation of the refrigerant gas is suppressed by the discharge muffler 28, and discharged from the discharge tube 22 to the refrigeration cycle. These structures are the same as in Example 1.

In addition, the refrigerant gas flowing from the suction pipe 24 reaches the suction port 3 through the suction path and generates a pressure loss in the course of passing through the suction path. Therefore, the pressure in the airtight container 13 becomes higher than the pressure in the suction port 3. Thus, a suction pipe 30 is attached to the suction port 3 for supplying the lubricating oil 26 to the compression chamber by using the differential pressure in the compression chamber and the sealed container 13, and the cylinder 5 and the frame 19 are attached. The sealing property is improved by supplying the lubricating oil 26 to the contact surface 21 and the contact surface 23 of the cylinder 5 and the cylinder head 20. This point is also the same as in Example 1.

These electric motor part 70 and the compression mechanism part 80 are accommodated in the sealed container 13, and the stator 1 protrudes in the axial direction toward the electric motor part 70 from the compression mechanism part 80. It is bolted with the leg part 31 of. At this time, the leg part 31 of the frame 19 is three or more so that the engagement surface with the stator 1 can be determined. This frame leg part 31 has a flexible structure which is easy to deform by taking the shape of the leg part which protrudes from the other part of the frame 19. As shown in FIG. In addition, even when there is a shape deviation of the stator 1 (unevenness in the axial dimension of the stator occurs due to the non-uniformity of the plate thickness of the laminated steel sheet forming the iron core of the stator) when the bolt is fastened, The contact portion between the piston 15a of the frame 19 and the cylinder 5 is integrally or appropriately connected to other parts of the frame so as not to transmit distortion or deformation. Therefore, even if the stator 1 has a shape deviation, the contact portion between the frame 19, the piston 15a, and the cylinder 5 does not become uneven and wear, increase in input, leakage, and the like do not occur.

Since the vane 15b and the piston 15a are integrally formed in the rotary compressor of the blade integral piston type configured as described above, the vane spring 12 for pressing the vane 11 against the piston 8 is provided. Of the vane spring and the outer circumferential surface of the piston can be avoided, and the vane tip and the piston outer circumferential surface of the vane spring 12 can be avoided. This eliminates the occurrence of sludge, leakage into the circuit and deposition. In addition, since the inside of the airtight container 13 is a suction pressure atmosphere, a high temperature is generated at the contact surface 21 between the cylinder 5 and the frame 19 and the contact surface 23 between the cylinder 5 and the cylinder head 20. Since the high-pressure gas refrigerant does not flow back to the low pressure side where the evaporator 36 is located, it is possible to prevent the temperature rise of the stopped cooler without providing a check valve or the like in the circuit. By these effects, it is possible to improve the efficiency of the compressor, to improve the reliability and the long life, and to further lower the cost of the refrigeration cycle using the compressor.

In addition, the motor unit 70 and the compression mechanism unit 80 integrally configured as described above are supported in the hermetic container 13 by an elastic support member 32 such as a coil spring (in the case of Figs. 4A and 4B). The lower end of the 19 is supported by the plurality of elastic support members 32 in the hermetically sealed container 13), and a gap (between the inner wall of the hermetically sealed container 13 and the electric motor part 70 and the compression mechanism part 80). Since the electric motor unit 70 and the compression mechanism unit 80 are configured to generate a gap that does not collide with the inner wall of the sealed container 13, the vibration generated by the electric motor unit 70 and the compression mechanism unit 80 and Since noise is difficult to transmit to the outside, it is possible to further reduce the vibration and noise of the compressor.

In addition, although the coil spring has been described as the elastic support member 32, vibration and noise of the electric motor unit 70 and the compression mechanism unit 80 are transmitted to the outside in the case of elastic support members such as leaf springs and rubber in addition to the coil springs. Clearly, it is difficult to achieve further low vibration and low noise of the compressor.

In addition, as described above, the electric motor unit 70 and the compression mechanism unit 80 are held by the elastic support member 32 in the sealed container 13, and the discharge pipe 22 is discharged by the discharge muffler 28 of the compression mechanism unit 80. The shape can be easily changed as a whole by arrange | positioning so that it may not contact with the inner wall of the airtight container 13 from the connection part to the airtight container 13 to the fixed part with the airtight container 13. In other words, the pipe is formed into a weak rigid shape as a whole, and the structure is such that the vibration of the compression mechanism 80 and the electric motor 70 in the sealed container 13 is less absorbed and transmitted to the outside.

On the other hand, the suction pipe 24 enters the hermetic container 13 from the fixing portion of the hermetic container 13 and is connected to the suction muffler 25, but the connection with the suction muffler 25 allows the vibration of the compression mechanism 80. Can be made by loose connection (since the sealed pressure chamber 13 is the suction pressure atmosphere).

Example 3

Next, Example 3 of the present invention will be described. The blade integrated piston type rotary compressor of this example uses an HFC refrigerant such as R134a as the refrigerant in the blade integrated piston type rotary compressor configured in the first or second embodiment.

In the blade integrated piston-type rotary compressor configured as described above, since the inside of the sealed container is a suction pressure atmosphere, the high-temperature and high-pressure gas refrigerant flows back toward the low pressure side of the evaporator at the contact surface between the cylinder and the frame and the contact surface between the cylinder and the cylinder head. It is possible to prevent the rise of the temperature of the cooler during stop without providing a check valve or the like in the circuit. In addition, since the vanes and the piston are integrally formed, it is possible to avoid a decrease in motor efficiency due to unsatisfactory starting or increasing starting torque caused by excessive pressure on the vane spring generated in the conventional rotary compressor. At the same time, there is no sliding part of the vane tip and the piston outer circumferential condition where conditions are strict, so even if HFC-based refrigerants such as R134a, which do not contain chlorine and have no extreme pressure effect, there is no sliding part with strict lubrication conditions. Runoff and deposition can be suppressed. By these effects, the efficiency of the compressor can be improved, the reliability can be improved, and the life can be further extended. Further, the refrigeration cycle using this compressor can be reduced in price.

Example 4

Next, Example 4 of the present invention will be described. In this example, the blade-integrated piston-type rotary compressor is a lubricating oil 26 encapsulated in the hermetic container 13 in the compressor configured as in the third embodiment, and is hardly incompatible or hardly compatible with HFC refrigerants such as R134a. Lubricants such as (HAB) are used.

In the blade-integrated piston-type rotary compressor configured as described above, since the refrigerant is not dissolved in the lubricating oil, the viscosity of the lubricating oil is always kept constant and supplied to the sliding part, so that abnormal wear and sintering of the sliding part are difficult to occur.

Example 5

Next, Example 5 of the present invention will be described. The blade integrated piston type rotary compressor of this example uses hydrocarbon refrigerants such as propane and isobutane (HC refrigerant) as the refrigerant in the blade integrated piston type rotary compressors of the first and second embodiments.

In the blade integrated piston-type rotary compressor configured as described above, since the inside of the sealed container is an intake pressure atmosphere, the amount of refrigerant charge can be reduced compared to a compressor configured as a discharge pressure atmosphere. No limit is reached. In addition, compared with the reciprocating compressor of the suction pressure atmosphere in the sealed container, the rotary compressor of the blade integral piston type has the symmetrical arrangement of the compressor, so that the space volume in the sealed container is less than that of the asymmetric reciprocating type. It is more advantageous from the point of view. That is, in this embodiment, CFC refrigerants containing chlorine, which are ozone depleting substances, HCFC refrigerants, or HFC refrigerants with high global warming coefficient, can be safely used as refrigerants without adverse effects on the global environment. Can get a compressor.

Moreover, when it is comprised as a compressor for refrigerators, the mountability to a refrigerator machine room is also improved by the part which can make an external dimension smaller than a reciprocating reciprocating-type asymmetry arrangement.

Example 6

Next, Example 6 of the present invention will be described. In this example, the blade-integrated piston-type rotary compressor is a lubricant 26 encapsulated in the hermetic container 13 in the compressor configured as in the fifth embodiment, and is less incompatible or incompatible with hydrocarbon refrigerants such as propane and isobutane. Lubricating oils such as fluorine or polyalkylene glycol (PAG) are used.

In the blade-integrated piston-type rotary compressor configured as described above, the amount of hydrocarbon refrigerants such as propane and isobutane, which are combustible refrigerants, can be suppressed to a small amount. Therefore, the amount of refrigerant refrigerant to the lubricant 26 can be reduced. It is not necessary to enclose an extra refrigerant in anticipation, and it becomes possible to reduce the amount of encapsulation of the refrigerant as a whole, and the explosion limit is not reached even when the enclosed refrigerant leaks into the room.

In addition, since the refrigerant is not dissolved in the lubricating oil 26, the viscosity of the lubricating oil 26 is always kept constant and supplied to the sliding portion, so that abnormal wear, sintering, etc. of the sliding portion are less likely to occur.

Example 7

Next, Example 7 of the present invention will be described. The rotary compressor of the blade-integrated piston type of the present example is a lubricating oil 26 encapsulated in the hermetic container 13 in the compressor configured as in the third embodiment, and includes lubricating oil such as ester oil having compatibility with HFC refrigerants such as R134a. use.

In the compressor configured as described above, since the returnability of the lubricating oil circulated in the circuit is better than that of the incompatible lubricating oil, the viscosity of the lubricating oil can be increased, so that the sealing effect of the oil in the compression chamber is increased and the loss caused by leakage is reduced. It becomes possible.

Example 8

Next, Example 8 of the present invention will be described. The rotary compressor of the blade-integrated piston type of this example is a lubricating oil 26 enclosed in the hermetic container 13 in the compressor configured as in Example 6, and is a paraffinic mineral oil having compatibility with hydrocarbon refrigerants such as propane and isobutane. Or lubricating oil, such as a hard acyl benzene (HAB) system, is used.

In the compressor configured as described above, since the returnability of the lubricating oil circulated in the circuit is better than that of the incompatible lubricating oil, the viscosity of the lubricating oil can be increased, so that the sealing effect of the oil in the compression chamber is increased and the occurrence of loss due to leakage is reduced. It becomes possible.

Example 9

Next, Example 9 of the present invention will be described. As shown in FIGS. 1 and 2, the rotary compressor of the blade-integrated piston type described in Embodiments 1 to 8 is connected to a condenser 38, a decompression device 37, an evaporator 36, and the like to form a refrigeration cycle. Thus, a refrigerating device or an air conditioner utilizing the characteristics of the compressor can be obtained.

In particular, when a refrigeration cycle is constructed using the compressor and the refrigerator is used, the inside of the sealed container 13 of the compressor is a suction pressure atmosphere, thereby providing a check valve or the like to the evaporator of a high temperature and high pressure gas refrigerant. A high-efficiency refrigerator without backflow can be obtained, and a refrigerator with low vibration and low noise can be obtained by supporting the electric motor unit 70 and the compression mechanism unit 80 of the compressor with the elastic support member 32. By using a hydrocarbon-based refrigerant, it is possible to obtain a refrigerator which ensures safety and does not adversely affect the global environment.

In addition, by adding an inverter function to the compressor of the above embodiment and using the refrigerant as a hydrocarbon-based refrigerant for use in a refrigerator, there is an effect that the compressor for a refrigerator can be downsized as compared with the corresponding reciprocating compressor.

According to the present invention, a more stable start can be always performed without using a motor of excessive starting torque, and a check valve or the like is specially provided in the circuit to prevent the high-temperature and high-pressure gas refrigerant from flowing back to the cooler side during stop during on / off operation. HFC system that can reduce the noise by preventing vibration and noise inside the compressor from being directly transmitted to the outside without damaging or damaging the suction pipe, and does not lead to ozone layer destruction as a refrigerant. In addition to the use of refrigerants, the use of flammable refrigerants such as hydrocarbon-based refrigerants that do not adversely affect the global environment further enhances the safety against ignition and explosion, and the occurrence of sludge caused by excessive sliding points and deposition in the circuit. High reliability and high efficiency blade integrated without increasing sliding loss of blade It is possible to obtain a rotary compressor of the stone type.

According to the present invention, a refrigeration cycle utilizing the characteristics of the compressor can be obtained using the compressor.

Moreover, according to this invention, the refrigerator which utilized the characteristic of the said compressor can be obtained using the said compressor.

Claims (10)

A compressor having a cylinder having a suction port and a discharge port in a cylinder chamber, a piston eccentrically revolving in the cylinder, a blade integrally provided in the piston and partitioning the cylinder into a high pressure chamber and a low pressure chamber, and a drive shaft for revolving the piston; A blade-integrated piston-type compressor comprising an electric motor portion for rotating the drive shaft and a hermetically sealed container, wherein the compression compressor and the inside of the hermetically sealed container accommodating the electric motor portion have a suction pressure atmosphere. . The method of claim 1, And a gap between the compressor sphere and the sealed vessel inner wall and between the motor portion and the sealed vessel inner wall, the compressor sphere and the motor portion being held by the elastic support member in the sealed vessel. The method according to claim 1 or 2, A rotary compressor, wherein the refrigerant used is an HFC refrigerant. The method of claim 3, And a lubricant having a low incompatibility or low compatibility with the HFC refrigerant in the sealed container. The method according to claim 1 or 2, A rotary compressor, wherein the refrigerant used is a hydrocarbon refrigerant. The method of claim 5, And a lubricant having a low incompatibility or low compatibility with a hydrocarbon-based refrigerant in the hermetically sealed container. The method of claim 3, And a lubricating oil having compatibility with the HFC refrigerant in the sealed container. The method of claim 5, And a lubricating oil having compatibility with a hydrocarbon-based refrigerant in the hermetic container. A refrigeration cycle comprising a compressor, an evaporator, a decompression device, and a condenser, wherein the compressor is a rotary compressor according to any one of claims 1 to 8. A refrigerator provided with a compressor, an evaporator, a decompression device and a condenser, wherein the compressor is a rotary compressor according to any one of claims 1 to 8.