JP5504681B2 - Rotary compressor - Google Patents

Description

  The present invention relates to a rotary compressor provided with a vane that is inserted into a slot formed in a cylinder, partitions a compression chamber into a high-pressure side and a low-pressure side, and has a cylindrical columnar portion.

  Conventionally, in a refrigeration apparatus, an air conditioner, etc., gas refrigerant evaporated by an evaporator is sucked, compressed to a pressure necessary to condense the sucked gas refrigerant, and high-temperature and high-pressure gas refrigerant is sent out into the refrigerant circuit. A compressor is used. As one of such compressors, a rolling piston rotary compressor (hereinafter simply referred to as a rotary compressor) is known.

  FIG. 10 is a partial longitudinal sectional view showing an example of a conventional rotary compressor. Moreover, FIG. 11 is a figure which shows the cross section which follows surface AA of the rotary compressor shown in FIG.

  As illustrated in FIGS. 10 and 11, in the rotary compressor, the electric motor 202 and the compression mechanism unit 203 are connected by a shaft 231 and stored in the sealed container 201. The compression mechanism unit 203 includes a cylinder 230, and an upper bearing 234 and a lower bearing 235 that close the upper end surface and the lower end surface of the cylinder 230. A space called a compression chamber 239 is formed by the cylinder 230, the upper bearing 234, and the lower bearing 235.

  In the compression chamber 239, a piston 232 fitted to the eccentric portion 231a of the shaft 231 supported by the upper bearing 234 and the lower bearing 235 is provided. The compression chamber 239 further includes a vane 233 that reciprocates following the eccentric rotation of the outer periphery of the piston 232 and partitions the compression chamber 239 into a low pressure side and a high pressure side.

  An oil hole 241 is formed in the shaft 231 along the central axis, and an oil supply hole 242 communicating with the oil hole 241 and an oil supply are provided in a portion close to the lower end portion of the upper bearing 234 and the upper end portion of the lower bearing 235. A hole 243 is provided. An oil supply hole 244 communicating with the oil hole 241 is provided in a portion of the shaft 231 that is close to the eccentric portion 231a. An oil groove 245 that passes through the opening of the oil supply hole 244 is formed on the outer periphery of the shaft 231.

  A suction port 240 that sucks gas into the low pressure side of the compression chamber 239 is opened in the cylinder 230, and gas is discharged from the high pressure side of the compression chamber 239 formed by turning from the low pressure side to the upper bearing 234. The discharge port 238 is opened. The discharge port 238 is formed as a circular hole in plan view that penetrates the upper bearing 234. Further, a discharge valve 236 that is opened when a pressure of a predetermined magnitude or more is received from the discharge port 238 is provided at a portion corresponding to the upper portion of the upper bearing 234 above the discharge port 238. A cup muffler-237 is further disposed on the upper bearing 234 so as to cover the discharge valve 236.

  In the rotary compressor configured as described above, on the low pressure side of the compression chamber 239, when the sliding contact portion of the piston 232 and the cylinder 230 starts to pass through the suction port 240 due to eccentric rotation, the suction chamber gradually expands. During this time, gas is sucked into the suction chamber from the suction port 240. On the other hand, on the high pressure side, the sliding portion of the piston 232 approaches the discharge port 238 while gradually reducing the compression chamber 239. When the pressure is compressed to a predetermined pressure or higher, the discharge valve 236 is opened and the discharge port 238 is opened. Out of the gas. The outflowing gas is discharged into the sealed container 201 by the cup muffler-237.

  In the above configuration, the oil is hardly held at the sliding portion between the piston 232 and the tip of the vane 233, and the sliding property is severe. That is, since it is difficult to form an oil film, metal contact occurs and wear tends to occur. Furthermore, due to the recent shift of alternative refrigerants, when the non-azeotropic refrigerants R407C and R410A are used in conventional rotary compressors, the lubricity of these refrigerants themselves is poor, and thus wear at the sliding parts further occurs. Cheap.

  Several means for solving such wear have been proposed. FIG. 12 is a cross-sectional view showing a main part of a swinging piston type rotary compressor which is one means for solving the above-mentioned wear problem. In FIG. 12, this piston type rotary compressor reciprocates in a cylinder 130, a piston 132 fitted to an eccentric portion 131 a of a crankshaft 131 disposed in the cylinder 130, and a slot 130 b formed in the cylinder 130. And a vane 133 which is moved and is connected to the piston 132 so as to freely swing. In this way, by making the piston 132 swing freely, the oil is easily held at the swinging portion at the tip of the piston 132 and the vane 133, thereby easily forming an oil film. Can be improved significantly (see, for example, Patent Document 1).

JP 2000-120572 A

  However, in the oscillating piston type rotary compressor shown in FIG. 12, a gap must be provided in the oscillating part of the piston 132 and the vane 133. Gas and oil are likely to leak from the high pressure side to the low pressure side of the compression chamber. As a result, the conventional oscillating piston type has a problem that the compression loss increases and the efficiency of the compressor decreases.

  Therefore, an object of the present invention is to provide a rotary compressor in which leakage of gas and oil from the high pressure side to the low pressure side of the compression chamber hardly occurs.

  To achieve the above object, according to the present invention, a cylinder, an eccentric part of a shaft disposed in the cylinder, and a cylindrical groove fitted to the eccentric part and having an arc angle of more than 180 ° are formed. A rotary compressor comprising: a piston; and a vane having a columnar cylindrical portion that is inserted into a slot formed in the cylinder, partitions a space in the cylinder into a high pressure side and a low pressure side, and engages with a groove. The extension line of the arc of the groove is inside the outer peripheral line of the piston.

  According to the said structure, since the circular arc part of the groove | channel formed in a piston can be increased, the seal width of a high voltage | pressure side and a low voltage | pressure side increases. As a result, when the vane reciprocates in the slot, the leakage of gas and oil from the high pressure side to the low pressure side can be suppressed to the minimum, so that a rotary compressor having high efficiency can be provided. .

The fragmentary longitudinal cross-sectional view of the rocking | swiveling piston type rotary compressor which concerns on one Embodiment of this invention Enlarged view of the compression mechanism of the rotary compressor shown in FIG. The figure which shows the state transition of the compression mechanism part 3 during the shaft 31 shown in FIG. 1 making one rotation. An exploded perspective view of the piston 32 and the vane 33 shown in FIGS. Schematic diagram when the extension line La of the groove 32a is inside the extension line Lb of the piston 32 Schematic diagram when the extension line La of the groove 32a is outside the extension line Lb of the piston 32 FIG. 2 is a schematic diagram showing a case where the cylindrical portion 33a is brought closer to the high pressure side of the compression chamber 39 with reference to the central plane Pc on the two side surfaces of the vane 33 shown in FIG. FIG. 2 is a schematic diagram showing a case where the cylindrical portion 33a is brought closer to the low pressure side of the compression chamber 39 with reference to the central plane Pc on the two side surfaces of the vane 33 shown in FIG. The figure which illustrates the mark 33c provided in the vane 33 shown in FIG. Longitudinal sectional view of a conventional rolling piston type rotary compressor FIG. 10 is a cross-sectional view showing a compression mechanism portion of the rolling piston type rotary compressor shown in FIG. Cross-sectional view showing a compression mechanism of a conventional oscillating piston type rotary compressor

  The present invention is formed in a cylinder, an eccentric portion of a shaft disposed in the cylinder, a piston fitted with the eccentric portion and formed with a cylindrical groove having an arc angle of over 180 °, and the cylinder A rotary compressor provided with a vane inserted into a slot, partitioning a space in the cylinder into a high-pressure side and a low-pressure side, and having a cylindrical columnar portion engaged with the groove, and extending the arc of the groove It is characterized in that the line is inside the outer peripheral line of the piston.

  Since the arc portion of the groove can be increased with the above configuration, the seal width between the high pressure side and the low pressure side increases. As a result, when the vane reciprocates in the slot, leakage of gas and oil from the high pressure side to the low pressure side of the compressor can be reduced, and as a result, the efficiency of the rotary compressor is improved. Further, when machining the groove of the piston, it is possible to first make a hole in the piston and then process other than the arc portion. As a result, the processing accuracy such as roundness and squareness of the arc portion of the groove is improved, the processing cost can be reduced, and the efficiency of the rotary compressor is improved.

  Preferably, the cylindrical portion is closer to the high pressure side with respect to the center surface of the two side surfaces of the vane. Here, in the rotary compressor, it is necessary to provide a relief portion to either avoid contact of the piston and in the vane movement. On the high-pressure side of the relief portion, the top clearance volume is reached, and loss occurs due to re-expansion during inhalation. However, by adopting the above configuration, the amount of escape on the high pressure side is reduced, so that the top clearance volume can be reduced and the efficiency of the compressor is improved.

  More preferably, there is a mark on either one of the two side surfaces of the vane. Since this mark can be used as a mark for determining whether the vane is up or down during assembly, it is possible to reduce a loss due to a wrong assembly of the rotary compressor.

In the rotary compressor, CO ₂ that is a high-pressure refrigerant can be used as the working fluid. Regarding CO ₂ , the differential pressure is large and sliding loss and leakage loss are large, but it is more preferable to use CO ₂ as the working fluid by making the cylindrical portion and the groove as described above. As a result, the efficiency and reliability of the compressor can be improved.

In the rotary compressor, it is possible to use a refrigerant mixed with a hydrofluorocarbon having a double bond between carbon and carbon as a base component, and a hydrofluorocarbon having no double bond as a working refrigerant. Since this refrigerant does not contain chlorine, the reliability of the sliding portion is very strict. However, the efficiency and reliability of the compressor can be improved more effectively by making the groove as described above and using this refrigerant. Moreover, since this refrigerant has no ozone destruction and a low global warming potential, it can contribute to the configuration of an air-conditioning cycle that is friendly to the earth.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 is a partial longitudinal sectional view of a swinging piston type rotary compressor according to an embodiment of the present invention. FIG. 2 is an enlarged view of a compression mechanism of the rotary compressor shown in FIG.

  1 and 2, in the rotary compressor, the electric motor 2 and the compression mechanism unit 3 are connected by a shaft 31 and stored in the sealed container 1. The compression mechanism unit 3 includes a cylinder 30, an upper bearing 34 and a lower bearing 35 that close the upper end surface and the lower end surface of the cylinder 30 and support the shaft 31. A space called a compression chamber 39 is formed by the cylinder 30, the upper bearing 34, and the lower bearing 35.

  In the compression chamber 39, a piston 32 fitted to the eccentric portion 31a of the shaft 31 is provided. The compression chamber 39 further includes a vane 33 that reciprocates following the eccentric rotation of the outer periphery of the piston 32 to partition the compression chamber 39 into a low pressure side and a high pressure side. The main body portion of the vane 33 is inserted into a slot 30b provided in the cylinder 30 so as to be able to reciprocate.

  An oil hole 41 is formed in the shaft 31 along the central axis, and an oil supply hole 42 and an oil supply communicating with the oil hole 41 are provided in portions close to the lower end portion of the upper bearing 34 and the upper end portion of the lower bearing 35. A hole 43 is provided. An oil supply hole 44 communicating with the oil hole 41 is provided in a portion of the shaft 31 adjacent to the eccentric portion 31a. An oil groove 45 that passes through the opening of the oil supply hole 44 is formed on the outer periphery of the shaft 31.

  The cylinder 30 is opened with a suction port 40 for sucking gas into the low pressure side of the compression chamber 39, and the upper bearing 34 discharges gas from the high pressure side of the compression chamber 39 formed by turning from the low pressure side. The discharge port 38 is opened. The discharge port 38 is formed as a circular hole in plan view that penetrates the upper bearing 34. A discharge valve 36 is provided above the discharge port 38 in the upper bearing 34 and is opened when pressure of a predetermined magnitude or more is received from the discharge port 38. A cup muffler 37 is further disposed on the upper bearing 34 so as to cover the discharge valve 36.

  Here, FIG. 3 is a diagram showing a state transition of the compression mechanism unit 3 during one rotation of the shaft 31 shown in FIG. In FIG. 3, the position at which the cylindrical portion 33 a of the vane 33 is closest to the inner wall of the cylinder 30 is defined as 0 degree. In FIG. 3, on the low pressure side, the sliding contact portion between the piston 32 and the cylinder 30 moves away from the suction port 40 while gradually expanding the gas suction chamber when passing through the suction port 40. During this time, gas is sucked from the suction port 40 into the suction chamber. On the other hand, on the high pressure side, the sliding portion of the piston 32 gradually approaches the discharge port 38 while gradually reducing the compression chamber, and when the gas in the compression chamber 39 is compressed to a predetermined pressure or higher, the discharge valve 36 (FIG. 1) opens, and gas flows out from the discharge port 38. The outflowing gas is discharged from the cup muffler 37 shown in FIG. 1 into the high-pressure discharge space 52 inside the sealed container 1, more specifically, outside the compression mechanism unit 3. On the other hand, there are spaces 46 (see FIG. 2) between the inner peripheral surfaces of the eccentric portion 31a, the upper bearing 34, and the piston 32, and between the eccentric portion 31a, the lower bearing 35, and the inner peripheral surfaces of the piston 32. Has a space 47 (see FIG. 2). Oil leaks into the spaces 46 and 47 from the oil hole 41 through the oil supply holes 42 and 43. The spaces 46 and 47 are almost always higher than the pressure inside the compression chamber 39.

FIG. 4 is an exploded perspective view of the piston 32 and the vane 33 shown in FIGS. In FIG. 3, the vane 33 has a columnar portion 33a having a columnar shape at the tip portion. The piston 32 is formed with a cylindrical groove 32a having a diameter substantially the same as the diameter of the cylindrical portion 33a and an arc angle exceeding 180 °. The cylindrical portion 33a is swingably fitted in the groove 32a, and both are connected.

  Here, as shown in FIG. 5, the arc extension line La of the groove 32 a is inside the extension line Lb of the outer peripheral line of the piston 32. If the extension line La is inside the extension line Lb, the arc portion of the groove 32a can be greatly increased. Therefore, the seal width on the high-pressure side and the low-pressure side in the compression chamber 39 is increased, and gas and oil leaks. By reducing, the efficiency of the compressor is improved. Further, when machining the groove 32a of the piston 32, it is possible to first make a hole in the piston 32 and then perform machining other than the arc portion. As a result, the processing accuracy such as roundness and squareness of the arc portion of the groove 32a is improved, the processing cost can be reduced, and the efficiency is improved.

  On the other hand, as shown in FIG. 6, when the extension line La is outside the extension line Lb, the arc portion of the groove 32a is reduced and the seal width is also reduced.

  Preferably, as shown in FIG. 7, the center plane Pb of the cylindrical portion 33 a is brought closer to the high-pressure side of the compression chamber 39 with reference to the center plane Pa of the two side surfaces of the vane 33 in contact with the inner wall of the slot 30 b. Here, in the rolling piston rotary compressor, to avoid contact during movement of the piston 32 and the vane 33 it is necessary to provide a relief portion to either the high pressure side of the relief portion becomes the top clearance volume V . Since the top clearance volume V is re-expanded during gas inhalation, a loss occurs. More specifically, as shown in FIG. 8, if the center plane Pc and the axis X of the cylindrical portion 33 a are aligned or the cylindrical portion 33 a is moved to the low pressure side with respect to the central plane Pa, The top clearance volume V becomes large. On the other hand, as shown in FIG. 7, the cylindrical portion 33a can be made closer to the high pressure side of the compression chamber 39, so that the top clearance volume V on the high pressure side can be reduced. The efficiency of the compressor is improved.

  Moreover, as shown in FIG. 9, it is preferable to provide, for example, a small depression as a mark 33c on either the upper end surface or the lower end surface of the vane 33. Thereby, it becomes a mark which judges the up-down direction at the time of an assembly, and it becomes possible to reduce the loss by an assembly mistake.

Further, the compressor is suitable for use with CO ₂ as the working fluid. CO ₂ has a large differential pressure and a large leakage loss and sliding loss. By adopting the piston 32 and the vane 33 according to this embodiment, the efficiency and reliability of the compressor can be improved more effectively. It becomes.

  In addition, a refrigerant mixed with a hydrofluoroolefin having a double bond between carbon and carbon as a working fluid and having a double bond as a working fluid is used for the compressor. Since this refrigerant does not contain chlorine, the reliability of the sliding portion is very severe. However, by adopting the piston 32 and the vane 33 according to this embodiment, the reliability and efficiency can be improved more effectively. . Furthermore, since it is a refrigerant that does not destroy ozone and has a low global warming potential, it can constitute an air-conditioning cycle that is friendly to the earth.

  The rotary compressor according to the present invention hardly leaks gas or oil from the high pressure side to the low pressure side of the compression chamber, and is suitable for a water heater device, an air conditioner, a refrigerator-freezer, a dehumidifier, and the like.

30 Cylinder 30b Slot 31 Shaft 31a Eccentric part 32 Piston 32a Groove 33 Vane 33a Cylindrical part La Extension line (arc side of groove)
Lb extension line (piston outer circumference side)

Claims (2)

A cylinder,
An eccentric portion of a shaft disposed in the cylinder;
A piston fitted into the eccentric part and formed with a cylindrical groove having an arc angle of more than 180 °;
A vane that is inserted into a slot formed in the cylinder, divides a space in the cylinder into a high-pressure side and a low-pressure side, and has a cylindrical columnar portion that engages with the groove;
A rotary compressor comprising:
Ri inside near the outer periphery line of the arc of extension said piston of said groove, wherein said cylindrical portion is closer to the high-pressure side with respect to the center plane of the two side surfaces of said vane, rotary compressor . The rotary compressor according to claim 1 , wherein a mark is provided on one of the two side surfaces of the vane.