JP2017002734A - Rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary compressor capable of preventing locking of a piston in the case of one-side contact of the piston due to an inclination of a driving shaft.SOLUTION: A rotary compressor includes a piston (28) in which a roller (27) and a blade (100) are integrally provided, and a pair of bushes fastening and supporting the blade (100) from both sides so as to be freely retreated and advanced. The blade (100) has a first protrusion (101) extended toward a distal end side from the roller (27) side on an end plate member (50) side by a first groove (100a) provided on the end plate member (50) side and the distal end side, a second protrusion (102) extended toward a distal end side from the roller (27) side on an end plate member (60) side by a second groove (100b) provided on the end plate member (60) side and the distal end side, and a center portion (103) fastened by the first and the second grooves (100a and 100b) and brought into surface contact with a sliding surface of the bush.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a rotary compressor.

  Conventionally, as a rotary compressor, there is a rotary compressor in which a piston integrally provided with a roller and a blade swings in a cylinder (see, for example, JP-A-7-27074 (Patent Document 1)).

  In the above rotary compressor, the eccentric shaft portion of the drive shaft moves eccentrically, and the piston revolves, and the refrigerant is obtained by repeating the suction process into the low pressure chamber partitioned by the blade in the cylinder and the compression stroke of the high pressure chamber. Gas compression is performed.

JP 7-27074 A

  In the conventional rotary compressor, as shown in the schematic diagram of FIG. 9, when the drive shaft 512 having the eccentric shaft portion 526 is inclined, the end surface of the blade 500 on the head 550 side becomes the face surface 550 a of the head 550. On the other hand, they hit each other (region A2 surrounded by a dotted line shown in FIG. 9). On the other hand, the end surface of the roller 527 opposite to the blade 500 with respect to the drive shaft 512 comes into contact with the face surface 560a of the head 560 (in a region B2 surrounded by a dotted line shown in FIG. 9).

  In the rotary compressor, when the piston 528 in which the roller 527 and the blade 500 are integrally provided is inclined and hits the face surfaces 550a and 560a of the heads 550 and 560, the contact surface pressure between the end surface of the blade 500 and the face surface 550a is reduced. There is a problem in that the piston 528 is locked in a state where the piston 528 is sandwiched between the face surfaces 550a and 560a.

  Accordingly, an object of the present invention is to provide a rotary compressor that can reduce the contact surface pressure between the end face of the blade and the face face of the head when the piston comes into contact with each other due to the inclination of the drive shaft, and can prevent the piston from being locked. It is in.

In order to solve the above problems, the rotary compressor of the present invention is
In the cylinder sandwiched between the first head and the second head, a rotary compressor in which a piston integrally provided with a roller and a blade swings,
It has a pair of bushes that support the blade so that it can be advanced and retracted from both sides,
The blade is
A first protrusion formed on the first head side so as to extend from the roller side toward the front end side by a first groove provided on the first head side and the front end side;
A second protrusion formed on the second head side so as to extend from the roller side toward the front end side by a second groove provided on the second head side and the front end side;
And a central portion that is sandwiched between the first and second groove portions and is in surface contact with the sliding surface of the bush.

  According to the above configuration, the first groove portion is provided on the leading end side of the blade and the first head side, and the second groove portion is provided on the leading end side of the blade and the second head side. A first protrusion extending to the one head side is formed, and a second protrusion extending to the second head side from the roller side toward the tip side is formed. Thus, when the piston tilts with the tilt of the drive shaft and the end surface on the first head side of the first projection portion of the blade comes into contact with the face surface of the first head, the first projection portion of the blade is Since the first groove portions are adjacent to each other, it is possible to elastically deform so as to release the stress received from the face surface of the first head.

  Thereby, the stress which acts on the 1st projection part of a blade from the 1st head side, and the stress which acts on the end surface of the roller on the opposite side to a blade from the 2nd head side can be reduced.

  Furthermore, since at least the central portion of the blade sandwiched between the first and second groove portions and the sliding surface of the bush are in surface contact, the surface pressure at the sliding portion between the blade and the bush can be reduced. The sliding performance between the blade and the bush can be ensured.

  Therefore, the contact surface pressure between the end face of the blade and the face face of the head can be reduced when the piston comes into contact with one side due to the inclination of the drive shaft. Accordingly, it is possible to prevent the piston from being locked between the first and second heads due to the piston being sandwiched between the face surfaces of the first and second heads and the contact portion being seized.

  A similar effect can be obtained when the piston is inclined and the end surface of the second protrusion of the blade on the second head side comes into contact with the face surface of the second head.

Moreover, in the rotary compressor of one embodiment,
The first protrusion of the blade is in surface contact with the sliding surface of the bush;
The second protrusion of the blade is in surface contact with the sliding surface of the bush.

  According to the above embodiment, since the first protrusion and the second protrusion of the blade are in surface contact with the sliding surface of the bush, the surface pressure at the sliding portion between the blade and the bush can be further reduced.

Moreover, in the rotary compressor of one embodiment,
The width of the first and second protrusions of the blade gradually decreases from the roller side toward the tip side.

  According to the above embodiment, the width of the first and second protrusions of the blade gradually decreases from the roller side toward the tip side, and the first head side of the first protrusion and the second protrusion of the second protrusion. When the taper surface is provided on the head side, the allowable tilt angle of the piston can be widened.

  Alternatively, when the width of the first and second protrusions of the blade gradually decreases from the roller side toward the tip side and the width of the first and second groove portions increases toward the tip side, The piston tilts as the shaft tilts, and the elastic deformation of the first protrusion (or second protrusion) of the blade becomes easier, and the contact surface pressure between the end surface of the blade and the face surface of the head can be further reduced. .

Moreover, in the rotary compressor of one embodiment,
The end face on the first head side of the blade including the first protrusion is on the same plane as the end face on the first head side of the roller, and
An end surface on the second head side of the blade including the second protrusion is on the same plane as an end surface on the second head side of the roller,
The groove widths of the first and second groove portions of the blade gradually narrow from the tip side toward the roller side.

  According to the above embodiment, the end face on the first head side of the blade including the first protrusion is flush with the end face on the first head side of the piston, and the second head of the blade including the second protrusion is provided. The end face on the side is flush with the end face on the second head side of the piston, and the groove width of the first and second groove portions of the blade is gradually narrowed from the tip side toward the roller side, so that The contact surface pressure at the time can be made more uniform.

Moreover, in the rotary compressor of one embodiment,
When the piston is at the bottom dead center in the cylinder, the distance from the bush end exposed in the cylinder to the first and second groove portions of the blade is ½ of the width of the blade. That's it.

  According to the above embodiment, when the piston is at the bottom dead center in the cylinder, the distance from the bush end exposed in the cylinder to the first and second groove portions of the blade is ½ or more of the width of the blade. By doing so, the sealing performance between the low pressure chamber and the high pressure chamber in the cylinder defined by the blade can be secured.

Moreover, in the rotary compressor of one embodiment,
In the direction in which the blade extends from the roller, the lengths of the first protrusion and the second protrusion are shorter than the length of the central portion of the blade.

  According to the above embodiment, in the direction in which the blade extends from the roller, the length of the first protrusion and the second protrusion is shorter than the length of the central portion of the blade, so that the sliding portion between the blade and the bush It is possible to widen the allowable tilt angle of the piston while ensuring the sealing performance.

  As is clear from the above, according to the present invention, the first groove portion is provided on the blade tip side and the first head side, and the second groove portion is provided on the blade tip side and the second head side. Forming a first protrusion extending toward the first head toward the tip side and a second protrusion extending toward the second head from the roller side toward the tip side; and first and second groove portions Realizes a rotary compressor that reduces the contact surface pressure between the piston end face and the blade end face due to the tilt of the drive shaft and the face face of the head by bringing the central part sandwiched between the two and the sliding surface of the bush into surface contact. can do.

FIG. 1 is a longitudinal sectional view of a rotary compressor according to a first embodiment of the present invention. FIG. 2 is a plan view of the main part of the compression mechanism of the rotary compressor. FIG. 3 is a side view of a piston composed of rollers and blades of the rotary compressor. FIG. 4 is a schematic view of the main part in a state where the drive shaft of the rotary compressor is tilted. FIG. 5 is a plan view of the main part of the rotary compressor showing the distance from the ends of the first and second groove portions to the bush ends. FIG. 6 is a side view of a piston comprising rollers and blades of a rotary compressor according to a second embodiment of the present invention. FIG. 7 is a side view of a piston comprising rollers and blades of a rotary compressor according to a third embodiment of the present invention. FIG. 8 is a side view of a piston comprising rollers and blades of a rotary compressor according to a fourth embodiment of the present invention. FIG. 9 is a schematic view of a main part in a state where the drive shaft of a conventional rotary compressor is tilted.

  Hereinafter, the rotary compressor of the present invention will be described in detail with reference to the illustrated embodiments.

[First Embodiment]
FIG. 1 is a longitudinal sectional view of a rotary compressor according to a first embodiment of the present invention.

  As shown in FIG. 1, the rotary compressor according to the first embodiment includes a sealed container 1, a compression mechanism unit 2 disposed in the sealed container 1, and a compression mechanism unit 2 disposed in the sealed container 1. And a motor 3 that drives the motor via a drive shaft 12.

  This rotary compressor is a so-called vertical high-pressure dome type rotary compressor, in which a compression mechanism section 2 is disposed on the lower side of the sealed container 1 and a motor 3 is disposed on the upper side of the compression mechanism section 2. doing. The compressor 6 is driven by the rotor 6 of the motor 3 via the drive shaft 12. The motor 3 is an inner rotor type motor.

  The compression mechanism section 2 sucks refrigerant gas from the accumulator 10 through the suction pipe 11. The refrigerant gas is obtained by controlling a condenser, an expansion mechanism, and an evaporator (not shown) that constitute an air conditioner as an example of a refrigeration system together with the rotary compressor. This refrigerant is, for example, carbon dioxide, HFC such as HC and R410A, and HCFC such as R22 and R32.

  The rotary compressor discharges the compressed high-temperature and high-pressure refrigerant gas from the compression mechanism unit 2 to fill the inside of the sealed container 1 and passes the motor 3 through the gap between the stator 5 and the rotor 6 of the motor 3. After cooling, it is discharged from a discharge pipe 13 provided on the upper side of the motor 3 to the outside.

  An oil reservoir 9 in which lubricating oil is stored is formed in the lower portion of the high-pressure region in the closed container 1. The lubricating oil moves from the oil reservoir portion 9 to a sliding portion such as the compression mechanism portion 2 through an oil passage (not shown) provided in the drive shaft 12, and lubricates the sliding portion. . Examples of the lubricating oil include polyalkylene glycol oil (polyethylene glycol, polypropylene glycol, etc.), ether oil, ester oil, mineral oil, and the like.

  The compression mechanism 2 includes a cylinder 21 attached to the inner surface of the sealed container 1, an upper end plate member 50 (front head) and a lower end plate attached to the upper and lower open ends of the cylinder 21. Member 60 (rear head). A cylinder chamber 22 is formed by the cylinder 21, the upper end plate member 50, and the lower end plate member 60. The upper end plate member 50 is an example of a first head, and the lower end plate member 60 is an example of a second head.

  The upper end plate member 50 includes a disk-shaped main body 51 and a boss 52 provided upward in the center of the main body 51. The drive shaft 12 is inserted through the main body 51 and the boss 52.

  The main body 51 is provided with a discharge port 51 a that communicates with the cylinder chamber 22. A discharge valve 31 is attached to the main body 51 so as to be located on the opposite side of the main body 51 from the cylinder 21. The discharge valve 31 is a reed valve, for example, and opens and closes the discharge port 51a.

  A cup-shaped muffler cover 40 is attached to the main body 51 so as to cover the discharge valve 31 on the side opposite to the cylinder 21. The muffler cover 40 is fixed to the main body 51 by bolts 35 or the like. The muffler cover 40 has a boss portion 52 inserted therethrough.

  A muffler chamber 42 is formed by the muffler cover 40 and the upper end plate member 50. The muffler chamber 42 and the cylinder chamber 22 communicate with each other through a discharge port 51a.

  The muffler cover 40 has a hole 43 that communicates the muffler chamber 42 with the outside of the muffler cover 40.

  The lower end plate member 60 includes a disc-shaped main body portion 61 and a boss portion 62 provided downward in the center of the main body portion 61. The drive shaft 12 is inserted through the body portion 61 and the boss portion 62.

  Thus, one end of the drive shaft 12 is supported by the upper end plate member 50 and the lower end plate member 60. That is, the drive shaft 12 is cantilevered. One end portion (support end side) of the drive shaft 12 enters the cylinder chamber 22.

  An eccentric shaft portion 26 is provided on the support end side of the drive shaft 12 so as to be positioned in the cylinder chamber 22 on the compression mechanism portion 2 side. The eccentric shaft portion 26 is fitted to the roller 27 of the piston 28. The piston 28 is disposed so as to be able to revolve in the cylinder chamber 22, and performs a compression action by the revolving motion of the piston 28.

  In other words, one end portion of the drive shaft 12 is supported by the housing 7 of the compression mechanism portion 2 on both sides of the eccentric shaft portion 26. The housing 7 includes an upper end plate member 50 and a lower end plate member 60.

  Next, the compression action of the cylinder 21 of the compression mechanism 2 will be described with reference to FIG. FIG. 2 shows a plan view of the main part of the compression mechanism 2 of the rotary compressor.

  As shown in FIG. 2, the rotary compressor includes a piston 28 in which a roller 27 and a blade 100 are integrally provided, and the piston is placed in a cylinder 21 sandwiched between end plate members 50 and 60 (shown in FIG. 1). 28 swings. The cylinder chamber 22 is partitioned by the blade 100 of the piston 28. That is, in the chamber on the right side of the blade 100, the suction pipe 11 opens on the inner surface of the cylinder chamber 22 to form a suction chamber (low pressure chamber) 22a. On the other hand, the chamber on the left side of the blade 100 has a discharge port 51a (shown in FIG. 1) opened on the inner surface of the cylinder chamber 22 to form a discharge chamber (high pressure chamber) 22b.

  A pair of semi-cylindrical bushes 25, 25 are in close contact with both side surfaces of the blade 100 for sealing. The blade 100 and the bushes 25, 25 are lubricated with lubricating oil. The bush 100 is supported by the bushes 25 so that the blade 100 can be advanced and retracted from both sides. The blade 100 appears and disappears in a back space 110 provided in the cylinder 21.

  The eccentric shaft portion 26 rotates eccentrically with the drive shaft 12, and the roller 27 fitted to the eccentric shaft portion 26 revolves while the outer peripheral surface of the roller 27 is in contact with the inner peripheral surface of the cylinder chamber 22.

  As the roller 27 revolves in the cylinder chamber 22, the blade 100 moves forward and backward with both side surfaces of the blade 100 being supported by the bushes 25 and 25. As a result, a low-pressure refrigerant gas is sucked into the suction chamber 22a from the suction pipe 11 and compressed to a high pressure in the discharge chamber 22b, and then the high-pressure refrigerant gas is discharged from the discharge port 51a (shown in FIG. 1).

  Thereafter, as shown in FIG. 1, the refrigerant gas discharged from the discharge port 51 a is discharged to the outside of the muffler cover 40 via the muffler chamber 42.

  FIG. 3 shows a side view of the piston 28 composed of the roller 27 and the blade 100 of the rotary compressor. In FIG. 3, 27 a is a shaft hole into which the eccentric shaft portion 26 of the drive shaft 12 is inserted.

  As shown in FIG. 3, the blade 100 is provided with a first groove portion 100a provided on the tip side and on the end plate member 50 (first head) side shown in FIG. Thereby, the 1st projection part 101 extended in the end-plate member 50 side toward the front end side from the roller 27 side is formed.

  Further, the blade 100 is provided with a second groove portion 100b provided on the tip side and on the end plate member 60 (second head) side shown in FIG. Thereby, the 2nd projection part 102 extended in the end-plate member 60 side toward the front end side from the roller 27 side is formed.

  Both side surfaces of the central portion 103 sandwiched between the first and second groove portions 100a and 100b are in surface contact with the sliding surfaces of the bushes 25 and 25 (shown in FIG. 2).

  Further, both side surfaces of the first protrusion 101 of the blade 100 are in surface contact with the sliding surfaces of the bushes 25 and 25, and both side surfaces of the second protrusion 102 of the blade 100 are in contact with the sliding surfaces of the bushes 25 and 25. In contact.

  The end surface on the end plate member 50 side of the blade 100 including the first protrusion 101 is flush with the end surface on the end plate member 50 side of the piston 28, and the blade 100 including the second protrusion 102 is included in the blade 100. The end surface on the end plate member 60 side is flush with the end surface of the piston 28 on the end plate member 60 side. Furthermore, the groove width (the width in the axial direction of the roller 27) of the first and second groove portions 100a and 100b of the blade 100 is constant.

  In FIG. 3, the dimensions of each part are different from the actual dimensions in order to make the drawing easier to understand.

  FIG. 4 shows a schematic view of the main part of the rotary compressor with the drive shaft 12 tilted. As shown in FIG. 4, the drive shaft 12 is inclined and the end surface of the first protrusion 101 of the blade 100 on the end plate member 50 side comes into contact with the face surface 50a of the end plate member 50 (shown in FIG. 4). Region A1) surrounded by a dotted line. On the other hand, the end surface of the roller 27 opposite to the blade 100 with respect to the drive shaft 12 comes into contact with the face surface 60a of the end plate member 60 (region B1 surrounded by a dotted line shown in FIG. 4).

  At this time, the first protrusion 101 of the blade 100 can be elastically deformed by the stress received from the face surface 50a of the end plate member 50 due to the presence of the first groove 100a. Thereby, the stress which acts on the 1st projection part 101 of the blade 100 from the end plate member 50, and the stress which acts on the end surface of the roller 27 on the opposite side to the blade 100 from the end plate member 60 can be reduced.

  According to the rotary compressor configured as described above, the first groove portion 100a is provided on the front end side of the blade 100 and the end plate member 50 (first head) side, and the front end side of the blade 100 and the end plate member 60 (second head). By providing the second groove portion 100b on the side, the first protrusion 101 extending from the roller 27 side toward the tip end side toward the end plate member 50 side is formed, and the end plate from the roller 27 side toward the tip end side is formed. A second projecting portion 102 extending to the member 60 side is formed. Accordingly, when the piston 28 is inclined with the inclination of the drive shaft 12 and the end surface on the end plate member 50 side of the first protrusion 101 of the blade 100 is in contact with the face surface 50a of the end plate member 50, The first protrusion 101 of the blade 100 can be elastically deformed so as to release the stress received from the face surface 50a of the end plate member 50 due to the adjacent first groove 100a. Here, the inclination of the drive shaft 12 depends on the accuracy of assembly of the compression mechanism unit 2 and the like and the pressure acting from the discharge chamber (high pressure chamber) 22b formed in the cylinder chamber 22 toward the suction chamber (low pressure chamber) 22a. Arise.

  Thereby, the stress which acts on the 1st projection part 101 of the braid | blade 100 from the end plate member 50 side can be reduced. Accordingly, stress acting on the end surface of the roller on the side opposite to the blade 100 from the end plate member 60 side can also be reduced.

  Further, since both side surfaces of the central portion 103 sandwiched between the first and second groove portions 100a, 100b of the blade 100 and the sliding surfaces of the bushes 25, 25 are in surface contact, the blade 100 and the bushes 25, 25 are in contact with each other. The surface pressure at the sliding portion can be made uniform, and sealing performance can be secured.

  Therefore, the contact surface pressure between the end surface of the blade 100 and the face surfaces 50a, 60a of the end plate members 50, 60 can be reduced when the piston 28 comes into contact with each other due to the inclination of the drive shaft 12. As a result, the piston 28 is sandwiched between the face surface 50a of the end plate member 50 and the face surface 60a of the end plate member 60, and the contact portion is seized so that the piston 28 is locked between the face surfaces 50a and 60a. Can be prevented.

  The same effect can be obtained when the piston 28 is inclined and the end surface on the end plate member 60 side of the second protrusion 102 of the blade 100 comes into contact with the face surface 60 a of the end plate member 60.

  Further, since both side surfaces of the first projecting portion 101 of the blade 100 and both side surfaces of the second projecting portion 102 are in surface contact with the sliding surfaces of the bushes 25, 25, the sliding portion between the blade 100 and the bushing is in contact. The surface pressure can be further reduced.

  Further, the width of the first and second protrusions 101 and 102 of the blade 100 (the width in the axial direction of the roller 27) gradually decreases from the roller 27 side toward the tip end side, so that the end of the first protrusion 101 In the case where the plate member 50 side and the end plate member 60 side of the second protrusion 102 have a tapered surface, the allowable inclination angle of the piston 28 can be widened.

  Alternatively, the width of the first and second protrusions 101 and 102 of the blade 100 (the width in the axial direction of the roller 27) gradually decreases from the roller 27 side toward the tip end side, so that the first and second groove portions 100a, When the width of 100b becomes wider toward the front end side, the piston 28 is inclined with the inclination of the drive shaft 12, and the first protrusion 101 (or the second protrusion 102) of the blade 100 is elastically deformed. It becomes easier.

  FIG. 5 is a plan view of the main part of the rotary compressor showing the distance from the ends of the first and second groove portions 100a and 100b to the ends of the bushes 25 and 25. FIG.

  When the piston 28 is at the bottom dead center position in the cylinder 21, the distance δ from the ends of the bushes 25, 25 exposed in the cylinder 21 to the first and second groove portions 100 a, 100 b of the blade 100 is defined as the blade 100. It is set to 1/2 or more of the width W.

  As a result, a sealing property between the suction chamber (low pressure chamber) 22a and the discharge chamber (high pressure chamber) 22b in the cylinder 21 defined by the blade 100 can be secured.

[Second Embodiment]
FIG. 6 shows a side view of a piston 228 comprising a roller 27 and a blade 200 of a rotary compressor according to a second embodiment of the present invention. The rotary compressor according to the second embodiment has the same configuration as that of the rotary compressor according to the first embodiment except for the blade 200, and FIGS.

  As shown in FIG. 6, a piston 228 in which the roller 27 and the blade 200 are integrally provided is configured. The blade 200 of the piston 228 is provided with a first groove portion 200a provided on the tip side and on the end plate member 50 (first head) side shown in FIG. Thereby, the 1st projection part 201 extended from the roller 27 side toward the end plate member 50 side toward the front end side is formed.

  Further, the blade 200 is provided with a second groove portion 200b provided on the tip side and on the end plate member 60 (second head) side shown in FIG. Thereby, the 2nd projection part 202 extended in the end plate member 60 side toward the front end side from the roller 27 side is formed.

  The first protrusion 201 is provided with a tapered surface 201a on the end plate member 50 side. Further, the second protrusion 202 is provided with a tapered surface 202a on the end plate member 60 side.

  Both side surfaces of the central portion 203 sandwiched between the first and second groove portions 200a and 200b are in surface contact with the sliding surfaces of the bushes 25 and 25 (shown in FIG. 2).

  Further, both side surfaces of the first protrusion 201 of the blade 200 are in surface contact with the sliding surfaces of the bushes 25 and 25, and both side surfaces of the second protrusion 202 of the blade 200 are in contact with the sliding surfaces of the bushes 25 and 25. In contact.

  In the schematic diagram of FIG. 6, the dimensions of each part are different from the actual dimensions in order to make the drawing easy to understand.

  The rotary compressor of the second embodiment has the same effect as the rotary compressor of the first embodiment.

  Further, the width of the first and second protrusions 201 and 202 of the blade 200 gradually becomes narrower from the roller 27 side toward the tip end side, and the end plate member 50 side and the second protrusion part of the first protrusion 201. Since the taper surfaces 201a and 202a are provided on the end plate member 60 side of 202, the allowable inclination angle of the piston 228 can be widened.

[Third Embodiment]
FIG. 7 shows a side view of a piston 328 composed of a roller 27 and a blade 300 of a rotary compressor according to a third embodiment of the present invention. The rotary compressor according to the third embodiment has the same configuration as that of the rotary compressor according to the first embodiment except for the blade 300, and FIGS.

  As shown in FIG. 7, a piston 328 in which the roller 27 and the blade 300 are integrally provided is configured. The blade 300 of the piston 328 is provided with a first groove portion 300a provided on the tip side and on the end plate member 50 (first head) side shown in FIG. Thereby, the 1st projection part 301 extended in the end plate member 50 side toward the front end side from the roller 27 side is formed.

  Further, the blade 300 is provided with a second groove portion 300b provided on the tip side and on the end plate member 60 (second head) side shown in FIG. Thereby, the 2nd projection part 302 extended in the end plate member 60 side toward the front end side from the roller 27 side is formed.

  The groove widths of the first and second groove portions 300a and 300b are gradually narrowed from the front end side toward the roller 27 side. Here, the end surface of the blade 300 including the first protrusion 301 on the first head 50 side is flush with the end surface of the piston 28 on the end plate member 50 side, and the blade 300 including the second protrusion 302 is included in the same plane. The end face on the second head 60 side is flush with the end face on the end plate member 60 side of the piston 28.

  Both side surfaces of the central portion 303 sandwiched between the first and second groove portions 300a and 300b are in surface contact with the sliding surfaces of the bushes 25 and 25 (shown in FIG. 2).

  Further, both side surfaces of the first protrusion 301 of the blade 300 are in surface contact with the sliding surfaces of the bushes 25 and 25, and both side surfaces of the second protrusion 302 of the blade 300 are in contact with the sliding surfaces of the bushes 25 and 25. In contact.

  In the schematic diagram of FIG. 7, the dimensions of each part are different from the actual dimensions in order to make the drawing easier to understand.

  The rotary compressor of the third embodiment has the same effect as the rotary compressor of the first embodiment.

  Further, the width of the first and second protrusions 301 and 302 of the blade 300 (the width in the axial direction of the roller 27) gradually decreases from the roller 27 side toward the tip side, and the first and second groove portions 300a. , 300b becomes wider toward the distal end side, the piston 328 is inclined as the drive shaft 12 is inclined, and the first protrusion 301 (or the second protrusion 302) of the blade 300 is elastically deformed. The contact surface pressure between the end surface of the blade 300 and the face surfaces 50a, 60a of the end plate members 50, 60 can be further reduced, and the surface pressure at the sliding portion between the blade 300 and the bushes 25, 25 can be reduced. Can be reduced.

  Further, the end surface of the blade 300 including the first protrusion 301 on the end plate member 50 side is flush with the end surface of the piston 328 on the end plate member 50 side, and the blade 300 including the second protrusion 302 is included in the blade 300. The end surface on the end plate member 60 side is flush with the end surface on the end plate member 60 side of the piston 328, and the groove widths of the first and second groove portions 300a and 300b of the blade 300 are changed from the tip side to the roller 27 side. It is narrowing gradually. As a result, the contact surface pressure at the time of contact can be made uniform.

[Fourth Embodiment]
FIG. 8 shows a side view of a piston 428 composed of a roller 27 and a blade 400 of a rotary compressor according to a fourth embodiment of the present invention. The rotary compressor according to the fourth embodiment has the same configuration as that of the rotary compressor according to the first embodiment except for the blade 400, and FIGS.

  As shown in FIG. 8, a piston 428 in which the roller 27 and the blade 400 are provided integrally is configured. The blade 400 of the piston 428 is provided with a first groove portion 400a provided on the tip side and on the end plate member 50 (first head) side shown in FIG. Thereby, the 1st projection part 401 extended in the end plate member 50 side toward the front end side from the roller 27 side is formed.

  Further, the blade 400 is provided with a second groove 400b provided on the tip side and on the end plate member 60 (second head) side shown in FIG. Thereby, the 2nd projection part 402 extended in the end-plate member 60 side toward the front end side from the roller 27 side is formed.

  Both side surfaces of the central portion 403 sandwiched between the first and second groove portions 400a and 400b are in surface contact with the sliding surfaces of the bushes 25 and 25 (shown in FIG. 2).

  Further, both side surfaces of the first protrusion 401 of the blade 400 are in surface contact with the sliding surfaces of the bushes 25 and 25, and both side surfaces of the second protrusion 402 of the blade 400 are in contact with the sliding surfaces of the bushes 25 and 25. In contact.

  In the direction in which the blade 400 extends from the roller 27, the length L 2 of the first protrusion 401 and the second protrusion 402 is shorter than the length L 1 of the central portion 403 of the blade 400.

  In the schematic diagram of FIG. 8, the dimensions of each part are different from the actual dimensions in order to make the drawing easier to understand.

  The rotary compressor of the fourth embodiment has the same effect as the rotary compressor of the first embodiment.

  In addition, in the direction in which the blade 400 extends from the roller, the length L2 of the first protrusion 401 and the second protrusion 402 is shorter than the length L1 of the central portion 403 of the blade 400, so that the blade 400 and the bush The tilt allowable angle of the piston 428 can be widened while ensuring the sealing performance at the sliding portion between 25 and 25.

  In the said 4th Embodiment, although the length of the 1st projection part 401 and the 2nd projection part 402 was made the same, the length of a 1st projection part and a 2nd projection part does not need to be the same.

  In the first to fourth embodiments, both side surfaces of the first protrusions 101, 201, 301, 401 of the blades 100, 200, 300, 400 are in surface contact with the sliding surfaces of the bushes 25, 25, and the blade 100 , 200, 300, 400, both side surfaces of the second projections 102, 202, 302, 402 are in surface contact with the sliding surfaces of the bushes 25, 25, but both side surfaces of the first and second projections of the blade May not be in surface contact with the sliding surface of the bush. Even in this case, the contact surface pressure between the end surface of the blade and the face surfaces of the first and second heads can be reduced when the piston comes into contact with each other due to the inclination of the drive shaft.

  In the first to fourth embodiments, both side surfaces of the central portions 103, 203, 303, 403 of the blades 100, 200, 300, 400 and the sliding surfaces of the bushes 25, 25 are in surface contact. The present invention may be applied to a rotary compressor having a configuration in which both side surfaces of the central portion of the blade do not simultaneously contact the sliding surface of the bush.

  Similarly, the present invention may be applied to a rotary compressor having a configuration in which both side surfaces of the first and second protrusions of the blade do not simultaneously contact the sliding surface of the bush.

  Moreover, although the 1st-4th embodiment demonstrated the rotary compressor of 1 cylinder structure, you may apply this invention to the rotary compressor of 2 cylinder structure.

  Although specific embodiments of the present invention have been described, the present invention is not limited to the first to fourth embodiments, and various modifications can be made within the scope of the present invention. For example, what combined suitably the content described in the said 1st-4th embodiment is good also as one Embodiment of this invention.

DESCRIPTION OF SYMBOLS 1 ... Sealed container 2 ... Compression mechanism part 3 ... Motor 5 ... Stator 6 ... Rotor 7 ... Housing 9 ... Oil reservoir part 10 ... Accumulator 11 ... Suction pipe 12 ... Drive shaft 13 ... Discharge pipe 21 ... Cylinder 22 ... Cylinder chamber 22a ... Suction chamber (low pressure chamber)
22b ... Discharge chamber (high pressure chamber)
25 ... Bush 26 ... Eccentric shaft 27 ... Rollers 28, 228, 328, 428 ... Piston 31 ... Discharge valve 35 ... Bolt 40 ... Muffler cover 42 ... Muffler chamber 43 ... Hole 50 ... End plate member 50a ... Face surface 51 ... Body portion 51a ... Discharge port 52 ... Boss portion 60 ... End plate member 60a ... Face surface 61 ... Body portion 62 ... Boss portion 100, 200, 300, 400 ... Blade 100a, 200a, 300a, 400a ... First groove portion 100b, 200b , 300b, 400b ... second groove 101, 201, 301, 401 ... first protrusion 102, 202, 302, 402 ... second protrusion 103, 203, 303, 403 ... central part 201a ... taper surface 202a ... taper surface

Claims (6)

In a cylinder (21) sandwiched between the first head (50) and the second head (60), a piston (28,228) in which a roller (27) and a blade (100,200,300,400) are integrally provided. , 328, 428) are oscillating rotary compressors,
A pair of bushes (25, 25) supporting the blade (100, 200, 300, 400) from both sides so as to be able to advance and retreat;
The blade (100, 200, 300, 400)
The first groove (100a, 200a, 300a, 400a) provided on the first head (50) side and the front end side causes the first head (50) side to move toward the front end side from the roller (27) side. A first protrusion (101, 201, 301, 401) formed to extend;
The second groove (100b, 200b, 300b, 400b) provided on the second head (60) side and the front end side causes the second head (60) side to move toward the front end side from the roller (27) side. A second protrusion (102, 202, 302, 402) formed to extend;
A central part (103, 203, which is sandwiched between the first and second groove parts (100a, 200a, 300a, 400a, 100b, 200b, 300b, 400b) and is in surface contact with the sliding surface of the bush (25, 25). 303, 403). The rotary compressor according to claim 1.
The first protrusion (101, 201, 301, 401) of the blade (100, 200, 300, 400) is in surface contact with the sliding surface of the bush (25, 25);
A rotary characterized in that the second protrusion (102, 202, 302, 402) of the blade (100, 200, 300, 400) is in surface contact with the sliding surface of the bush (25, 25). Compressor. The rotary compressor according to claim 1 or 2,
The width of the first and second protrusions (201, 301, 202, 302) of the blade (200, 300) is gradually narrowed from the roller (27) side toward the tip side. Rotary compressor. The rotary compressor according to claim 3,
The end surface of the blade (300) including the first protrusion (301) on the first head (50) side is flush with the end surface of the roller (27) on the first head (50) side. With
The end surface of the blade (300) including the second protrusion (302) on the second head (60) side is flush with the end surface of the roller (27) on the second head (60) side. ,
The rotary compressor according to claim 1, wherein the first and second groove portions (300a, 300b) of the blade (300) are gradually narrowed from the tip side toward the roller (27) side. In the rotary compressor according to any one of claims 1 to 4,
When the piston (28, 228, 328, 428) is at the bottom dead center position in the cylinder (21), the blade (25, 25) is exposed from the end of the bush (25, 25) exposed in the cylinder (21). 100, 200, 300, 400) to the first and second groove portions (100a, 200a, 300a, 400a, 100b, 200b, 300b, 400b) of the blade (100, 200, 300, 400) A rotary compressor having a width of 1/2 or more. In the rotary compressor according to any one of claims 1 to 5,
In the direction in which the blade (400) extends from the roller (27), the length of the first protrusion (401) and the second protrusion (402) is set to the central portion (403) of the blade (400). Rotary compressor characterized in that it is shorter than the length of.

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