JP2011032933A - Rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent the deformation of a pump blade at assembling, and to enhance assembling performance in a rotary compressor. <P>SOLUTION: An oil supply mechanism 14 is provided for supplying lubricating oil reserved at a lower portion of a compressor casing 11 through an oil supply port 100 of a rotary shaft 33 to a sliding portion of a compression section 12. The oil supply mechanism 14 is constituted of an accommodation hole 101 which is formed at a lower end of a rotary shaft 33 and communicates with the oil supply port 100, a pump case 102 having a lubricating oil suction hole 106 at its lower end, opened at an upper end, and mounted to the accommodation hole 101, and a pump blade 103 formed in a plate shape, accommodated in the accommodation hole 101 and the pump case 102 where a widened portion 107 formed at an intermediate portion in a longitudinal direction is latched to an inner surface of top of the pump case 102. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a rotary compressor used in an air conditioner, a refrigerator, and the like, and more particularly to a lubricant supply mechanism that lubricates bearings and the like.

  In a conventional rotary compressor, a motor is arranged at the upper part in a sealed container, and a compression unit that is operated by this motor is arranged at the lower part. The compression portion is a cylinder having a suction port and a discharge port, an annular piston that is mounted on an eccentric portion of the rotating shaft of the motor to form a working chamber whose volume increases and decreases, and projects from and into the working chamber. Thus, the vane is configured to come into contact with the piston and divide the working chamber into a suction chamber and a compression chamber.

  Therefore, when the rotating shaft is rotated by the motor, the annular piston revolves in the cylinder through the eccentric portion, the gas refrigerant is sucked into the working chamber from the suction port, and the volume of the working chamber is reduced, so that the gas refrigerant is When compressed and reaches a predetermined pressure, the compressed gas refrigerant is discharged from the discharge port, becomes high-pressure refrigerant, passes through the gap of the motor, and is discharged from the sealed container to the outside.

  In such a rotary compressor, lubricating oil is stored in the lower part of the hermetic container, and the lubricating oil is pumped up by an oil supply mechanism and supplied to the compression unit for lubrication. As this oil supply mechanism, there exists a thing described in the following patent document 1, for example. The oil supply device for a vertical compressor described in Patent Document 1 has a hollow hole formed in the center of a crankshaft, and a torsion pump blade for sucking lubricating oil is inserted into the hollow hole. A widened portion having a width larger than the inner diameter of the hollow hole is formed in the portion. Therefore, when the torsion pump blade is inserted into the hollow hole of the crankshaft, the widened portion is pressed against the inner wall of the hollow hole and can be fixed securely.

Japanese Utility Model Publication No. 06-049791

  In the above-described conventional vertical compressor oiling device, a torsion pump blade is first inserted into the hollow hole of the crankshaft, and then a pump case is inserted to cover the torsion pump blade. Yes. In this case, the widened portion of the torsion pump blade is in contact with the stepped portion of the crankshaft, and the upper end portion of the pump case is in contact with the widened portion of the widened portion of the torsion pump blade. That is, when the pump case is inserted into the hollow hole of the crankshaft, the upper end portion of the pump case twists and strongly presses the widened portion of the pump blade, and the twisted pump blade (widened portion) may be deformed. There is.

  The present invention solves the above-described problems, and an object of the present invention is to provide a rotary compressor that can improve the assembly by preventing the deformation of the pump blades during the assembly.

  In order to achieve the above object, a rotary compressor according to the present invention includes a compressor housing having a hollow shape provided with a refrigerant suction portion and a discharge portion, and the suction portion provided at a lower portion of the compressor housing. A compressor that compresses the refrigerant sucked from the motor, a motor that is provided at an upper part of the compressor casing and drives the compressor via a rotation shaft, and a lubricating oil that is stored at the lower part of the compressor casing. An oil supply mechanism that supplies oil to a sliding portion of the compression portion through an oil supply hole of the rotary shaft. The oil supply mechanism opens at a lower end portion of the rotary shaft and communicates with the oil supply hole. A hole, a pump case having a lubricating oil suction hole at the lower end and having an upper end opened to be mounted in the receiving hole, and a plate shape that is accommodated in the receiving hole and the pump case and is long The widened portion formed in the middle part of the direction And a pump blade to be locked in the upper inner surface of Pukesu, it is characterized in.

  In the rotary compressor according to the present invention, the pump blade is positioned by contacting an inner surface of the pump case with an end portion accommodated in the pump case in the longitudinal direction.

  In the rotary compressor of the present invention, the pump blade is characterized in that an end portion accommodated in the accommodation hole in the longitudinal direction is separated from an inner surface of the accommodation hole.

  In the rotary compressor according to the present invention, the widened portion is formed with a convex portion in which an intermediate portion in the longitudinal direction of the pump blade protrudes in one or both of the width directions, so that the width is equal to or larger than the inner diameter of the pump case. It is characterized by having.

  In the rotary compressor according to the present invention, the pump blade is characterized in that an inclined portion is formed between a side portion and the convex portion.

  In the rotary compressor according to the present invention, the pump blade is twisted by a predetermined angle in the circumferential direction, and is made of a material that can be elastically deformed in the twist direction.

  The rotary compressor according to the present invention is characterized in that the pump case is deformable at least in a radial direction.

  According to the rotary compressor of the present invention, the compression unit is disposed at the lower part of the compressor housing, the motor for driving the compression unit via the rotating shaft is disposed at the upper part, and stored in the lower part of the compressor housing. As an oil supply mechanism that supplies lubricating oil to the sliding part of the compression part through the oil supply hole of the rotating shaft, it has a receiving hole that opens at the lower end of the rotating shaft and communicates with the oil supply hole, and a lubricating oil suction hole at the lower end. The upper end of the pump case and the widened portion formed in the middle portion in the longitudinal direction and having a plate shape and accommodated in the accommodation hole and the pump case. And a pump blade that is locked to the front end. Therefore, since the pump blade is locked to the upper inner surface of the pump case, when the pump blade or the pump case is mounted in the accommodation hole of the rotating shaft, the deformation of the pump blade can be prevented to improve the assembling property. it can.

FIG. 1 is a longitudinal sectional view showing a rotary compressor according to an embodiment of the present invention. FIG. 2 is a cross-sectional view taken along the line II-II in FIG. 1 showing a compression unit in the rotary compressor of the present embodiment. FIG. 3 is a cross-sectional view showing an oil supply mechanism in the rotary compressor of the present embodiment. 4 is a cross-sectional view taken along the line IV-IV in FIG. 3 showing an oil supply mechanism in the rotary compressor of the present embodiment. FIG. 5 is a front view showing a pump blade before twisting. FIG. 6 is a front view showing the pump blade after twisting.

  Exemplary embodiments of a rotary compressor according to the present invention will be explained below in detail with reference to the accompanying drawings. In addition, this invention is not limited by this Example.

  1 is a longitudinal sectional view showing a rotary compressor according to an embodiment of the present invention, FIG. 2 is a sectional view taken along the line II-II in FIG. 1 showing a compression section in the rotary compressor of the embodiment, and FIG. 4 is a sectional view showing an oil supply mechanism in the rotary compressor of this embodiment, FIG. 4 is a sectional view taken along the line IV-IV in FIG. 3 showing an oil supply mechanism in the rotary compressor of this embodiment, and FIG. FIG. 6 is a front view showing the pump blade, and FIG. 6 is a front view showing the pump blade after twisting.

  As shown in FIGS. 1 and 2, the rotary compressor of the present embodiment includes a compressor housing 11, a compression unit 12, a motor 13, and an oil supply mechanism 14. That is, the compressor housing 11 is configured as a sealed container having a hollow shape in which a lid portion 22 is fixed to an upper portion of a cylindrical main body 21 and a bottom portion 23 is fixed to a lower portion. The compression part 12 is arrange | positioned at the lower part of this compressor housing | casing 11, and can compress the inhaled gas refrigerant | coolant and can discharge it as a high pressure refrigerant | coolant.

  The motor 13 is disposed on the upper portion of the compressor housing 11 and includes a stator 31 and a rotor 32. In this case, the stator 31 is fixed by being shrink-fitted on the inner peripheral surface of the compressor housing 11. On the other hand, the rotor 32 is disposed at a central portion of the stator 31 with a predetermined gap, and is fixed by being shrink-fitted to the rotating shaft 33. The rotation shaft 33 extends downward and is mechanically connected to the compression unit 12. The compression unit 12 can be driven by the motor 13 via the rotation shaft 33.

  The oil supply mechanism 14 supplies lubricating oil stored in the lower part of the compressor housing 11 to a sliding portion of the compression unit 12 through an oil supply hole described later of the rotary shaft 33, and functions as an oil supply pump.

  Here, the compression unit 12 will be described in detail. The compression unit 12 includes a first compression unit 41 located on the upper side and a second compression unit 51 located on the lower side. The first compression unit 41 and the second compression unit 51 are substantially the same. It is arranged to be stacked side by side up and down.

  In the first compression section 41, a first cylinder 42 having a short cylindrical shape is disposed on the outer peripheral side, and the first cylinder 42 has a circular first concentric with the motor 13 and the rotation shaft 33. A cylinder inner wall 42a is formed. An annular first annular piston 43 having an outer diameter smaller than the cylinder inner diameter is disposed in the first cylinder 42 (first cylinder inner wall 42 a), and the first cylinder inner wall 42 a and the first annular piston 43 A first working chamber 44 (compression space) is formed between the first piston outer wall 43a and capable of sucking and compressing the refrigerant and discharging the compressed refrigerant.

  A first vane groove 45 is formed in the first cylinder 42 along the radial direction from the first cylinder inner wall 42a and over the entire cylinder height, and a flat plate-shaped first vane groove 45 is formed in the first vane groove 45. One vane 46 is fitted. The first vane 46 is urged and supported in a direction in which the first vane 46 protrudes into the first working chamber 44 by a first spring (not shown) mounted in the inner part of the first vane groove 45.

  Accordingly, the first vane 46 is normally urged in the direction protruding from the first vane groove 45 to the first working chamber 44 by the urging force of the first spring, and the tip thereof is the outer periphery of the first annular piston 43. It is in contact with the surface. Therefore, the first working chamber 44 is divided into a first suction chamber 44a and a first compression chamber 44b by the first vane 46.

  Further, the back of the first cylinder 42 communicates the back of the first vane groove 45 and the inside of the compressor housing 11 and applies a back pressure to the first vane 46 by the pressure of the compressed refrigerant. A pressure introduction path 47 is formed. Further, the first cylinder 42 is provided with a first suction hole 48 that allows the first suction chamber 44a to communicate with the outside in order to suck the refrigerant from the outside into the first suction chamber 44a.

  On the other hand, in the second compression section 51, similarly to the first compression section 41, a second cylinder 52 having a short cylindrical shape is disposed on the outer peripheral side. The second cylinder 52 includes the motor 13 and the rotation. A circular second cylinder inner wall concentric with the shaft 33 is formed. An annular second annular piston 53 having an outer diameter smaller than the cylinder inner diameter is disposed in the second cylinder 52 (second cylinder inner wall), and the second cylinder inner wall and the second annular piston 53 secondly are arranged. Between the piston outer wall, a second working chamber 54 (compression space) that sucks and compresses the refrigerant and discharges the compressed refrigerant is defined.

  A second vane groove (not shown) is formed in the second cylinder 52 along the radial direction from the inner wall of the second cylinder and over the entire cylinder height, and a flat plate shape is formed in the second vane groove. A second vane (not shown) is fitted. The second vane is urged and supported in a direction in which the second vane protrudes into the second working chamber 54 by a second spring (not shown) mounted in the inner part of the second vane groove.

  Therefore, the second vane is normally urged in the direction protruding from the second vane groove to the second working chamber 54 by the urging force of the second spring, and the tip thereof is directed to the outer peripheral surface of the second annular piston 53. It is in contact. Therefore, the second working chamber 54 is partitioned into a second suction chamber 54a and a second compression chamber 54b by the second vane.

  Although not shown, the back of the second vane groove and the inside of the compressor housing 11 are communicated with the second cylinder 52, and a back pressure is applied to the second vane by the pressure of the compressed refrigerant. A back pressure introduction path is formed. Further, the second cylinder 52 is provided with a second suction hole that allows the second suction chamber 54a to communicate with the outside in order to allow the second suction chamber 54a to suck the refrigerant from the outside.

  In the compression unit 12 described above, an intermediate partition plate 61 is provided between the first cylinder 42 and the second cylinder 52 so that the first compression unit 41 and the second compression unit 51 operate independently of each other. Has been placed. The intermediate partition 61 partitions the first working chamber 44 and the second working chamber 54 so as to partition each other. In addition, an upper end plate 62 is disposed above the first cylinder 42 and closes the first working chamber 44. On the other hand, a lower end plate 63 is disposed below the second cylinder 52 and closes the second working chamber 54.

  In this case, the upper end plate 62, the first cylinder 42, the intermediate partition plate 61, the second cylinder 52, and the lower end plate 63 are laminated from the top to the bottom, and are integrally fixed by a fixing bolt (not shown). The outer peripheral portion of the upper end plate 62 is fitted and fixed to the inner peripheral portion of the compressor casing 11.

  An upper bearing 62a is formed at the center of the upper end plate 62, and the rotary shaft 33 is rotatably supported by the upper bearing 62a. The lower end plate 63 has a lower bearing portion 63a formed at the center thereof, and the rotary shaft 33 is rotatably supported by the lower bearing portion 63a. The upper end plate 62 has a plurality of through holes 62b having an arc long hole shape formed in the outer peripheral portion at equal intervals in the circumferential direction. Each of the through holes 62b is a hole through which the lubricating oil mixed with the refrigerant in the compression unit 12 and blown to the upper portion of the compressor housing 11 is separated from the refrigerant and returned to the lower portion of the compressor housing 11. .

  The rotary shaft 33 is provided with a first eccentric portion 64 and a second eccentric portion 65 that are eccentric with a phase shifted by 180 ° from each other on the tip end side (lower end portion side). The first eccentric portion 64 is slidably fitted inside the first annular piston 43 of the first compression portion 41 and is rotatable. The second eccentric portion 65 is slidably fitted inside the second annular piston 53 of the second compression portion 51 and is rotatable.

  Therefore, when the rotating shaft 33 rotates, the first and second eccentric portions 64 and 65 rotate integrally, and the first and second annular pistons 43 and 53 are rotated via the first and second eccentric portions 64 and 65. Rotate and revolve. That is, when the rotating shaft 33 rotates in the clockwise direction in FIG. 2, the first eccentric portion 64 rotates in the same direction while sliding with the first annular piston 43. As the piston outer wall 43a rolls on the first cylinder inner wall 42a, it rotates counterclockwise in FIG. 2 and revolves clockwise in FIG. Similarly, when the rotating shaft 33 rotates, the second eccentric portion 65 also rotates in the same direction, and the second annular piston 53 rotates and revolves.

  When the first and second annular pistons 43 and 53 rotate and revolve, the first vane 46 and the second vane (not shown) reciprocate following the operation of the first and second annular pistons 43 and 53. Therefore, by the operation of the first and second annular pistons 43 and 53, the volumes of the first suction chamber 44a, the second suction chamber 54a, the first compression chamber 44b, and the second compression chamber 54b change continuously, and the first The second compression units 41 and 51 can continuously suck and compress the refrigerant and discharge the compressed refrigerant.

  An upper muffler cover 66 is fixed to an upper portion of the upper end plate 62, and an upper muffler chamber 67 is formed between the upper end plate 62 and the upper muffler cover 66. The upper end plate 62 is formed with a first discharge hole 68 communicating with the first compression chamber 44b of the first cylinder 42 and the upper muffler chamber 67. The first discharge hole 68 has a compressed refrigerant flow. A first discharge valve 69 that prevents backflow is provided. The upper muffler chamber 67 reduces the pressure pulsation of the discharged refrigerant.

  A lower muffler cover 70 is fixed to a lower portion of the lower end plate 63, and a lower muffler chamber 71 is formed between the lower end plate 63 and the lower muffler cover 70. The lower end plate 63 is formed with a second discharge hole 72 that allows the second compression chamber 54b of the second cylinder 52 and the lower muffler chamber 71 to communicate with each other. A second discharge valve 73 is installed to prevent backflow. The lower muffler chamber 71 reduces the pressure pulsation of the discharged refrigerant.

  Although not shown, first and second through holes are provided on the outer peripheral wall of the cylindrical compressor casing 11 so as to be separated from each other in the axial direction. In addition, an accumulator 81 made of an independent sealed cylindrical container is held by an accumulator holder (not shown) and an accumulator band 82 on the outer wall of the compressor housing 11. This accumulator 81 has a system connection pipe 83 connected to the low pressure side of the refrigeration cycle at the upper end.

  The accumulator 81 is connected to the lower ends of first and second suction pipes 84 and 85, and the first and second suction pipes 84 and 85 are connected to the first and second suction pipes 84 and 85. The other end is connected to the first and second suction holes 48 (not shown) of the first and second cylinders 42 and 52 in the first and second compression parts 41 and 51 through the two through holes.

  The compressor casing 11 is connected to the upper end of the discharge pipe 86 as a discharge unit that is connected to the high-pressure side of the refrigeration cycle and discharges high-pressure refrigerant to the high-pressure side of the refrigeration cycle. That is, the first and second discharge holes 68 and 72 communicate with the high-pressure side of the refrigeration cycle via the discharge pipe 86.

  The compressor housing 11 stores lubricating oil in a lower portion, and an oil supply mechanism 14 that supplies the stored lubricant oil to the sliding portion of the compression unit 12 through the oil supply hole 100 of the rotary shaft 33 is provided. . The oil supply mechanism 14 includes an accommodation hole 101, a pump case 102, and pump blades 103.

  That is, in the oil supply mechanism 14, as shown in FIGS. 1, 3, and 4, the rotary shaft 33 is formed with a receiving hole 101 having a lower end opened on the lower side and an upper end opened on the upper side. A through hole 104 communicating with the housing hole 101 is formed, and a lateral hole 105 penetrating in the radial direction and communicating with the housing hole 101 is formed in the intermediate portion. The oil supply hole 100 includes the accommodation hole 101, the through hole 104, and the lateral hole 105. The horizontal hole 105 is provided corresponding to the upper bearing portion 62a, the first and second annular pistons 43 and 53, and the lower bearing portion 63a.

  The pump case 102 is a pipe having a cylindrical shape, and a lubricating oil suction hole 106 having a small inner diameter is formed at the lower end portion, and the upper end portion is opened and fitted into the accommodation hole 101 to be attached. The pump blade 103 has a plate shape and is accommodated in the accommodation hole 101 and the pump case 102, and a widened portion 107 is formed at an intermediate portion in the longitudinal direction, and the widened portion 107 is related to the upper inner surface of the pump case 102. It has been stopped.

  In this case, the accommodation hole 101 formed in the rotating shaft 33 includes the accommodation hole body 101a formed on the upper side and the accommodation hole body 101a formed on the lower side via the stepped portion 101b. The mounting hole 101c is slightly larger in diameter than the main body 101a. The pump case 102 is positioned by fitting the upper end of the pump case 102 into the mounting hole 101c in the housing hole 101 and abutting the upper end of the stepped portion 101b. In this case, the pump case 102 is fixed to the rotary shaft 33 by being press-fitted into the mounting hole 101c, but the press-fitting allowance between the pump case 102 and the mounting hole 101c can be set to 0 to 0.06 mm. preferable. Further, it is preferable that the inner diameter of the housing hole main body 101a and the inner diameter of the pump case 102 are set to be substantially the same.

  The pump case 102 can be deformed at least in the radial direction. In this embodiment, the pump case 102 is made of copper, so that it can be slightly elastically deformed.

  Further, the pump blade 103 is twisted by a predetermined angle in the circumferential direction, which is 180 degrees in this embodiment. As shown in FIG. 5, with respect to the plate material 201 having a predetermined length L and having a predetermined width W, a side portion 203a having a predetermined width W in both the width direction is formed in a predetermined length region L1 in an intermediate portion in the longitudinal direction. , 203b are formed to protrude from the projections 202a, 202b by a predetermined amount W1. In addition, inclined portions 204a and 204b having a predetermined angle α are formed between the side portions 203a and 203b having a predetermined width W and the convex portions 202a and 202b with respect to the plate material 201. In this case, the inclined portions 204a and 204b are formed on both sides of the convex portions 202a and 202b. Further, arc portions 205 having predetermined radii R at four corners are formed on the plate material 201. The inclined portions 204a and 204b and the arc portion 205 may be formed integrally when the plate material 201 is pressed, or may be formed by chamfering corner portions after pressing, or barrel polishing. May be formed.

  By twisting the plate material 201 formed in this way by 180 degrees, the pump blade 103 is formed as shown in FIG. At this time, only the edge part of the longitudinal direction in the board | plate material 201 is not twisted, but flat part 103a, 103b is formed. In addition, the pump blade 103 is formed symmetrically with respect to the longitudinal direction with the widened portion 107 as a center by forming the widened portion 107 at an intermediate portion in the longitudinal direction.

  In this case, the pump blade 103 after being twisted is processed so that the width of the widened portion 107 is equal to or larger than the inner diameter of the pump case 102. Specifically, the pump blade 103 is fixed to the pump case 102 by press-fitting the widened portion 107 into the inner peripheral portion of the pump case 102. The press-fitting allowance is preferably set to 0 to 0.5 mm. The pump blade 103 is made of an inexpensive and elastically deformable material such as a carbon steel material for tools (so-called spring steel) or a cold rolled steel material. Therefore, the pump blade 103 can be elastically deformed in the twisting direction, and is deformed and fixed in the twisting direction when the pump blade 103 (the widened portion 107) is press-fitted into the pump case 102. Moreover, it is preferable to set the angle α of the inclined portions 204a and 204b in the pump blade 103 to 10 to 45 degrees.

  The twist angle of the pump blade 103 is not limited to 180 degrees, and may be set as appropriate. Further, the widened portion 107 of the pump blade 103 may be configured by providing a convex portion only on one side in the width direction. In addition, the inclined portions 204a and 204b in the pump blade 103 are not limited to a straight line, but may be curved, that is, an arc shape in which the side portions 203a and 203b and the convex portions 202a and 202b are smoothly continuous.

  When the oil supply mechanism 14 is configured by assembling the housing hole 101, the pump case 102, and the pump blade 103 configured as described above, the pump blade 103 is press-fitted into the pump case 102 and fixed, and the pump blade 103 is fixed. The case 102 is press-fitted into the accommodation hole 101 of the rotating shaft 33 and fixed.

  When the widened portion 107 of the pump blade 103 is press-fitted into the pump case 102, the pump blade 103 is elastically deformed in the torsional direction to reduce the diameter, but the pump case 102 is also elastically deformed in the radial direction to expand the diameter. To do. Therefore, the force that the pump blade 103 (the widened portion 107) press-fits to the pump case 102 is reduced, and generation of shaving powder due to rubbing between the widened portion 107 and the pump case 102 is suppressed. In addition, since the pump blade 103 is made of a carbon steel material for tools or a cold rolled steel material and can be elastically deformed, the press-fitting operation of the pump blade 103 to the pump case 102 can be performed using a small hand press or the like. There is easy and reliable assembly by press-fitting. When the pump case 102 to which the pump blade 103 is fixed is press-fitted into the accommodation hole 101 of the rotary shaft 33, the holding force of the pump blade 103 by the pump case 102 is restored by the elastic deformation of the pump case 102 having an enlarged diameter. Is enhanced and firmly fixed.

  When the widened portion 107 of the pump blade 103 is press-fitted into the pump case 102, the pump blade 103 has an end portion (corner portion of the flat portion 103 b) accommodated in the pump case 102 in the longitudinal direction. It is positioned by contacting the inner surface of. Further, when the pump case 102 to which the pump blade 103 is fixed is press-fitted into the accommodation hole 101 of the rotating shaft 33, the end of the pump case 102 is positioned by contacting the stepped portion 101 b of the accommodation hole 101. In this case, the pump blade 102 has an end portion (corner portion of the flat portion 103 a) accommodated in the accommodation hole 101 in the longitudinal direction spaced from the inner surface of the accommodation hole 101.

  Therefore, as shown in FIG. 1, when the rotation shaft 33 rotates in the oil supply mechanism 14, the pump case 102 and the pump blade 103 rotate together and are stored in the lower portion of the compressor housing 11 by the centrifugal force. Lubricating oil can be pumped up. That is, the lubricating oil in the compressor housing 11 enters the pump case 102 from the lubricating oil suction hole 106 and rises in the accommodation hole 101 by the rotation of the pump blade 103. Then, the oil is supplied to the upper bearing portion 62a, the first and second annular pistons 43 and 53, the lower bearing portion 63a, and the like through each lateral hole 105 and lubricated. Then, the lubricating oil that has lubricated each part enters the first and second working chambers 44 and 54 through the minute gaps between the parts that define the first and second compression parts 41 and 51, and lubricates each sliding part. A small gap is sealed and discharged.

  Here, the operation of the rotary compressor of this embodiment will be described. When the rotary compressor is operated, the refrigerant flows from the low pressure side of the refrigeration cycle through the system connection pipe 83 into the accumulator 81, and the liquid refrigerant is separated into the lower part of the accumulator 81 and the gas refrigerant is separated into the upper part of the accumulator 81. The

  In the compressor housing 11, the rotation shaft 33 is driven and rotated by the motor 13, and the first and second annular pistons 43 and 53 rotate and revolve through the first and second eccentric portions 64 and 65. Then, the first and second annular pistons 43 and 53 revolve while rotating in the first and second cylinders 42 and 52, so that the volumes of the first and second suction chambers 44a and 54a are expanded, and the accumulators. The gas refrigerant in 81 is sucked into the first and second suction chambers 44a and 54a from the first and second suction pipes 84 and 85 through the first and second suction holes 48 (not shown).

  When the first and second annular pistons 43 and 53 revolve once, the first and second suction chambers 44a and 54a are blocked from the first and second suction holes 48 and (not shown), and the first and second The gas refrigerant is compressed by switching to the compression chambers 44b and 54b.

  The pressure of the refrigerant in the compressed first and second compression chambers 44b and 54b is such that the upper and lower mufflers on the downstream side of the first and second discharge valves 69 and 72 provided in the first and second discharge holes 68 and 72, respectively. When the pressure in the chambers 67 and 71 is reached, the first and second discharge valves 69 and 72 are opened. Then, the compressed refrigerant is discharged to the upper and lower muffler chambers 67 and 71 through the first and second discharge holes 68 and 72, and after the pressure pulsation causing noise is reduced in the upper and lower muffler chambers 67 and 71, The high-pressure refrigerant is discharged into the compressor casing 11.

  Thereafter, the high-pressure refrigerant passes through a core notch (not shown) of the stator 31 of the motor 13 and a gap between the core and the winding, is sent to the upper side of the motor 13, and is discharged to the high-pressure side of the refrigeration cycle through the discharge pipe 86. Is done.

  At this time, the lubricating oil stored in the lower portion of the compressor housing 11 is pumped up by the oil supply mechanism 14 and lubricates the upper bearing portion 62a, the first and second annular pistons 43 and 53, the lower bearing portion 63a, and the like. . That is, when the pump case 102 and the pump blade 103 rotate together with the rotating shaft 33, the lubricating oil is pumped up by the centrifugal force, and the lubricating oil rises in the accommodation hole 101 and passes through the horizontal holes 105 to the upper bearing portion 62a. The first and second annular pistons 43 and 53, the lower bearing portion 63a, and the like are lubricated. And the lubricating oil after lubricating each part is returned to the lower part of the compressor housing | casing 11. FIG.

  As described above, in the rotary compressor according to the present embodiment, the compressor 12 that compresses the sucked refrigerant is provided at the lower part of the compressor casing 11, and the rotary shaft 33 is provided above the compressor casing 11. A motor 13 that drives the compression unit 12 is provided, and an oil supply mechanism 14 that supplies the lubricating oil stored in the lower portion of the compressor housing 11 to the sliding portion of the compression unit 12 through the oil supply hole 100 of the rotary shaft 33 is provided. As the oil supply mechanism 14, the housing hole 101 that opens to the lower end portion of the rotating shaft 33 and communicates with the oil supply hole 100 and the lubricating oil suction hole 106 at the lower end portion and the upper end portion opens to the housing hole 101. A pump case 102 to be mounted and a widened portion 107 formed in a plate shape and housed in the housing hole 101 and the pump case 102 and formed in an intermediate portion in the longitudinal direction are locked to the upper inner surface of the pump case 102. Pump blade And 03 are provided.

  Accordingly, the pump blade 103 is locked to the upper inner surface of the pump case 102 via the widened portion 107, and the pump blade 103 is fitted into the accommodation hole 101 of the rotating shaft 33, so that the pump blade 103 is rotated to the rotating shaft 33. The oil supply hole 100 is attached. Therefore, when the pump blade 103 is mounted in the housing hole 101, the pump blade 103 does not come into contact with the housing hole 101, can prevent the pump blade 103 from being deformed, and improve the assembling property. Can do.

  Further, in the rotary compressor of the present embodiment, the pump blade 103 is positioned by the end portion on the side accommodated in the pump case 102 in the longitudinal direction coming into contact with the inner surface of the pump case 102. Accordingly, the pump blade 103 is positioned at a predetermined position with respect to the pump case 102, so that the pump blade 103 is positioned at a predetermined position in the housing hole 101 only by fitting the pump case 102 into the housing hole 101. It will be easily positioned and the assembly of the oil supply mechanism 14 can be improved.

  Further, in the rotary compressor of this embodiment, the pump blade 103 is separated from the inner surface of the accommodation hole 101 at the end on the side accommodated in the accommodation hole 101 in the longitudinal direction. Therefore, the pump blade 103 is positioned with one end contacting the pump case 102 and the other end is separated from the receiving hole 101, and no excessive stress acts on the pump blade 103. The deformation and breakage of 103 can be prevented and the durability can be improved.

  Further, in the rotary compressor of this embodiment, the accommodation hole 101 is composed of the accommodation hole main body 101a, the stepped portion 101b, and the large-diameter attachment hole 101c, and the upper end portion of the pump case 102 is fitted into the attachment hole 101c. The pump case 102 is positioned by contacting the stepped portion 101b. Therefore, by positioning the pump case 102 using the stepped portion 101b of the housing hole 101, the pump blade 103 is positioned with respect to the housing hole 101, so that direct positioning by the pump blade 103 is unnecessary, and the pump blade 103 can be prevented from being deformed or damaged, and the assembling property can be improved.

  Further, in the rotary compressor of the present embodiment, the widened portion 107 having a width equal to or larger than the inner diameter of the pump case 102 is formed by forming convex portions 202 a and 202 b projecting outward at the intermediate portion in the longitudinal direction of the pump blade 103. Is forming. Therefore, the processing cost can be reduced by forming the widened portion 107 easily.

  Further, in the rotary compressor of this embodiment, inclined portions 204a and 204b are formed between the side portions 203a and 203b of the pump blade 103 and the convex portions 202a and 202b. Accordingly, when the pump blade 103 is mounted on the pump case 102, the widened portion 107 (the convex portions 202a and 202b) is fitted from the side portions 203a and 203b through the inclined portions 204a and 204b, so that the pump blade 103 is smooth. It can be attached to the pump case 102. In this case, since the pump blade 103 smoothly fits into the pump case 102, generation of shaving powder in the pump blade 103 and the pump case 102 can be suppressed, and damage can be prevented.

  Further, in the rotary compressor of the present embodiment, the pump blade 103 is manufactured by a material that is twisted by a predetermined angle in the circumferential direction and elastically deformable in the twisted direction. Therefore, when the pump blade 103 is attached to the pump case 102, the pump blade 103 is elastically deformed and fitted in the twist direction, and the pump blade 103 can be smoothly attached to the pump case 102.

  In the rotary compressor of this embodiment, the pump case 102 can be deformed at least in the radial direction. Therefore, when the pump blade 103 is attached to the pump case 102, the pump case 102 is deformed and the pump blade 103 is fitted, and the pump blade 103 can be smoothly attached to the pump case 102. Thereafter, when the pump case 102 is fitted into the accommodation hole 101, the elastic deformation of the pump case 102 returns, and the pump blade 103 can be firmly fixed to the pump case 102.

  Further, in the rotary compressor of this embodiment, the pump blade 103 has the widened portion 107, that is, the convex portions 202a and 202b, the side portions 203a and 203b, the inclined portion 204a, and the like so as to have a point-symmetric shape with respect to the center position. 204b and an arc portion 205 are formed. Therefore, when the pump blade 103 is fitted to the pump case 102, the directionality is not regulated, and the assembling property can be improved.

  In the rotary compressor according to the present invention, the pump blade is locked to the pump case via the widening portion, and the pump case is fitted to the accommodation hole and the pump blade is attached to the rotating shaft, so that the assembly can be performed at the time of assembly. The pump blade is prevented from being deformed to improve the assemblability, and can be applied to any rotary compressor.

DESCRIPTION OF SYMBOLS 11 Compressor housing | casing 12 Compression part 13 Motor 14 Oil supply mechanism 33 Rotating shaft 41 1st compression part 42 1st cylinder 43 1st annular piston 44 1st working chamber 44a 1st suction chamber 44b 1st compression chamber 46 1st vane 51 Second compression portion 52 Second cylinder 53 Second annular piston 54 Second working chamber 54a Second suction chamber 54b Second compression chamber 61 Intermediate partition plate 62 Upper end plate 63 Lower end plate 64 First eccentric portion 65 Second eccentric portion 81 Accumulator DESCRIPTION OF SYMBOLS 100 Oil supply hole 101 Accommodating hole 101b Stepped part 102 Pump case 103 Pump blade 106 Lubricating oil suction hole 107 Widening part 202a, 202b Protrusion part 204a, 204b Inclination part

Claims (7)

A compressor housing having a hollow shape provided with a refrigerant suction portion and a discharge portion;
A compression unit that is provided in a lower portion of the compressor housing and compresses the refrigerant sucked from the suction unit;
A motor that is provided in an upper part of the compressor housing and drives the compression unit via a rotation shaft;
An oil supply mechanism for supplying lubricating oil stored in a lower part of the compressor housing to a sliding portion of the compression part through an oil supply hole of the rotary shaft;
A rotary compressor comprising:
The oil supply mechanism is
An accommodation hole that opens at the lower end of the rotating shaft and communicates with the oil supply hole;
A pump case having a lubricating oil suction hole at its lower end and having its upper end open and mounted in the accommodation hole;
A widened portion formed in a plate shape and accommodated in the accommodating hole and the pump case and formed in an intermediate portion in the longitudinal direction has a pump blade locked to an upper inner surface of the pump case,
A rotary compressor characterized by that.   2. The rotary compressor according to claim 1, wherein the pump blade is positioned by contacting an inner surface of the pump case with an end portion accommodated in the pump case in a longitudinal direction.   3. The rotary compressor according to claim 2, wherein an end portion of the pump blade that is accommodated in the accommodation hole in a longitudinal direction is separated from an inner surface of the accommodation hole.   The widened portion has a width equal to or larger than an inner diameter of the pump case by forming a convex portion in which an intermediate portion in the longitudinal direction of the pump blade projects in one or both of the width directions. The rotary compressor as described in any one of 1-3.   The rotary compressor according to claim 4, wherein the pump blade has an inclined portion formed between a side portion and the convex portion.   The rotary compression according to any one of claims 1 to 5, wherein the pump blade is twisted by a predetermined angle in a circumferential direction and is made of a material that is elastically deformable in the twist direction. Machine.   The rotary compressor according to any one of claims 1 to 6, wherein the pump case is deformable at least in a radial direction.

Images