JP2010031690A - Rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary compressor reducing displacement of a bush on the side of a high-pressure chamber in the state of a top dead center and reducing abnormal noise and vibration caused by collision of the bush on the side of the high-pressure chamber with a retaining hole, in comparison with the existing rotary compressor. <P>SOLUTION: This rotary compressor includes: a cylinder chamber B1 formed in an internal space; a cylinder 9 having a suction hole 9a sucking a refrigerant from the outside into the cylinder chamber B1 and the retaining hole 9b arranged outside of the cylinder chamber B1; a roller 8a arranged inside of the cylinder chamber B1; a blade 8b extended to pass from the peripheral surface of the roller 8a through the inside of the retaining hole 9b and partitioning the cylinder chamber B1 into a low-pressure chamber LB1 sucking the refrigerant through the suction hole 9a and the high-pressure chamber HB1 compressing the refrigerant; and a bush 14 on the side of a low-pressure chamber and the bush 15 on the side of the high-pressure chamber respectively arranged in the retaining hole 9b at both sides of the blade 8b. The movable distance of the bush 15 on the side of the high-pressure chamber in the retaining hole 9b, in the extending direction of the blade 8b, is shorter than the movable distance of the bush 14 on the side of the low-pressure chamber in the retaining hole 9b, in the extending direction of the blade 8b. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a rotary compressor provided with bushes respectively disposed on both sides of a blade in a holding hole outside a cylinder chamber.

  A conventional rotary compressor includes a casing, an oil reservoir, a motor, a crankshaft, a cylinder and a piston, a discharge pipe provided on the upper part of the casing, and the like, which are covered with the casing. The cylinder has a cylinder chamber and a suction port penetrating from the cylinder chamber toward the outer peripheral portion. A holding hole is provided outside the cylinder chamber.

  The piston has a roller disposed inside the cylinder chamber and a blade extending from the outer peripheral surface of the roller to the inside of the holding hole. The cylinder and chamber are partitioned by the roller and the blade into a high-pressure chamber that discharges the compressed refrigerant from the discharge port by opening and closing the discharge valve, and a low-pressure chamber that sucks the refrigerant through the suction port. According to such a configuration, the refrigerant sucked into the low pressure chamber can be compressed in the high pressure chamber by the rotation of the crankshaft via the motor, and the compressed refrigerant can be discharged from the discharge port.

Also, the holding hole has a bush (hereinafter referred to as a high pressure chamber side bush) disposed on the high pressure chamber side of the cylinder chamber and a bush (hereinafter referred to as a low pressure chamber) disposed on the low pressure chamber side of the cylinder chamber on both sides of the blade. Each of which is a room-side bush). Also, a gap formed between the high pressure chamber side bush and the inner peripheral surface of the holding hole (hereinafter referred to as a high pressure chamber side bush clearance) and a low pressure chamber side bush and the inner peripheral surface of the holding hole are formed. The gap to be made (hereinafter referred to as the low pressure chamber side bush gap) is substantially the same (see Patent Document 1).
JP 2002-147381 A

  By the way, in such a conventional rotary compressor, the internal pressure of the high-pressure chamber is higher than the internal pressure of the casing when the above-described discharge valve is open (hereinafter referred to as the discharge valve open state). And by this pressure difference, the high pressure chamber side bush is pressed in the extending direction of the blade, and moves toward the casing side of the holding hole.

  On the other hand, when the roller is located at the top dead center (hereinafter referred to as the top dead center state), the high pressure chamber and the low pressure chamber communicate with each other, so that the internal pressure of the high pressure chamber rapidly decreases, and the internal pressure of the high pressure chamber and the casing The pressure difference from the internal pressure increases. Then, due to this large pressure difference, the high pressure chamber side bush located on the casing side of the holding hole is pressed in the extending direction of the blade and moves toward the high pressure chamber side of the holding hole. Due to this movement, the high pressure chamber side bush collides with the inner peripheral surface of the holding hole on the high pressure chamber side, and there is a problem that abnormal noise and vibration are generated by the collision force.

  Accordingly, the present invention has been made to solve the above-described problems, and compared with a conventional rotary compressor, the amount of movement of the high-pressure chamber side bush in the top dead center state can be reduced, and the high-pressure chamber An object of the present invention is to provide a rotary compressor capable of reducing abnormal noise and vibration due to a collision with a holding hole by a side bush.

  A rotary compressor according to a first aspect of the present invention includes a cylinder chamber formed in an internal space, a cylinder having a suction hole for sucking refrigerant from outside into the cylinder chamber, and a holding hole provided outside the cylinder chamber; A roller disposed in the cylinder chamber, a low-pressure chamber extending from the outer peripheral surface of the roller so as to pass through the holding hole, and a cylinder chamber for sucking refrigerant through the suction hole; and a high-pressure chamber for compressing the refrigerant And a high pressure chamber side bush and a low pressure chamber side bush respectively disposed in the holding hole on both sides of the blade, and the movable distance in the extending direction of the blade of the high pressure chamber side bush in the holding hole is In the holding hole, it is shorter than the movable distance in the extending direction of the blade of the low pressure chamber side bush.

  In this rotary compressor, the high pressure chamber side bush gap is smaller than the low pressure side bush gap. Therefore, the moving distance of the high pressure chamber side bush can be reduced as compared with the conventional rotary compressor in which the high pressure chamber side bush clearance and the low pressure side bush clearance are substantially the same. For this reason, compared with the conventional rotary compressor, the collision force to the holding hole by the high pressure chamber side bush in the top dead center state can be reduced, and abnormal noise and vibration at the time of collision can be reduced.

  A rotary compressor according to a second aspect of the invention is the rotary compressor according to the first aspect of the invention, wherein the holding hole is substantially circular in a plan view and each of the holding holes of the high pressure chamber side bush and the low pressure chamber side bush is The outer peripheral surface facing the inner peripheral surface is substantially circular in plan view, and the difference in the radius of curvature between the outer peripheral surface of the high pressure chamber side bush and the inner peripheral surface of the holding hole is the same as that of the outer peripheral surface of the low pressure chamber side bush. It is smaller than the difference in curvature radius with the inner peripheral surface of the hole.

  In this rotary compressor, the difference in curvature radius between the outer peripheral surface of the high pressure chamber side bush and the inner peripheral surface of the holding hole is smaller than the difference in curvature radius between the outer peripheral surface of the low pressure chamber side bush and the inner peripheral surface of the holding hole. Therefore, the movable distance of the high pressure chamber side bush in the extending direction of the blade in the holding hole can be easily made shorter than the moving average distance in the holding hole of the low pressure chamber side bush in the extending direction of the blade.

A rotary compressor according to a third aspect of the present invention is the rotary compressor according to the first or second aspect, wherein the refrigerant sucked from the outside into the cylinder chamber is a CO ₂ refrigerant.

In this rotary compressor, CO ₂ refrigerant is sucked into the cylinder chamber from the outside. Generally, CO ₂ refrigerant has a higher pressure than the other refrigerants, force the high pressure chamber side bush in the discharge valve open state strikes the holding hole is larger than the other refrigerants. In this respect, the present invention is particularly effective in that it can reduce the moving distance of the high-pressure chamber side bush compared to the conventional rotary compressor, and can reduce abnormal noise and vibration during a collision.

  As described above, according to the present invention, the following effects can be obtained.

  In the first invention, the moving distance of the high pressure chamber side bush can be reduced as compared with the conventional rotary compressor in which the high pressure chamber side bush clearance and the low pressure side bush clearance are substantially the same. For this reason, compared with the conventional rotary compressor, the collision force to the holding hole by the high pressure chamber side bush in the top dead center state can be reduced, and abnormal noise and vibration at the time of collision can be reduced.

  In the second aspect of the invention, the difference in curvature radius between the outer peripheral surface of the high pressure chamber side bush and the inner peripheral surface of the holding hole is the difference in curvature radius between the outer peripheral surface of the low pressure chamber side bush and the inner peripheral surface of the holding hole. Therefore, the movable distance of the high pressure chamber side bush in the extending direction of the blade in the holding hole can be easily made shorter than the moving average distance in the holding hole of the low pressure chamber side bush in the extending direction of the blade.

In the third invention, CO ₂ refrigerant is sucked into the cylinder chamber from the outside. Generally, the pressure of CO ₂ refrigerant is higher than that of other refrigerants, and the force with which the high pressure chamber side bush collides with the holding hole in the top dead center state is greater than that of other refrigerants. In this respect, the present invention is particularly effective in that it can reduce the moving distance of the high-pressure chamber side bush compared to the conventional rotary compressor, and can reduce abnormal noise and vibration during a collision.

  Hereinafter, embodiments of a rotary compressor according to the present invention will be described with reference to the drawings.

  FIG. 1 is a cross-sectional view of a rotary compressor according to an embodiment of the present invention, and FIG. 2 is a cross-sectional view taken along line AA of FIG. 3 is a cross-sectional view taken along line BB in FIG. Hereinafter, the rotary compressor 1 will be described in detail with reference to FIGS.

  As shown in FIG. 1, the rotary compressor 1 is a one-cylinder rotary compressor, and includes a sealed casing 2, a drive mechanism 3 and a compression mechanism 4 disposed in the sealed casing 2. The rotary compressor 1 is a so-called high-pressure dome type compressor, and a compression mechanism 4 is disposed below the drive mechanism 3 in a sealed casing 2. In addition, a lubricating oil 5 supplied to each sliding portion of the compression mechanism 4 is stored in the lower portion of the hermetic casing 2.

  The drive mechanism 3 is provided to drive the compression mechanism 4 and includes a motor 6 serving as a drive source and a shaft 7 attached to the motor 6.

  The motor 6 includes a rotor 6a and a stator 6b disposed on the radially outer side of the rotor 6a via an air gap. A shaft 7 is rotatably attached to the rotor 6a. And the rotor 6a has the rotor main body which consists of a laminated | stacked electromagnetic steel plate, and the magnet embed | buried under this rotor main body. The stator 6b has a stator body made of iron and a coil wound around the stator body. The motor 6 rotates the rotor 6a together with the shaft 7 by the electromagnetic force generated in the stator 6b by passing a current through the coil.

  The shaft 7 rotates together with the rotor 6a described above to rotate the roller 8a of the compression mechanism 4. The shaft 7 is provided with an eccentric portion 7a so as to be positioned in a cylinder chamber B1 of a cylinder 9 described later. A roller 8a is attached to the eccentric portion 7a. Thereby, with rotation of the shaft 7, the roller 8a attached to the eccentric part 7a can be rotated in the cylinder chamber B1.

On the other hand, the compression mechanism 4 is provided to compress and discharge CO ₂ refrigerant (hereinafter abbreviated as refrigerant) sucked from an accumulator (not shown) through a suction hole 9a (see FIG. 3). The refrigerant discharged by the compression mechanism 4 passes through an air gap between the stator 6b of the drive mechanism 3 and the rotor 6a, cools the drive mechanism 3, and is then discharged from the discharge pipe 10. The compression mechanism 4 includes a front muffler 11, a front head 12, a cylinder 9, a roller 8a, and a rear head 13 from the top to the bottom along the rotation axis of the shaft 7 of the drive mechanism 3. Yes.

  The front muffler 11 forms a muffler space A1 between the front head 12 and the noise due to refrigerant discharge. The front muffler 11 has a hat shape and is attached so as to close the valve accommodating chamber 12d (see FIG. 2) of the front head 12.

  The front head 12 is disposed on the upper side of the cylinder 9 and closes the opening above the cylinder chamber B1 of the cylinder 9. As shown in FIG. 2, the front head 12 includes a disc-shaped main body portion 12b having a bearing hole 12a into which the shaft 7 is inserted, and an annular boss protruding upward from the main body portion 12b so as to surround the bearing hole 12a. Part 12c.

  The main body 12b is formed with a concave valve housing chamber 12d whose upper side is open and a discharge port 12e communicating with the valve housing chamber 12d. Thereby, the refrigerant | coolant compressed by the rotational drive of the roller 8a in cylinder chamber B1 of the cylinder 9 is guide | induced to the valve storage chamber 12d through the discharge port 12e. The refrigerant in the valve storage chamber 12d is discharged from a discharge hole (not shown) formed in the front muffler 11 through the muffler space A1. A discharge valve 12f that opens and closes the outlet of the discharge port 12e and a pressing member (not shown) that restricts the opening of the discharge valve 12f are provided in the valve storage chamber 12d.

  As shown in FIG. 3, the cylinder 9 is provided with a cylinder chamber B <b> 1 in which a roller 8 a that moves eccentrically with the rotation of the shaft 7 is disposed. The cylinder chamber B1 and the muffler space A1 are communicated with each other via a discharge port 12e (see FIG. 2). Therefore, the refrigerant compressed by the eccentric motion of the roller 8a attached to the eccentric portion 7a of the shaft 7 is guided from the cylinder chamber B1 to the muffler space A1 through the discharge port 12e.

  The cylinder 9 is formed with a suction hole 9a penetrating from the outer periphery to the cylinder chamber B1. The refrigerant is sucked into the cylinder chamber B1 from the outside through the suction hole 9a. A holding hole 9b is formed outside the cylinder chamber B1.

  On the outer peripheral surface of the roller 8a, a blade 8b extending so as to pass through the inside of the holding hole 9b is formed. The piston 8 is formed by the roller 8a and the blade 8b.

  The cylinder chamber B1 is partitioned by the blade 8b into a low pressure chamber LB1 for sucking refrigerant through the suction hole 9a and a high pressure chamber HB1 for compressing the sucked refrigerant. A low pressure chamber side bush 14 and a high pressure chamber side bush 15 are disposed on the low pressure chamber LB1 side and the high pressure chamber HB1 side of the holding hole 9b, respectively.

  When the discharge valve 12f (see FIG. 3) that opens and closes the outlet of the discharge port 12e (see FIG. 3) is open (hereinafter referred to as the discharge valve open state), the internal pressure of the high pressure chamber HB1 is the casing 2 (see FIG. 1). ) Higher than the internal pressure. Due to this pressure difference, the high pressure chamber side bush 15 is pressed in the extending direction of the blade 8b, and moves toward the casing 2 side of the holding hole 9b.

  On the other hand, when the roller 8a is located at the top dead center (hereinafter referred to as the top dead center state), the high pressure chamber and the low pressure chamber communicate with each other, so that the internal pressure of the high pressure chamber HB1 rapidly decreases, and the inside of the high pressure chamber BH1. The pressure difference between the pressure and the internal pressure of the casing 2 increases. Due to this large pressure difference, the high pressure chamber side bush 15 located on the casing 2 side of the holding hole 9b is pressed in the extending direction of the blade 8b and moves toward the high pressure chamber BH1 side of the holding hole 9b. . By this movement, the high pressure chamber side bush 15 collides with the inner peripheral surface of the holding hole 9b on the high pressure chamber BH1 side.

FIG. 4 is an enlarged view around the low pressure chamber side bush 14 and the high pressure chamber side bush 15 shown in FIG. 3. _Reference numerals R, R _LB , and R _HB shown in the drawing indicate the radii of curvature of the inner peripheral surface of the holding hole 9b, the outer peripheral surface of the low pressure chamber side bush 14, and the outer peripheral surface of the high pressure chamber side bush 15, respectively. As shown in the figure, the curvature radii R _LB and R _HB are both smaller than the curvature radius R hole, and the difference between the curvature radius R _HB and the curvature radius R hole (the high pressure chamber side bush gap) is the curvature radius. It is smaller than the difference between R _LB and the radius of curvature R hole (low pressure chamber side bush gap).

  In the rotary compressor 1 of the present invention, the moving distance of the high pressure chamber side bush 15 in the open state of the discharge valve is smaller than that of a conventional rotary compressor in which the high pressure chamber side bush clearance and the low pressure chamber side bush clearance are substantially the same. it can. For this reason, the collision force of the holding hole 9b by the high pressure chamber side bush 15 to the high pressure chamber BH1 side can be reduced. As a result, in the rotary compressor 1 of the present invention, abnormal noise and vibration at the time of collision can be reduced as compared with the conventional rotary compressor.

In general, since the rigidity of the cylinder 9 is weakened around the suction hole 9a, the cylinder 9 is easily deformed around the suction hole 9a. Therefore, if the influence on the holding hole 9b due to this deformation is taken into consideration, it is necessary to secure a certain amount of low pressure chamber bush clearance. In this regard, in the present invention, the difference between the curvature radius R _LB and the curvature radius R hole can be made larger than the difference between the curvature radius R _HB and the curvature radius R hole. In other words, the low pressure side bush gap can be made larger than the high pressure chamber side bush gap. For this reason, in the present invention, the low pressure side bush gap can be maintained at an appropriate size in consideration of the influence on the holding hole 9 a due to the deformation of the cylinder 9.

  As described above, in this embodiment, the amount of movement of the high-pressure chamber side bush 15 in the top dead center state can be reduced as compared with the conventional rotary compressor. Accordingly, the collision force of the holding hole 9a by the high pressure chamber side bush 15 to the high pressure chamber BH1 side can be reduced. For this reason, compared with the conventional rotary compressor, the noise and vibration at the time of a collision can be reduced.

  As mentioned above, although embodiment of this invention was described based on drawing, it should be thought that a specific structure is not limited to these embodiment. The scope of the present invention is indicated not only by the above description of the embodiments but also by the scope of claims for patent, and further includes all modifications within the meaning and scope equivalent to the scope of claims for patent.

  If the present invention is used, the amount of movement of the high pressure chamber side bush in the top dead center state can be reduced as compared with the conventional rotary compressor, and abnormal noise and vibration due to the collision with the holding hole by the high pressure chamber side bush are reduced. A possible rotary compressor can be obtained.

It is sectional drawing of the rotary compressor which concerns on one Embodiment of this invention. It is sectional drawing along the AA line of FIG. It is sectional drawing along the BB line of FIG. FIG. 4 is an enlarged view around a low pressure chamber side bush and a high pressure chamber side bush shown in FIG. 3.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Rotary compressor 2 Sealed casing 3 Drive mechanism 4 Compression mechanism 8 Piston 8a Roller 8b Blade 9 Cylinder 9a Suction hole 9b Holding hole 14 Low pressure chamber side bush 15 High pressure chamber side bush A1 Muffler space B1 Cylinder chamber LB1 Low pressure chamber HB1 High pressure chamber

Claims (3)

A cylinder chamber formed in an internal space, a cylinder having a suction hole for sucking refrigerant from outside into the cylinder chamber, and a holding hole provided outside the cylinder chamber;
A roller disposed in the cylinder chamber;
The cylinder chamber extends from the outer peripheral surface of the roller and passes through the holding hole, and the cylinder chamber is divided into a low pressure chamber that sucks the refrigerant through the suction hole and a high pressure chamber that compresses the refrigerant. A blade to
A high pressure chamber side bush and a low pressure chamber side bush respectively disposed in the holding hole on both sides of the blade;
The movable distance of the high pressure chamber side bush in the extending direction of the blade in the holding hole is shorter than the movable distance of the low pressure chamber side bush in the extending direction of the blade in the holding hole. Rotary compressor. The holding hole is substantially circular in plan view,
The outer peripheral surfaces of the high pressure chamber side bush and the low pressure chamber side bush that face the inner peripheral surface of the holding hole are substantially circular in a plan view,
The difference in radius of curvature between the outer peripheral surface of the high pressure chamber side bush and the inner peripheral surface of the holding hole is smaller than the difference in curvature radius between the outer peripheral surface of the low pressure chamber side bush and the inner peripheral surface of the holding hole. The rotary compressor according to claim 1. The rotary compressor according to claim 1, wherein the refrigerant is a CO ₂ refrigerant.

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