JP2012117409A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress the deformation of an end plate portion, and to increase an oil passage amount of an oil return hole.SOLUTION: A compressor comprises a casing 2 and a compression mechanism accommodated in the casing 2. The compression mechanism comprises a cylinder 10 having a compression chamber, and a front head 30 which is arranged at the axial end of the cylinder 10 and fixed to the inner peripheral surface of the casing 2. The front head 30 comprises a support 36 which is inclined so as to be arranged outside the radial direction as separating from the cylinder 10 in the axial direction, and the oil return hole 38 which is formed at the support 36 and inclined to the axial direction.

Description

  The present invention relates to a compressor in which an outer peripheral surface of an end plate member disposed on an end surface of a cylinder is fixed to an inner peripheral surface of a casing.

2. Description of the Related Art Conventionally, there is known a compressor including a cylinder having a compression chamber and an end plate member that is disposed on an end surface of the cylinder to close the opening of the compression chamber and is fixed to the inner peripheral surface of the casing (for example, Patent Document 1). This end plate member has a disc-shaped main body portion disposed horizontally and a boss portion protruding upward from the center of the main body portion. A shaft is rotatably inserted into the main body portion and the boss portion.
An oil return hole is formed in a portion of the end plate member that is radially outward from the outer edge of the cylinder. Lubricating oil supplied to the sliding part of the compression mechanism is stored in the lower part of the casing, and the lubricating oil discharged from the compression mechanism together with the refrigerant passes through the oil return hole of the end plate member and is moved to the lower part of the casing. Returned to

JP 2007-162641 A

  However, in the conventional compressor, when the compression mechanism vibrates up and down with respect to the casing due to the pulsation of the refrigerant discharged from the compression chamber, the main body portion of the end plate member extends in the extending direction (horizontal direction). Since it receives a force in a direction perpendicular to, it may be bent and deformed.

  In order to reduce the size of the compressor, the diameter of the casing can be reduced while keeping the diameter of the compression chamber constant, or to increase the capacity of the compression chamber, the diameter of the compression chamber can be increased while keeping the diameter of the casing constant. When the diameter of the cylinder is increased, a range in which the oil return hole can be formed in the end plate member (a portion on the outer side in the radial direction from the outer edge of the cylinder) is reduced. As a result, the amount of oil passing through the oil return hole is not sufficient, and the return of oil to the lower portion of the casing is deteriorated.

  Therefore, the present invention provides a compressor that can suppress the deformation of the end plate portion and can relatively increase the diameter of the compression chamber with respect to the diameter of the casing while ensuring the amount of oil passing through the oil return hole. Objective.

  In order to solve the above problems, a compressor according to a first aspect of the present invention is a compressor including a casing and a compression mechanism accommodated in the casing, and the compression mechanism is a cylinder having a compression chamber. And an end plate member disposed at an axial end portion of the cylinder and fixed to an inner peripheral surface of the casing, and the end plate member is radially outer as it moves away from the cylinder in the axial direction. And a support portion that is inclined so as to be disposed on the surface, and an oil return hole that is formed in a region including the support portion and is inclined with respect to the axial direction.

In this compressor, since the support portion extends while being inclined with respect to a plane orthogonal to the axial direction, when an axial force is applied to the support portion, the direction parallel to the extending direction of the support portion. And a component force in a direction perpendicular to the extending direction of the support portion are generated. Therefore, since the force in the direction perpendicular to the extending direction of the support part can be reduced compared to the case where the support part extends in the direction orthogonal to the axial direction, the deformation of the support part is suppressed. can do.
Further, in this compressor, since the oil return hole is formed to be inclined with respect to the axial direction in the region including the inclined support portion, the same flow path as that of the present invention is provided in the horizontally extending support portion. The diameter of the compression chamber can be made relatively large with respect to the inner diameter of the casing as compared with the case where the oil return hole having the area is provided so as to be orthogonal to the support portion. Since the oil passage amount of the oil return hole depends on the flow path area, in the present invention, the diameter of the compression chamber can be made relatively large with respect to the inner diameter of the casing while maintaining the oil passage amount of the oil return hole. .

  In the present invention, the oil return hole is inclined with respect to the axial direction, not only when the entire inner peripheral surface of the oil return hole is inclined with respect to the axial direction, This includes the case where only a part of the peripheral surface is inclined with respect to the axial direction.

  A compressor according to a second invention is characterized in that, in the compressor according to the first invention, a portion on the radially inner side and a portion on the radially outer side of the oil return hole face each other in the radial direction. To do.

  In this compressor, the radial length of the range in which the oil return hole is formed in the end plate member, compared to the case where the radially inner portion and the radially outer portion of the oil return hole do not face each other in the radial direction. Can be reduced.

  A compressor according to a third aspect of the present invention is the compressor according to the second aspect, wherein the oil return hole is orthogonal to the inclination direction of the support portion.

  In this compressor, since the oil return hole is orthogonal to the inclination direction of the support portion, the amount of oil passing through the oil return hole can be reliably increased.

  A compressor according to a fourth aspect of the present invention is the compressor according to any one of the first to third aspects, wherein a portion of the oil return hole on the radially inner side is formed in a region overlapping the cylinder when viewed from the axial direction. It is characterized by being.

  In this compressor, the flow area of the oil return hole can be increased as compared with the case where the oil return hole is formed on the outer side in the radial direction of the cylinder when viewed from the axial direction.

  In the compressor according to the fifth invention, in the compressor according to the fourth invention, at the boundary between the end plate member and the cylinder, the position of the radially inner end of the oil return hole is the position of the cylinder. It is characterized by being coincident with the position of the outer edge.

In this compressor, at the boundary between the end plate member and the cylinder, the position of the radially inner end of the oil return hole is more radially outward than the position of the outer edge of the cylinder. The channel area can be increased.
Further, at the boundary between the end plate member and the cylinder, the position of the end portion on the radially inner side of the oil return hole is more inward than the position of the outer edge of the cylinder. Since the space can be effectively used as an oil passage, it is possible to prevent the strength of the support portion from being lowered unnecessarily.

  In the compressor which concerns on 6th invention, in the compressor which concerns on any 1st-5th invention, the said support part inclines within the range of 30 degrees or more and 60 degrees or less with respect to the axial direction. It is characterized by that.

  In this compressor, deformation of the support portion can be suppressed not only when the support portion receives an axial force but also when the support portion receives a force perpendicular to the axial direction.

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

In the first invention, since the support portion extends while being inclined with respect to the plane orthogonal to the axial direction, when an axial force acts on the support portion, the support portion is parallel to the extending direction of the support portion. The component force in the direction and the component force in the direction orthogonal to the extending direction of the support portion are generated. Therefore, since the force in the direction perpendicular to the extending direction of the support part can be reduced compared to the case where the support part extends in the direction orthogonal to the axial direction, the deformation of the support part is suppressed. can do.
Further, in this compressor, since the oil return hole is formed to be inclined with respect to the axial direction in the region including the inclined support portion, the same flow path as that of the present invention is provided in the horizontally extending support portion. The diameter of the compression chamber can be made relatively large with respect to the inner diameter of the casing as compared with the case where the oil return hole having the area is provided so as to be orthogonal to the support portion. Since the oil passage amount of the oil return hole depends on the flow path area, in the present invention, the diameter of the compression chamber can be made relatively large with respect to the inner diameter of the casing while maintaining the oil passage amount of the oil return hole. .

  In the second invention, the radial length of the range in which the oil return hole is formed in the end plate member as compared with the case where the radially inner portion and the radially outer portion of the oil return hole do not face each other in the radial direction. Can be reduced.

  In the third aspect of the invention, since the oil return hole is orthogonal to the inclination direction of the support portion, the amount of oil passing through the oil return hole can be reliably increased.

In the fourth aspect of the present invention, the flow area of the oil return hole can be increased as compared with the case where the oil return hole is formed on the radially outer side of the cylinder as viewed from the axial direction.
In addition, the cylinder outer diameter is increased with the casing diameter kept constant, or the casing diameter is reduced with the cylinder outer diameter kept constant, compared to the case where the oil return hole is provided in the horizontally extending support portion. can do.

In the fifth aspect of the present invention, the oil return hole is located at the boundary between the end plate member and the cylinder at the radially inner end of the oil return hole in the radial direction outside the position of the outer edge of the cylinder. The flow path area can be increased.
Further, at the boundary between the end plate member and the cylinder, the position of the end portion on the radially inner side of the oil return hole is more inward than the position of the outer edge of the cylinder. Since the space can be effectively used as an oil passage, it is possible to prevent the strength of the support portion from being lowered unnecessarily.

  In the sixth invention, not only when the support portion receives an axial force, but also when the support portion receives a force in a direction orthogonal to the axial direction, the deformation of the support portion can be suppressed.

It is sectional drawing of the compressor which concerns on embodiment of this invention. It is the II-II sectional view taken on the line of FIG. It is the III-III sectional view taken on the line of FIG. (A) is the elements on larger scale of FIG. 1, (b) is sectional drawing of the compressor of a comparative example, (c) is sectional drawing of the conventional compressor. It is a partial expanded sectional view of the compressor concerning other embodiments of the present invention. It is a partial expanded sectional view of the compressor concerning other embodiments of the present invention. (A) is a top view of the front head of the compressor which concerns on other embodiment of this invention, (b) is BB sectional drawing of (a). It is a partial expanded sectional view of the compressor concerning other embodiments of the present invention. It is sectional drawing of the compressor which concerns on other embodiment of this invention. It is sectional drawing of the compressor which concerns on other embodiment of this invention.

Embodiments of the present invention will be described below.
As shown in FIG. 1, the compressor 1 of this embodiment includes a casing 2, a compression mechanism 9 and a drive mechanism 6 accommodated in the casing 2. The compressor 1 is used by being incorporated in a refrigeration cycle such as an air conditioner, for example, and compresses the refrigerant (CO 2 in this embodiment) supplied from the suction pipe 3 and discharges it from the discharge pipe 4. The compressor 1 is installed in the direction shown in FIG. 1, that is, the direction in which the direction of the shaft 8 is the vertical direction. In FIG. 1, hatching indicating a cross section of the drive mechanism 6 is omitted.

  The casing 2 is a cylindrical container closed at both ends, and an electric current is supplied to the upper portion of the discharge pipe 4 for discharging the compressed refrigerant and to a coil of a stator 7b described later of the drive mechanism 6. A terminal terminal 5 is provided for supply. In FIG. 1, wiring for connecting the coil and the terminal terminal 5 is omitted. Further, a suction pipe 3 for introducing a refrigerant into the compressor 1 is provided on a side portion of the casing 2. Lubricating oil L for smoothing the operation of the sliding portion of the compression mechanism 9 is stored in the lower part of the casing 2.

  The drive mechanism 6 is disposed above the compression mechanism 9 and drives the compression mechanism 9. The drive mechanism 6 includes a motor 7 serving as a drive source and a shaft 8 for transmitting the drive force of the motor 7 to the compression mechanism 9.

  The motor 7 includes a substantially annular stator 7b fixed to the inner peripheral surface of the casing 2, and a substantially annular rotor 7a disposed on the radially inner side of the stator 7b via an air gap. It is configured. The rotor 7a has a magnet (not shown), and the stator 7b has a coil. The rotor 7a rotates by an electromagnetic force generated by passing a current through the coil of the stator 7b. The outer peripheral surface of the stator 7b is not in close contact with the inner peripheral surface of the casing 2 over the entire periphery, and the outer peripheral surface of the stator 7b extends in the vertical direction and communicates with the upper and lower spaces of the motor 7. Are formed side by side in the circumferential direction.

The shaft 8 is fixed to the inner peripheral surface of the rotor 7a and rotates integrally with the rotor 7a.
The shaft 8 has an eccentric portion 8a at a position in the compression chamber 11 described later. The eccentric portion 8 a is formed in a columnar shape, and its axis is eccentric from the rotation center of the shaft 8. A roller 21 described later of the compression mechanism 9 is mounted on the outer peripheral surface of the eccentric portion 8a.

  An oil supply passage 8b extending in the vertical direction is formed inside the lower half of the shaft 8. A spiral blade-shaped pump member (not shown) that sucks the lubricating oil L into the oil supply passage 8b as the shaft 8 rotates is inserted into the lower end portion of the oil supply passage 8b. Further, the shaft 8 is formed with a plurality of discharge holes 8 c for discharging the lubricating oil L in the oil supply passage 8 b to the outside of the shaft 8.

  The compression mechanism 9 includes a cylinder 10, a piston 20, a front head (end plate member) 30, a muffler 40, and a rear head 50. These are all formed of a metal material, and the parts other than the muffler 40 are manufactured by sintering, casting, cutting, or the like. The muffler 40 is manufactured by drawing or the like.

  As shown in FIG. 2, the cylinder 10 is a substantially annular member, and a compression chamber 11 is formed at the center thereof. The upper opening of the compression chamber 11 is closed by the lower surface of the front head 30, and the lower opening of the compression chamber 11 is closed by the upper surface of the rear head 50.

  Further, the cylinder 10 is formed with a suction hole 12 for introducing the refrigerant into the compression chamber 11. The suction hole 12 extends in the radial direction. As shown in FIG. 1, the distal end of the suction pipe 3 is fitted into the radially outer end of the suction hole 12. Further, as shown in FIG. 2, the cylinder 10 is formed with a blade accommodating portion 13 having a shape that is recessed radially outward from the peripheral wall surface of the compression chamber 11. The blade accommodating part 13 penetrates the cylinder 10 in the vertical direction.

  As shown in FIG. 2, the outer diameter of the cylinder 10 is not constant, and the diameter of the radially outer portion of the blade housing portion 13 and the suction hole 12 is the diameter of the other portion 10a (hereinafter referred to as the small diameter surface 10a). It is larger than R1.

  As shown in FIG. 2, the piston 20 includes an annular roller 21 and a blade 22 that extends radially outward from the outer peripheral surface of the roller 21. The roller 21 is mounted so as to be rotatable relative to the outer peripheral surface of the eccentric portion 8 a and is disposed in the compression chamber 11. The blade 22 is disposed between the pair of bushes 14 disposed in the blade accommodating portion 13 so as to be able to advance and retreat. The pair of bushes 14 has a shape obtained by semi-dividing a substantially cylindrical member. The pair of bushes 14 can swing in the blade accommodating portion 13 with the blade 22 disposed therebetween. Therefore, the blade 22 can move forward and backward in the blade accommodating portion 13 and can swing around the pair of bushes 14.

  As shown in FIG. 1, the front head 30 is disposed on the upper side of the cylinder 10 and is fixed to the inner peripheral surface of the casing 2. The front head 30 includes a main body portion 31, a boss portion 35, a support portion (support portion) 36, and a ring portion 37.

  The main body 31 is formed in a disk shape having a hole in the center. The lower surface of the main body 31 is in contact with the upper end surface of the cylinder 10 and is fixed to the cylinder 10 with bolts. The shaft 8 is rotatably inserted in the central hole of the main body 31. The outer diameter of the main body 31 is the same as the diameter R1 of the small diameter surface 10a of the cylinder 10.

  As shown in FIG. 3, the body portion 31 is formed with a discharge hole 32 for discharging the refrigerant compressed in the compression chamber 11. A concave portion 33 is formed on the upper surface of the main body portion 31, and an outlet of the discharge hole 32 is formed on the bottom surface of the concave portion 33. A valve mechanism 34 that opens and closes the outlet of the discharge hole 32 is disposed in the recess 33. The valve mechanism 34 has a leaf spring and is configured to open the outlet of the discharge hole 32 when the pressure in the compression chamber 11 is equal to or higher than a predetermined pressure. In FIG. 3, substantially half of the muffler 40 is omitted.

  As shown in FIG. 1, the boss portion 35 protrudes upward from the center of the upper surface of the main body portion 31 and is formed in a cylindrical shape. The inner diameter of the boss portion 35 is the same as that of the central hole of the main body portion 31, and the shaft 8 is rotatably inserted into the boss portion 35.

  As shown in FIG. 1, the support portion 36 extends in an upward oblique direction from the outer peripheral end of the main body portion 31 toward the inner peripheral surface of the casing 2. In other words, the support portion 36 is inclined so as to be disposed on the radially outer side as it is separated upward from the cylinder 10. The support part 36 is formed in an annular shape. The position of the lower end of the boundary between the support portion 36 and the main body portion 31 coincides with the position of the upper end of the small diameter surface 10 a of the cylinder 10. Further, the outer peripheral end of the support portion 36 is connected to the inner peripheral surface of the cylindrical ring portion 37, and the outer peripheral surface of the ring portion 37 is fixed to the inner peripheral surface of the casing 2 by spot welding or the like. .

  The support portion 36 has a constant plate thickness, and the upper surface and the lower surface are parallel to each other. As shown in FIG. 4A, the inclination angle of the support portion 36 with respect to the vertical direction (axial direction) is α. In the present embodiment, the inclination angle α is 60 °, but is not limited to this. It may be 0 ° <α <90 °, and preferably 30 ° ≦ α ≦ 60 °. In FIG. 4A, the muffler 40 is omitted.

  As shown in FIG. 3, a plurality of oil return holes 38 aligned in the circumferential direction are formed in the support portion 36. Each oil return hole 38 extends along the circumferential direction. As shown in FIG. 4A, of the inner surface of the oil return hole 38, the radially outer portion is the first surface 38a, the radially inner portion is the second surface 38b, and the first surface 38a and the second surface 38b. A portion between the first and second surfaces 38c is defined as a third surface 38c.

  The first surface 38a and the second surface 38b are parallel and are inclined with respect to the vertical direction so as to be arranged radially inward as going upward. More specifically, the first surface 38a and the second surface 38b extend in a direction orthogonal to the inclination direction of the support portion 36 (the direction of the two-dot chain line in FIG. 4A). The second surface 38 b is configured by the outer peripheral surface of the main body portion 31. The second surface 38b is formed in a region overlapping the cylinder 10 when viewed from the up-down direction (axial direction). Specifically, the position of the lower end of the second surface 38 b matches the position of the upper end of the small diameter surface 10 a of the cylinder 10. That is, at the boundary surface between the front head 30 and the cylinder 10, the position of the lower end of the second surface 38 b of the oil return hole 38 coincides with the position of the outer edge of the cylinder 10.

  Further, the first surface 38a is disposed at the same height as a part of the second surface 38b. Therefore, the upper end portion of the second surface 38b and the lower end portion of the first surface 38a face each other in the radial direction (horizontal direction). The shortest distance between the first surface 38a and the second surface 38b (the distance in the direction perpendicular to the first surface 38a and the second surface 38b) is D1. Further, the flow passage area of the oil return hole 38 is substantially equal to a value obtained by multiplying the distance D1 by the circumferential length of the oil return hole 38.

Here, the case where the diameter of the casing is reduced while keeping the diameter of the compression chamber constant for the purpose of downsizing the compressor will be described with reference to FIG.
FIG. 4C is a cross section of a conventional compressor. In this compressor, the diameter of the casing 80 is larger than the diameter of the casing 2 of the present embodiment, and the diameter of the small-diameter surface 81a of the cylinder 81 and the diameter of the compression chamber (not shown) are the same as those of the cylinder 10 of the present embodiment. It is. The front head 82 shown in FIG. 4C includes a main body portion 83 that is in contact with the upper end surface of the cylinder 81, a support portion 84 that extends horizontally from the outer peripheral end of the main body portion 83, a ring portion 85, and a boss portion. The support portion 84 is formed with a plurality of oil return holes 86 extending in the vertical direction. The shortest distance between the radially outer surface 86a and the radially inner surface 86b of the oil return hole 86 and the circumferential length of the oil return hole 86 are the same as those of the first surface 38a of the oil return hole 38 of the present embodiment. This is the same as the shortest distance D1 from the second surface 38b and the circumferential length. Therefore, the flow passage area of the oil return hole 86 is the same as that of the present embodiment.
FIG. 4B shows a comparative example, and shows a cross section when the diameter of the compressor casing shown in FIG. 4C is reduced to the same size as the present embodiment.
As in this comparative example, the support portion 94 of the front head 92 extends in the horizontal direction (direction orthogonal to the axial direction), and the oil return hole 96 extends in the vertical direction (axial direction). However, when the diameter of the casing 90 is reduced while the diameter of the cylinder 91 (and the diameter of the compression chamber) is kept constant, the shortest distance D9 between the radially outer surface 96a and the radially inner surface 96b of the oil return hole 96 is Since it becomes smaller than the conventional example of FIG.4 (c), the oil passage amount same as a prior art example cannot be ensured.
On the other hand, in this embodiment, even if the diameter of the casing 2 is reduced by providing the oil return hole 38 so as to be inclined with respect to the axial direction in the support portion 36 that is inclined with respect to the horizontal. The shortest distance between the first surface 38a and the second surface 38b of the oil return hole 38 can be maintained equivalent to that of the conventional example of FIG. 4C, and the same oil passage amount as that of the conventional example can be maintained. That is, in the present embodiment, the diameter of the compression chamber 11 can be made relatively larger than the diameter of the casing 2 while ensuring the amount of oil passing through the oil return hole 38.

  The muffler 40 is provided in order to reduce noise accompanying the discharge of the refrigerant. As shown in FIG. 1, the muffler 40 is disposed on the upper side of the front head 30 and is fixed to the main body 31 with bolts. The muffler 40 forms a muffler space M with the front head 30. Further, as shown in FIG. 3, the muffler 40 is formed with a muffler discharge hole 41 for discharging the refrigerant in the muffler space M.

  As shown in FIG. 1, the rear head 50 is a substantially annular member, and is disposed on the lower side of the cylinder 10 and fixed to the cylinder 10 with bolts. A shaft 8 is rotatably inserted into the rear head 50.

Next, operation | movement of the compressor 1 of this embodiment is demonstrated.
When the shaft 8 is rotated by driving the motor 7 while supplying the refrigerant into the compression chamber 11 from the suction pipe 3 through the suction hole 12, the roller 21 attached to the eccentric portion 8 a Move in the circumferential direction. Thereby, since the volume of the space formed by the side surface of the piston 20 and the peripheral wall surface of the compression chamber 11 changes, the refrigerant is compressed in the compression chamber 11.

  When the pressure in the compression chamber 11 becomes equal to or higher than a predetermined pressure, the valve mechanism 34 provided in the front head 30 is opened, and the refrigerant in the compression chamber 11 is discharged into the muffler space M through the discharge hole 32. . The refrigerant discharged into the muffler space M is discharged from the muffler discharge hole 41 of the muffler 40 to the outside of the compression mechanism 9, and then passes through an air gap between the stator 7b and the rotor 7a, and finally. Then, the gas is discharged from the discharge pipe 4 to the outside of the casing 2.

  At this time, a part of the lubricating oil L discharged into the compression chamber 11 from the discharge hole 8c of the shaft 8 is discharged out of the compression mechanism 9 together with the refrigerant. Part of the lubricating oil L discharged outside the compression mechanism 9 passes through the oil return hole 38 of the front head 30 and is returned to the lower portion of the casing 2. Further, another part of the lubricating oil L discharged to the outside of the compression mechanism 9 moves to a space above the motor 7 together with the refrigerant, and then a recess (not shown) formed on the outer peripheral surface of the stator 7b. The oil passes through the oil return hole 38 of the front head 30 and is returned to the lower portion of the casing 2.

  In the compressor 1 of the present embodiment, since the support portion 36 extends while being inclined with respect to the horizontal direction, the compression mechanism 9 vibrates in the vertical direction with respect to the casing 2 to cause the support portion 36 to move vertically. When a force acts, a component force in a direction parallel to the extending direction of the support portion 36 and a component force in a direction orthogonal to the extending direction of the support portion 36 are generated. Therefore, compared with the case where the support portion extends horizontally, the force in the direction perpendicular to the extending direction of the support portion 36 is reduced by the amount of the component force in the direction parallel to the extending direction of the support portion 36. can do. Therefore, it is possible to suppress the support portion 36 from being bent and deformed.

  Further, in the present embodiment, the oil return hole 38 is formed in the support portion 36 that is inclined with respect to the horizontal direction so that the oil return hole 38 is inclined with respect to the vertical direction. The diameter of the compression chamber relative to the inner diameter of the casing can be made relatively large as compared with the case where the oil return hole having the same flow path area is provided so as to be orthogonal to the support portion. Since the oil passage amount of the oil return hole depends on the flow path area, in the present invention, the diameter of the compression chamber can be made relatively large with respect to the inner diameter of the casing while maintaining the oil passage amount of the oil return hole. .

  In the present embodiment, the lower end portion of the first surface 38a and the upper end portion of the second surface 38b of the oil return hole 38 are opposed to each other in the radial direction. Therefore, compared with the case where the first surface 38a and the second surface 38b do not oppose each other in the radial direction, the radial length of the range in which the oil return hole 38 is formed in the front head 30 can be reduced.

  Further, in the present embodiment, the oil return hole 38 is orthogonal to the inclination direction of the support portion 36, so that the amount of oil passing through the oil return hole 38 can be reliably increased.

  In the present embodiment, the second surface 38b of the oil return hole 38 is formed in a region overlapping the cylinder 10 when viewed from the axial direction (vertical direction). Therefore, compared with the case where all the oil return holes are formed radially outside the small diameter surface 10a of the cylinder 10, the flow area of the oil return holes can be increased.

Further, in the present embodiment, the position of the lower end of the second surface 38 b of the oil return hole 38 coincides with the position of the upper end of the small diameter surface 10 a of the cylinder 10. Therefore, compared with the case where the position of the lower end of the second surface is radially outside the position of the upper end of the small diameter surface 10a of the cylinder 10 (see, for example, FIG. 5A), the flow area of the oil return hole is reduced. Can be big.
Further, compared with the case where the position of the lower end of the second surface is radially inward from the position of the upper end of the small diameter surface 10a of the cylinder 10, all the spaces in the oil return hole are effectively used as the passage of the lubricating oil L. Since it can utilize, it can prevent that the intensity | strength of the support part 36 falls wastefully.

  In the present embodiment, the inclination angle α of the support portion 36 is 60 °. When the inclination angle α of the support portion 36 is not less than 30 ° and not more than 60 °, not only when the support portion 36 receives a vertical force, the compression mechanism 9 vibrates in the horizontal direction and the support portion 36 moves in the horizontal direction. Even when force is received, deformation of the support portion 36 can be suppressed.

  As mentioned above, although embodiment of this invention was described, it should be thought that the specific structure of this invention is not limited to the said embodiment. The scope of the present invention is shown not only by the description of the above-described embodiment but also by the scope of claims for patent, and further includes meanings equivalent to the scope of claims for patent and all modifications within the scope. Note that the modifications described below can be implemented in appropriate combination.

In the above embodiment, at the boundary surface between the front head 30 and the cylinder 10, the position of the lower end of the second surface 38b of the oil return hole 38 coincides with the position of the outer edge (small diameter surface 10a) of the cylinder 10. It is not limited to this configuration.
For example, as in the oil return hole 138 shown in FIG. 5A, the lower end of the second surface 138b may be formed to be radially outward from the upper end of the small diameter surface 10a of the cylinder 10. Good.
Conversely, the position of the lower end of the second surface of the oil return hole may be formed to be radially inward from the position of the upper end of the small diameter surface 10a of the cylinder 10.

The oil return hole 38 does not necessarily have to be orthogonal to the inclination direction of the support portion 36.
For example, as shown in FIG. 5B, the oil return hole 238 extends in a direction closer to the horizontal direction than the direction orthogonal to the inclination direction of the support portion 236 (the direction of the two-dot chain line in the figure). It may be. D2 shown in FIG. 5B is the shortest distance between the first surface (radially outer surface) 238a of the oil return hole 238 and the second surface (radially inner surface) 238b. The flow path area substantially coincides with a value obtained by multiplying the distance D2 by the circumferential length of the oil return hole 238.
For example, as shown in FIG. 5C, the oil return hole 338 extends in a direction closer to the vertical direction than the direction orthogonal to the inclination direction of the support portion 336 (the direction of the two-dot chain line in the figure). It may exist (except when extending in the vertical direction). D3 shown in FIG. 5C is the shortest distance between the first surface (radially outer surface) 338a of the oil return hole 338 and the second surface (radially inner surface) 338b. Is substantially equal to a value obtained by multiplying the distance D3 by the circumferential length of the oil return hole 338.

  In the above embodiment, the first surface 38a and the second surface 38b of the oil return hole 38 are parallel, but they are not necessarily parallel.

In the above embodiment, the first surface (radially outer surface) 38b of the oil return hole 38 is inclined with respect to the axial direction (vertical direction). For example, as shown in FIG. If the second surface 438b of the hole 438 is inclined with respect to the vertical direction, the first surface 438a of the oil return hole 438 may extend in the vertical direction. In FIG. 5D, the first surface 438 a is configured by the inner peripheral surface of the ring portion 37.
In the present invention, “the oil return hole is inclined with respect to the axial direction” means that the entire inner peripheral surface of the oil return hole 38 is inclined with respect to the axial direction as in the above embodiment. In addition, as in the present modified embodiment, the case where only the second surface (the radially inner surface) of the oil return hole 438 is inclined with respect to the axial direction is included. In this case, the flow path area of the oil return hole is defined as the shortest distance between the first surface and the second surface in the direction orthogonal to the second surface (for example, the distance D4 shown in FIG. 5D) and the circumferential direction of the oil return hole. It almost matches the value multiplied by the length.

  In the above embodiment, the oil return hole 38 is formed only in the support portion 36. However, for example, as in the oil return holes 238 and 538 shown in FIG. 5B and FIG. 536) and the main body (231, 531). In FIG. 5 (e), the extending direction of the support portion 536 and the extending directions of the first surface 538a and the second surface 538b are the same as those in the above embodiment, and the plate thickness of the main body portion 531 is the same as that described above. It is larger than the main body 31 of the embodiment.

As described in the above embodiment, the inclination angle α of the support portion 36 is not limited to 60 °. For example, when the inclination angle α is smaller than the above embodiment (specifically, α = 30 °) as in the support portion 636 shown in FIG. 6A, the flow area of the oil return hole 638 is larger than that in the above embodiment. Can also be larger.
Thus, the smaller the inclination angle α, the larger the channel area of the oil return hole. However, in order to suppress the deformation of the support portion 36 both when the vertical force is applied to the support portion 36 and when the horizontal force is applied, the inclination angle α is 30 ° or more and 60 ° or less. The range of is preferable.

In the above embodiment, at the boundary between the front head 30 and the cylinder 10, the position of the lower end of the boundary between the support portion 36 and the main body portion 31 coincides with the position of the outer end (small diameter surface 10 a) of the cylinder 10. The configuration is not limited to this.
For example, as shown in FIG. 6B, the lower end position of the boundary between the support portion 736 and the main body portion 731 may be formed to be radially inward from the position of the small diameter surface 10 a of the cylinder 10. . In FIG. 6B, the oil return hole 738 is formed so that the lower end of the second surface 738b is located at the same position as the small-diameter surface 10a when viewed from the vertical direction.
Further, the lower end position of the boundary between the support portion and the main body portion may be formed so as to be radially outside the position of the upper end of the small diameter surface 10a of the cylinder 10.

  In the above embodiment, the lower surface of the support portion 36 extends from the outer peripheral end of the lower surface of the main body portion 31 toward the inner peripheral surface of the casing 2. For example, FIG. As shown in d), the lower surface of the support portion (836, 936) may extend from the outer peripheral surface of the main body portion (831, 931) toward the inner peripheral surface of the casing 2. In FIG. 6C, the oil return hole 838 is formed only in the support portion 836, and in FIG. 6D, the oil return hole 938 is formed in the support portion 936 and the main body portion 931. .

  In the front head 30 of the above-described embodiment, the support portion 36 is annular and is provided on the outer peripheral end of the main body portion 31 over the entire circumference, but is not limited to this configuration. For example, like a front head 1030 shown in FIG. 7, a fan-shaped support portion 1036 viewed from above and a fan-shaped flat portion 1039 extending horizontally and viewed from above on the outer peripheral end of the main body 31. However, the structure arrange | positioned along with the circumferential direction may be sufficient. In FIG. 7A, the support portion 1036 is indicated by dot hatching. The support portion 1036 (or the support portion 1036 and the main body portion 1031) has an oil return hole 1038 that is inclined with respect to the vertical direction. Further, the flat portion 1039 may or may not have a through hole through which oil passes.

  In the said embodiment, although the compressor 1 is installed in the direction in which the direction of the shaft 8 becomes an up-down direction, you may install in the direction other than this.

  In the above embodiment, the front head 30 has the short cylindrical ring portion 37 at the outer peripheral end of the support portion 36, but for example, as shown in FIG. 8, the support portion 1136 has no ring portion. The outer peripheral end of the casing 2 may be fixed to the inner peripheral surface of the casing 2. In FIG. 8, the first surface 1138a of the oil return hole 1138 is parallel to the second surface 1138b and is orthogonal to the extending direction (inclination direction) of the support portion 1136, but is not limited to this configuration. .

  In the above embodiment, the outer peripheral surface of the front head 30 is fixed to the inner peripheral surface of the casing 2 and the front head 30 constitutes the end plate member of the present invention. For example, the compressor 1201 shown in FIG. Like the compression mechanism 1209, the outer peripheral surface of the rear head 1250 may be fixed to the inner peripheral surface of the casing 2, and the rear head 1250 may constitute the end plate member of the present invention. The rear head 1250 includes a main body portion 1251, a boss portion 1255, a support portion 1256, and a ring portion 1257. The support portion 1256 is inclined so as to be arranged on the radially outer side as it moves away from the cylinder 10 in the downward direction. In addition, a plurality of oil return holes 1258 are formed side by side in the circumferential direction in the support portion 1256 (or the support portion 1256 and the main body portion 1251). The oil return hole 1258 is inclined so as to be disposed radially inward as it moves downward from the cylinder 10. Further, the outer diameter of the front head 1230 of the compression mechanism 1209 is substantially the same as the diameter of the small diameter portion 10 a of the cylinder 10.

  In the above-described embodiment, the compression mechanism 9 has a configuration in which the piston 20 including the roller 21 and the blade 22 is disposed inside the cylinder 10. For example, as illustrated in FIG. 10, the roller 13 is disposed inside the cylinder 1310. The compression mechanism 1309 may be configured such that 1360 and the vane 1361 are arranged. The cylinder 1310 is formed with a compression chamber 1311, a suction hole 1312, and a vane storage portion 1315 that stores the vane 1361. The roller 1360 is mounted on the outer peripheral surface of the eccentric portion 8a. The vane 1361 is biased by a biasing spring 1316 provided in the vane housing portion 1315, and the tip is pressed against the outer peripheral surface of the roller 1360. When the roller 1360 moves in the circumferential direction along the circumferential wall surface of the compression chamber 1311 as the eccentric portion 8a (shaft 8) rotates, the roller 1360 is formed by the outer circumferential surface of the roller 1360, the side surface of the vane 1361, and the circumferential wall surface of the compression chamber 1311. Since the volume of the space to be changed changes, the refrigerant is compressed in the compression chamber 1311.

  In the above embodiment, the present invention is applied to a one-cylinder compressor, but the present invention may be applied to a two-cylinder compressor.

  If the present invention is used, the deformation of the end plate portion can be suppressed, and the diameter of the compression chamber can be made relatively large with respect to the diameter of the casing while ensuring the amount of oil passing through the oil return hole.

DESCRIPTION OF SYMBOLS 1 Compressor 2 Casing 9 Compression mechanism 10 Cylinder 11 Compression chamber 30 Front head (end plate member)
31 Main body 36 Support part (support part)
38 Oil return hole

Claims (6)

A compressor comprising a casing and a compression mechanism housed in the casing,
The compression mechanism is
A cylinder having a compression chamber;
An end plate member disposed at an axial end of the cylinder and fixed to an inner peripheral surface of the casing;
The end plate member is
A support portion that is inclined so as to be disposed radially outward as it is axially separated from the cylinder;
A compressor having an oil return hole formed in a region including the support portion and inclined with respect to the axial direction.   2. The compressor according to claim 1, wherein a portion on the radially inner side and a portion on the radially outer side of the oil return hole face each other in the radial direction.   The compressor according to claim 1, wherein the oil return hole is orthogonal to an inclination direction of the support portion.   The compressor according to any one of claims 1 to 3, wherein a part of the oil return hole on the radially inner side is formed in a region overlapping with the cylinder when viewed from the axial direction.   5. The compression according to claim 4, wherein a position of a radially inner end of the oil return hole coincides with a position of an outer edge of the cylinder at a boundary between the end plate member and the cylinder. Machine.   The compressor according to claim 1, wherein the support portion is inclined within a range of 30 ° to 60 ° with respect to the axial direction.

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