JPWO2016174751A1 - Compressor - Google Patents

Abstract

The compressor (1) contacts the cylinder (11), the rolling piston (15) rotating eccentrically along the inner peripheral surface (11a) of the cylinder (11), and the outer peripheral surface of the rolling piston (15), A vane (17) that divides the space in the cylinder (11) into a suction chamber and a compression chamber, and a vane spring (19) that biases the vane (17) toward the rolling piston (15), 11) has a spring insertion hole (18) into which the vane spring (19) is inserted. The spring insertion hole (18) has a height dimension H11 in the axial direction of the cylinder (11) of the cylinder (11). ) Has a hole shape smaller than the width dimension W11 in the tangential direction, the vane spring (19) is a coil spring, and the vane spring (19) is a cylinder (11). Height H21 in the axial direction of has a smaller winding shape than the width W21 in the tangential direction of the cylinder (11).

Description

  The present invention relates to a compressor that compresses a fluid.

  Patent Document 1 describes a rotary compressor. This rotary compressor includes a rolling piston, a vane, and a vane spring. The vane spring is accommodated in a spring insertion hole provided in the cylinder. The winding shape of the vane spring and the hole shape of the spring insertion hole are both round.

JP 61-49188

  In recent years, there has been a demand for low GWP refrigerant and high efficiency compressors in response to increasing environmental awareness and stricter energy-saving regulations. Due to the low GWP of the refrigerant, the operating pressure of the refrigerant is higher than before. For this reason, in the hermetic compressor, leakage of refrigerant from the high pressure side space of the compression chamber to the low pressure side space is likely to occur.

  For this reason, recent sealed rotary compressors tend to reduce the thickness of the cylinder forming the compression chamber. When the thickness of the cylinder is reduced, the contact length between the cylinder and the sliding component can be shortened, so that leakage of the refrigerant from the high pressure side space to the low pressure side space of the compression chamber can be reduced.

  The compression mechanism of the hermetic rotary compressor is fixed by welding a plurality of locations on the outer peripheral surface of the flange portion of the upper bearing or the outer peripheral surface of the rib portion of the cylinder to the hermetic container.

  However, when the thickness of the cylinder is reduced, the cross-sectional area of the bridge portion formed on the back side of the vane groove is reduced. For this reason, when the outer periphery of the rib portion of the cylinder is welded to the sealed container, the inner peripheral surface of the cylinder and the vane groove are easily distorted. If the distortion of the inner peripheral surface of the cylinder or the vane groove is excessively increased, the airtightness in the compression mechanism is lowered and the compression performance is lowered. Further, since the contact between the cylinder and the sliding component becomes strong, the compressor is likely to fail. Therefore, when the thickness of the cylinder is reduced, the compressor performance cannot be maintained.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a compressor capable of reducing the thickness of a cylinder while maintaining performance.

  A compressor according to the present invention is in contact with a hollow cylinder housed in a container, a rolling piston that rotates eccentrically along the inner peripheral surface of the cylinder, and an outer peripheral surface of the rolling piston, A vane that divides the space into a suction chamber and a compression chamber; and a vane spring that urges the vane toward the rolling piston. The cylinder has a spring insertion hole into which the vane spring is inserted. The spring insertion hole has a hole shape in which the height dimension in the axial direction of the cylinder is smaller than the width dimension in the tangential direction of the cylinder in at least a part of the spring insertion hole in the axial direction. The vane spring is a coil spring, and the vane spring is at least in the axial direction of the vane spring. In part, in which the height in the axial direction of the cylinder has a smaller winding shape than the width dimension in the tangential direction of the cylinder.

  According to the present invention, since the size of the spring insertion hole in the axial direction of the cylinder can be reduced, the thickness of the cylinder can be reduced while maintaining the performance of the compressor.

It is a longitudinal cross-sectional view which shows schematic structure of the compressor 1 which concerns on Embodiment 1 of this invention. It is a perspective view which shows the partial cross-sectional structure of the compression mechanism 10 of the compressor 1 which concerns on Embodiment 1 of this invention. It is a top view which shows the structure of the cylinder 11 of the compressor 1 which concerns on Embodiment 1 of this invention. In the general compression mechanism 10, it is a figure which shows collectively the cross-sectional structure in case the thickness of the cylinder 11 is relatively thick, and the cross-sectional structure in case the thickness of the cylinder 11 is relatively thin. It is a perspective view which shows the structure of the cylinder 11 of the compressor 1 which concerns on Embodiment 1 of this invention. It is a figure which shows the structure which looked at the vane spring 19 of the compressor 1 which concerns on Embodiment 1 of this invention to the axial direction. It is a perspective view which shows the structure of the cylinder 11 of the compressor 1 which concerns on Embodiment 2 of this invention. It is a figure which shows the structure which looked at the vane spring 19 of the compressor 1 which concerns on Embodiment 2 of this invention to the axial direction. It is a perspective view which shows the structure of the cylinder 11 of the compressor 1 which concerns on Embodiment 3 of this invention. It is a figure which shows the structure which looked at the vane spring 19 of the compressor 1 which concerns on Embodiment 3 of this invention to the axial direction. It is a perspective view which shows the structure of the cylinder 11 of the compressor 1 which concerns on Embodiment 4 of this invention. It is a figure which shows the structure which looked at the vane spring 19 of the compressor 1 which concerns on Embodiment 4 of this invention to the axial direction.

Embodiment 1 FIG.
A compressor according to Embodiment 1 of the present invention will be described. FIG. 1 is a longitudinal sectional view showing a schematic configuration of a compressor 1 according to the present embodiment. The compressor 1 is a fluid machine that compresses and discharges a fluid (in this example, a low-pressure gas refrigerant in a refrigeration cycle), and is one of the components of a refrigeration cycle used in, for example, an air conditioner or a refrigerator. Is. In the present embodiment, as the compressor 1, a vertical type hermetic rotary compressor is illustrated. In the following drawings including FIG. 1, the dimensional relationship and shape of each component may differ from the actual ones. Moreover, the positional relationship (for example, vertical relationship etc.) between each structural member in a specification is a thing when it installs in the state which can use a vertical installation sealed rotary compressor in principle.

  As shown in FIG. 1, the compressor 1 includes a compression mechanism 10 that compresses a gas refrigerant and an electric mechanism 50 that drives the compression mechanism 10. The compression mechanism 10 and the electric mechanism 50 are accommodated in the sealed container 60 and fixed to the sealed container 60 by welding or shrink fitting, respectively. Refrigerating machine oil that lubricates the sliding portions of the compressor 1 is stored at the bottom of the sealed container 60.

  The electric mechanism 50 includes a stator 51 and a rotor 52. The outer peripheral portion of the stator 51 is fixed to the inner peripheral surface of the sealed container 60. A drive shaft 53 is coaxially fixed to the rotor 52. The drive shaft 53 is formed with an eccentric portion 53 a having a central axis at a position shifted from the rotation axis of the drive shaft 53.

  The compression mechanism 10 is disposed below the electric mechanism 50 in the sealed container 60. The compression mechanism 10 includes a hollow cylinder 11 having a cylindrical opening inside, an upper bearing 12 that is disposed at an upper end in the axial direction of the cylinder 11 and rotatably supports the drive shaft 53, and an axial direction of the cylinder 11. The lower bearing 13 is disposed at the lower end and rotatably supports the drive shaft 53. The upper bearing 12 and the lower bearing 13 also serve as an upper end plate and a lower end plate of the cylinder 11, respectively. A discharge muffler 14 is attached to the upper bearing 12. A discharge muffler chamber is formed between the upper bearing 12 and the discharge muffler 14 to reduce the pulsation of the refrigerant compressed and discharged by the compression mechanism 10.

  FIG. 2 is a perspective view showing a partial cross-sectional configuration of the compression mechanism 10. In FIG. 2, the upper bearing 12 is not shown. FIG. 3 is a top view showing the configuration of the cylinder 11. As shown in FIGS. 2 and 3, a plurality of rib portions 11 b projecting to the outer peripheral side are formed on the outer peripheral portion of the cylinder 11. The outer peripheral surface 11c of the rib portion 11b (hereinafter sometimes referred to as “the outer peripheral surface 11c of the cylinder 11”) is fixed to the inner peripheral surface of the sealed container 60 by welding or the like.

  In the space in the cylinder 11, a rolling piston 15 that is slidably fitted into the eccentric portion 53 a is provided. The rolling piston 15 rotates eccentrically along the inner peripheral surface 11a of the cylinder 11 as the eccentric portion 53a rotates. A vane groove 16 is formed from the inner peripheral surface 11 a of the cylinder 11 toward the radially outer side of the cylinder 11. A vane 17 that divides the space in the cylinder 11 into a suction chamber and a compression chamber is accommodated in the vane groove 16 so as to be slidable back and forth. A bridge portion 20 is formed on the back side of the vane groove 16 (that is, between the vane groove 16 and the outer peripheral surface 11 c of the cylinder 11).

  Between the vane groove 16 and the outer peripheral surface 11 c of the cylinder 11, a spring insertion hole 18 penetrating the bridge portion 20 along the radial direction of the cylinder 11 is formed. A vane spring 19 that urges the vane 17 toward the rolling piston 15 is inserted into the spring insertion hole 18 from the outer peripheral surface 11c side. The vane spring 19 is a compression coil spring. Since the spring insertion hole 18 communicates with the space inside the sealed container 60 outside the cylinder 11, the discharge pressure acts on the back side of the vane 17. The vane 17 is pressed against the outer peripheral surface of the rolling piston 15 by the pressing force due to the pressure difference between the back surface side and the tip end side and the urging force by the vane spring 19. Thereby, the vane 17 reciprocates in the vane groove 16 following the eccentric rotation of the rolling piston 15.

  Returning to FIG. 1, the compressor 1 is provided adjacent to the outside of the hermetic container 60, and stores the low-pressure refrigerant flowing from the outside (for example, the evaporator side of the refrigeration cycle) and separates the refrigerant from the accumulator. 61, a suction pipe 62 for introducing the gas refrigerant in the accumulator 61 into the sealed container 60, and a suction port 63 for guiding the gas refrigerant introduced into the sealed container 60 to the suction chamber in the cylinder 11. Yes. Further, the compressor 1 is discharged into a space inside the sealed container 60 and a discharge port (not shown) for discharging the high-pressure gas refrigerant compressed in the compression chamber inside the cylinder 11 into the space inside the sealed container 60. And a discharge pipe 64 for discharging high-pressure gas refrigerant to the outside (for example, the condenser side of the refrigeration cycle).

  In the compressor 1 configured as described above, when the rotor 52 is rotated by energization of the stator 51, the drive shaft 53 fitted in the rotor 52 is rotated. As a result, the rolling piston 15 slidably fitted into the eccentric portion 53 a of the drive shaft 53 rotates eccentrically (revolves) along the inner peripheral surface 11 a of the cylinder 11. The vane 17 always contacts the outer peripheral surface of the rolling piston 15 by reciprocating in the vane groove 16.

  By the revolving motion of the rolling piston 15 and the reciprocating motion of the vane 17, the volumes of the suction chamber and the compression chamber in the cylinder 11 are gradually changed. Due to the volume change of the suction chamber and the compression chamber, the low pressure gas refrigerant is sucked into the suction chamber via the suction pipe 62 and the suction port 63, and the sucked low pressure gas refrigerant is compressed to high temperature and high pressure in the compression chamber. The compressed high-pressure gas refrigerant is discharged from a discharge valve (not shown) provided in the upper bearing 12 to a space in the sealed container 60 via a discharge muffler chamber. The high-pressure gas refrigerant discharged into the space inside the sealed container 60 is discharged from the discharge pipe 64 to the outside of the sealed container 60.

  Here, a change in the cross-sectional area of the bridge portion 20 when the thickness of the cylinder 11 (length in the axial direction) is varied will be described. FIG. 4 shows a cross-sectional configuration (a) when the cylinder 11 is relatively thick and a cross-sectional configuration (b) when the cylinder 11 is relatively thin in the general compression mechanism 10. FIG.

  4A and 4B, the winding diameter and the wire diameter of the vane spring 19 are the same, and the inner diameter of the spring insertion hole 18 into which the vane spring 19 is inserted is also the same. This is because if the winding diameter of the vane spring 19 is reduced, the winding length of the vane spring 19 becomes insufficient, so that the stress generated in the vane spring 19 during expansion and contraction increases and the vane spring 19 breaks. It is because it ends. Further, when the winding diameter of the vane spring 19 is reduced, if the wire diameter of the vane spring 19 is reduced in order to maintain the stress generated in the vane spring 19, a sufficient urging force against the vane 17 cannot be secured. It is.

  In the configuration shown in FIG. 4B in which the thickness of the cylinder 11 is made thinner than the configuration shown in FIG. 4A, the thickness (axial dimension) of the bridge portion 20 is reduced by the reduction in the thickness of the cylinder 11. As a result, it can be seen that the cross-sectional area of the bridge portion 20 (the area of the hatched portion in FIGS. 4A and 4B) decreases.

  FIG. 5 is a perspective view showing the configuration of the cylinder 11 of the compressor 1 according to the present embodiment. The vertical direction in FIG. 5 represents the axial direction of the cylinder 11. As shown in FIG. 5, the spring insertion hole 18 of the present embodiment has an elliptical flat hole shape in at least a part of the spring insertion hole 18 in the axial direction (stretching direction) (the whole in this example). have. Specifically, the inner diameter of the spring insertion hole 18 in the axial direction of the cylinder 11 is set to a height dimension H11, and the tangential direction of the cylinder 11 in a plane perpendicular to the axial direction of the cylinder 11 (hereinafter simply referred to as “tangential line of the cylinder 11”). The height dimension H11 is smaller than the width dimension W11 (H11 <W11).

  FIG. 6 is a diagram illustrating a configuration in which the vane spring 19 of the compressor 1 according to the present embodiment is viewed in the axial direction. The vertical direction in FIG. 6 represents the axial direction of the cylinder 11 with the vane spring 19 inserted into the spring insertion hole 18. As shown in FIG. 6, the vane spring 19 of the present embodiment has an elliptical flat winding shape in at least a part of the vane spring 19 in the axial direction (in this example, the whole). The vane spring 19 has a winding shape that can be inserted into the spring insertion hole 18 shown in FIG. The vane spring 19 is inserted such that the winding diameter (height dimension H21) in the axial direction of the cylinder 11 is smaller than the winding diameter (width dimension W21) in the tangential direction of the cylinder 11 (H21 <W21). It is inserted into the hole 18.

  As described above, the compressor 1 according to the present embodiment includes the hollow cylinder 11 housed in the sealed container 60, the rolling piston 15 that rotates eccentrically along the inner peripheral surface 11a of the cylinder 11, A vane 17 that contacts the outer peripheral surface of the rolling piston 15 and divides the space in the cylinder 11 into a suction chamber and a compression chamber; and a vane spring 19 that biases the vane 17 toward the rolling piston 15. A spring insertion hole 18 into which the vane spring 19 is inserted is formed. The spring insertion hole 18 has a height dimension H11 in the axial direction of the cylinder 11 at least in a part of the spring insertion hole 18 in the axial direction. Has a flat hole shape smaller than the width dimension W11 in the tangential direction of the cylinder 11, and the vane spring 19 is The vane spring 19 has a winding shape in which the height dimension H21 in the axial direction of the cylinder 11 is smaller than the width dimension W21 in the tangential direction of the cylinder 11 in at least a part of the vane spring 19 in the axial direction. It is what you are doing.

  According to this configuration, since the size of the spring insertion hole 18 in the axial direction of the cylinder 11 can be reduced, the thickness of the cylinder 11 can be reduced while suppressing a reduction in the cross-sectional area of the bridge portion 20. By reducing the thickness of the cylinder 11, the contact length between the cylinder 11 and the sliding component can be shortened, so that the leakage of refrigerant from the high pressure side space to the low pressure side space of the compression chamber can be reduced. Further, by reducing the thickness of the cylinder 11, the compressor 1 can be reduced in size in the axial direction, and the material for manufacturing the compressor 1 can be reduced. Further, by reducing the thickness of the cylinder 11, it is possible to increase the number of cylinders without increasing the shell capacity of the compressor 1.

  Further, since the reduction in the cross-sectional area of the bridge portion 20 can be suppressed, the inner peripheral surface 11a of the cylinder 11 and the vane groove 16 can be made difficult to be distorted. Thereby, it is possible to suppress a decrease in compression performance due to a decrease in airtightness in the compression mechanism 10 and a failure of the compressor 1 due to a strong contact between the cylinder 11 and the sliding component. Therefore, according to the present embodiment, the cylinder 11 can be thinned while maintaining the performance of the compressor 1.

  Further, since the vane spring 19 has a flat winding shape, a necessary winding length can be ensured even if the height dimension H21 is reduced. Accordingly, it is possible to maintain the durability of the vane spring 19 while ensuring the urging force of the vane spring 19 against the vane 17.

  Furthermore, when the end winding part of the vane spring 19 is formed to have a larger diameter than the effective part, the tension of the end winding part located at the end opposite to the vane 17 is used to remove the vane spring 19. It may be fixed to the spring insertion hole 18. In the conventional configuration, since the end winding portion of the vane spring 19 and the spring insertion hole 18 are both round, the tension applied by the end winding portion is applied to the entire circumference of the inner peripheral surface of the spring insertion hole 18. . In contrast, in this example, since the entire vane spring 19 including the end winding portion is flat, the direction of the tension applied by the end winding portion can be limited, and the tension itself applied by the end winding portion can be easily adjusted. . Therefore, since the end winding portion can be made difficult to come off from the spring insertion hole 18, the vane spring 19 can be reliably fixed to the spring insertion hole 18.

  Since the spring insertion hole 18 is a deep hole, it has been difficult to process the spring insertion hole 18 into a flat hole shape as in the present embodiment with a conventional drilling machine or other processing equipment. However, in recent years, with the progress of processing equipment and processing technology, it is possible to process the spring insertion hole 18 as in the present embodiment.

Embodiment 2. FIG.
A compressor according to Embodiment 2 of the present invention will be described. FIG. 7 is a perspective view showing the configuration of the cylinder 11 of the compressor 1 according to the present embodiment. In addition, about the component which has the function and effect | action same as Embodiment 1, the same code | symbol is attached | subjected and the description is abbreviate | omitted. As shown in FIG. 7, the spring insertion hole 18 of the present embodiment has an oval shape (for example, two semicircular arcs) in at least a part of the spring insertion hole 18 in the axial direction (the whole in this example). It has a flat hole shape (rounded rectangular shape defined by two parallel straight lines). The height dimension H12 of the spring insertion hole 18 in the axial direction of the cylinder 11 is smaller than the width dimension W12 of the spring insertion hole 18 in the tangential direction of the cylinder 11 (H12 <W12).

  FIG. 8 is a diagram illustrating a configuration in which the vane spring 19 of the compressor 1 according to the present embodiment is viewed in the axial direction. As shown in FIG. 8, the vane spring 19 of the present embodiment has an oblong flat winding shape in at least a part of the vane spring 19 in the axial direction (in this example, the whole). . The vane spring 19 has a winding shape that can be inserted into the spring insertion hole 18 shown in FIG. The vane spring 19 is inserted such that the winding diameter (height dimension H22) in the axial direction of the cylinder 11 is smaller than the winding diameter (width dimension W22) in the tangential direction of the cylinder 11 (H22 <W22). It is inserted into the hole 18.

  According to the present embodiment, the same effect as in the first embodiment can be obtained. Further, when the height and the width are the same, the circumference of the ellipse is longer than the circumference of the ellipse. Therefore, in this embodiment, the winding length of the vane spring 19 is made longer than that in the first embodiment. be able to. Furthermore, since the outer periphery of the ellipse is configured by a straight line and an arc, the drilling process of the spring insertion hole 18 can be performed more easily than in the first embodiment.

Embodiment 3 FIG.
A compressor according to Embodiment 3 of the present invention will be described. FIG. 9 is a perspective view showing the configuration of the cylinder 11 of the compressor 1 according to the present embodiment. In addition, about the component which has the function and effect | action same as Embodiment 1, the same code | symbol is attached | subjected and the description is abbreviate | omitted. As shown in FIG. 9, the spring insertion hole 18 of the present embodiment has a rectangular flat hole shape in at least a part of the spring insertion hole 18 in the axial direction (in this example, the whole). Yes. The height dimension H13 of the spring insertion hole 18 in the axial direction of the cylinder 11 is smaller than the width dimension W13 of the spring insertion hole 18 in the tangential direction of the cylinder 11 (H13 <W13).

  FIG. 10 is a diagram illustrating a configuration in which the vane spring 19 of the compressor 1 according to the present embodiment is viewed in the axial direction. As shown in FIG. 10, the vane spring 19 of the present embodiment has a rectangular flat winding shape in at least a part of the vane spring 19 in the axial direction (the whole in the present example). The vane spring 19 has a winding shape that can be inserted into the spring insertion hole 18 shown in FIG. The vane spring 19 is inserted such that the winding diameter (height dimension H23) in the axial direction of the cylinder 11 is smaller than the winding diameter (width dimension W23) in the tangential direction of the cylinder 11 (H23 <W23). It is inserted into the hole 18.

  According to the present embodiment, the same effect as in the first embodiment can be obtained. Further, when the height and the width are the same, the circumference of the rectangle is longer than the circumference of the ellipse and the ellipse. Therefore, in the present embodiment, the winding length of the vane spring 19 is greater than those of the first and second embodiments. The length can be increased. Furthermore, since the outer periphery of the rectangle is configured by a straight line, in this embodiment, the drilling of the spring insertion hole 18 can be performed more easily than in the first embodiment.

Embodiment 4 FIG.
A compressor according to Embodiment 4 of the present invention will be described. FIG. 11 is a perspective view showing the configuration of the cylinder 11 of the compressor 1 according to the present embodiment. In addition, about the component which has the function and effect | action same as Embodiment 1, the same code | symbol is attached | subjected and the description is abbreviate | omitted. As shown in FIG. 11, the spring insertion hole 18 of the present embodiment has a polygonal shape (in this example, a hexagonal shape) in at least a part of the spring insertion hole 18 in the axial direction (in this example, the whole). It has a flat hole shape. Here, the polygon is a shape surrounded by three or more line segments. The height dimension H14 of the spring insertion hole 18 in the axial direction of the cylinder 11 is smaller than the width dimension W14 of the spring insertion hole 18 in the tangential direction of the cylinder 11 (H14 <W14).

  FIG. 12 is a diagram illustrating a configuration in which the vane spring 19 of the compressor 1 according to the present embodiment is viewed in the axial direction. As shown in FIG. 12, the vane spring 19 of the present embodiment is a flat polygonal shape (in this example, a hexagonal shape) in at least a part of the vane spring 19 in the axial direction (in this example, the whole). It has a winding shape. The vane spring 19 has a winding shape that can be inserted into the spring insertion hole 18 shown in FIG. The vane spring 19 is inserted such that the winding diameter (height dimension H24) in the axial direction of the cylinder 11 is smaller than the winding diameter (width dimension W24) in the tangential direction of the cylinder 11 (H24 <W24). It is inserted into the hole 18.

  According to the present embodiment, the same effect as in the first embodiment can be obtained. Further, since the outer periphery of the polygon is formed of a straight line, in this embodiment, the drilling process of the spring insertion hole 18 can be performed more easily than in the first embodiment.

Other embodiments.
The present invention is not limited to the above embodiment, and various modifications can be made.
For example, in the above-described embodiment, the vertical type compressor is taken as an example, but the present invention is also applicable to a horizontal type compressor.

  Moreover, although the compressor provided with one cylinder was mentioned as an example in the said embodiment, this invention is applicable also to the compressor provided with two or more cylinders.

  Moreover, in the said embodiment, although the spring insertion hole and vane spring which each have the shape whose height dimension is smaller than a width dimension in the whole axial direction were mentioned as an example, this invention is not limited to this. The spring insertion hole of the present invention may have a hole shape in which the height dimension is smaller than the width dimension only in a part in the axial direction and the height dimension and the width dimension are the same in other parts in the axial direction. Good. In addition, the vane spring of the present invention has a winding shape in which the height dimension is smaller than the width dimension only in one part in the axial direction, and the height dimension and the width dimension are equal in other parts in the axial direction, for example. Also good. In this case, each of the spring insertion hole and the vane spring may have a shape in which the height dimension is smaller than the width dimension at least in a portion corresponding to the bridge portion (a portion on the outer peripheral side of the vane groove in the radial direction of the cylinder). desirable. According to this, similarly to the above-described embodiment, it is possible to reduce the thickness of the cylinder while suppressing a reduction in the cross-sectional area of the bridge portion.

  In addition, the above embodiments and modifications can be implemented in combination with each other.

  DESCRIPTION OF SYMBOLS 1 Compressor, 10 Compression mechanism, 11 Cylinder, 11a Inner peripheral surface, 11b Rib part, 11c Outer peripheral surface, 12 Upper bearing, 13 Lower bearing, 14 Discharge muffler, 15 Rolling piston, 16 Vane groove, 17 vane, 18 Spring insertion Hole, 19 Vane spring, 20 Bridge part, 50 Electric mechanism, 51 Stator, 52 Rotor, 53 Drive shaft, 53a Eccentric part, 60 Airtight container, 61 Accumulator, 62 Suction pipe, 63 Suction port, 64 Discharge pipe

A compressor according to the present invention is in contact with a hollow cylinder housed in a container, a rolling piston that rotates eccentrically along the inner peripheral surface of the cylinder, and an outer peripheral surface of the rolling piston, A vane that divides the space into a suction chamber and a compression chamber; and a vane spring that urges the vane toward the rolling piston. The cylinder has a spring insertion hole into which the vane spring is inserted. and, the spring insertion hole, in some even without least of the spring insertion hole, the height in the axial direction of the cylinder has a small hole shape than the width dimension in the tangential direction of the cylinder, The vane spring is a coil spring, and the vane spring is at least partially in the axial direction of the vane spring. Te, in which the height in the axial direction of the cylinder has a smaller winding shape than the width dimension in the tangential direction of the cylinder.

Claims (3)

A hollow cylinder housed in a container;
A rolling piston that rotates eccentrically along the inner circumferential surface of the cylinder;
A vane that contacts an outer peripheral surface of the rolling piston and divides a space in the cylinder into a suction chamber and a compression chamber;
A vane spring that urges the vane toward the rolling piston,
The cylinder has a spring insertion hole into which the vane spring is inserted,
The spring insertion hole has a hole shape in which the height dimension in the axial direction of the cylinder is smaller than the width dimension in the tangential direction of the cylinder in at least a part of the spring insertion hole in the axial direction;
The vane spring is a coil spring,
The said vane spring is a compressor which has the winding shape in which the height dimension in the axial direction of the said cylinder is smaller than the width dimension in the tangential direction of the said cylinder in at least one part of the axial direction of the said vane spring.   The compressor according to claim 1, wherein a hole shape of the spring insertion hole is an elliptical shape, an oval shape, a rectangular shape, or a polygonal shape.   The compressor according to claim 1 or 2, wherein a winding shape of the vane spring is an elliptical shape, an oval shape, a rectangular shape, or a polygonal shape.

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