JP7619532B1 - Rotary Compressor - Google Patents

Abstract

A rotary compressor comprising: a vane (26) that is slidable from the piston (22) side to the radially outward side of the cylinder (23) and divides a compression chamber; a vane groove (32) that determines the sliding direction of the vane and has an opening on the inside of the cylinder; a spring (3) that presses the vane from the radially outward side of the cylinder toward the piston; and an elastic body (31) that is provided at least one of the radially outward end of the vane of the cylinder and an opposing position in the cylinder that faces the vane in the cylinder radial direction and has a smaller modulus of longitudinal elasticity than either the vane or the cylinder.

Description

The present disclosure relates to a rotary compressor for compressing a gas.

A rotary compressor comprises a cylinder into which a gas such as a refrigerant is supplied, a rolling piston that is rotated eccentrically within the cylinder with respect to the center of the cylinder, a vane that moves forward and backward radially from the inner wall surface of the cylinder and divides the space formed between the cylinder and the rolling piston into two, and a spring that presses the rear end of the vane so that the tip of the vane is always in contact with the rolling piston.

In a rotary compressor, it is disclosed that when a spring is compressed, it bulges and bends to the side, causing the spring to break or wear out. In order to prevent this, the spring is screwed into a spiral groove formed at the rear end of the vane to prevent it from shifting out of position (for example, Patent Document 1).

JP 2010-084575 A

In conventional rotary compressors, when the vane flies away from the piston and moves toward the cylinder at high speed, the vane collides with the outer radial side of the vane groove along which the vane moves. At this time, the spring wire may get into the radial inner or outer side of the adjacent winding, or the spring may vibrate abnormally. In addition, in a configuration in which the spring on the piston side is screwed into the vane, the vane stops moving when the vane collides with the vane, but the spring continues to move due to inertia, so that impact stress is concentrated at the fixed part of the vane and the spring. This may cause the spring to be fatigued early.
The present disclosure has been made to solve the above-mentioned problems, and provides a rotary compressor that prevents fatigue damage to the spring even if liquid gets into the suction chamber in the cylinder.

A rotary compressor according to one claim of the present disclosure comprises a cylinder forming a compression chamber therein, a piston which rotates eccentrically inside the cylinder, a vane which is slidably arranged from the piston side radially outward of the cylinder and which divides the compression chamber, a vane groove which determines the sliding direction of the vane and has an opening inside the cylinder, a spring which presses the vane from the radially outward side of the cylinder towards the piston side, and an elastic body which is arranged at least one of the radially outer end of the vane of the cylinder and an opposing position within the cylinder radially opposed to the vane, and which has a smaller longitudinal elastic modulus than either the vane or the cylinder, the elastic body being made of a rubber or gel material, the elastic body having projections and recesses in a direction perpendicular to the traveling direction of the vane, and the recesses of the projections and recesses of the elastic body engaging with projections provided on the vane or the cylinder.

According to the present disclosure, even if liquid gets into the suction chamber inside the cylinder, causing the vane to fly off and come into contact with the radially outer side of the vane groove in the cylinder, the impact speed of the vane is mitigated by the presence of an elastic body between the vane and the cylinder with which it comes into contact, thereby suppressing repeated impact loads on the vane side fixing part and preventing fatigue failure of the spring.

1 is a cross-sectional view of a cross section parallel to a rotary shaft of a rotary compressor according to a first embodiment of the present disclosure. 1 is a cross-sectional view taken along a plane perpendicular to a rotation axis of a compression mechanism of a rotary compressor according to a first embodiment of the present disclosure. 1 is a cross-sectional view taken along a plane perpendicular to a rotation axis of a vane sliding structure according to a first embodiment of the present disclosure. 1 is a schematic diagram of a vane sliding structure showing a first embodiment of the present disclosure; 1 is a schematic diagram showing an installation state of a cylinder outer elastic body according to the first embodiment of the present disclosure; FIG. 1 is a cross-sectional view taken along a plane perpendicular to a rotation axis of a vane sliding structure using an O-ring as an elastic body according to a first embodiment of the present disclosure. 1 is a cross-sectional view taken along a plane perpendicular to the rotation axis of a vane sliding structure in an example in which a vane end elastic body is provided inside a spring winding, according to a first embodiment of the present disclosure. FIG. 1 is a cross-sectional view taken along a plane perpendicular to the rotation axis of a vane sliding structure in an example in which a cylinder outer elastic body is provided on a protrusion provided on a lid that closes an opening in a cylinder outer wall, according to a first embodiment of the present disclosure. FIG. FIG. 11 is a cross-sectional view of a vane sliding structure showing a second embodiment of the present disclosure. FIG. 11 is a cross-sectional view of a vane sliding structure showing embodiment 3 of the present disclosure. FIG. 11 is a cross-sectional view of a vane sliding structure showing embodiment 4 of the present disclosure. FIG. 13 is a cross-sectional view of a vane sliding structure showing embodiment 5 of the present disclosure. FIG. 13 is a cross-sectional view of a vane sliding structure showing embodiment 6 of the present disclosure. FIG. 13 is a cross-sectional view of a vane sliding structure showing an embodiment 7 of the present disclosure.

Embodiment 1.
The rotary compressor disclosed herein is a rotary compressor having a cylinder forming a compression chamber inside, and a piston that rotates eccentrically inside the cylinder, and is equipped with a vane that is slidable from the piston side to the radially outside of the cylinder and divides the compression chamber, a vane groove that defines the sliding direction of the vane and has an opening inside the cylinder, a spring that presses the vane from the radially outside of the cylinder to the piston side, and an elastic body that is provided at least one of the radially outer end of the vane of the cylinder and an opposing position in the cylinder radially opposite the vane, and has a smaller longitudinal elastic modulus than both the vane and the cylinder.

Figure 1 shows a cross-sectional view of an example of a rotary compressor in this embodiment. This cross-sectional view is a cross-sectional view of the rotary compressor in a plane parallel to the rotation axis of the piston. In Figure 1, the rotary compressor 1 has a prime mover section 10 and a compression mechanism section 20 having a part rotated by the prime mover section 10. Here, the prime mover section 10 shows an example of an electric motor that converts electrical energy into rotational energy. Note that the prime mover section 10 may be configured to be outside the rotary compressor 1 and rotate the rotating part of the compression mechanism section 20 from outside.

The compression mechanism 20 is connected to the prime mover 10 so that rotational energy can be transmitted. The compression mechanism 20 includes a cylinder 23 that forms a compression chamber, a piston 22 that rotates eccentrically within the cylinder 23, a vane 26 that is slidable from the piston 22 side to the radially outer side (outer wall side) of the cylinder 23 at an opening that opens to the radially inner side (inner wall side) of the cylinder 23 and divides the compression chamber, and a spring 30 that is provided at the opening and presses the vane 26 from the outer wall side of the cylinder 23 to the piston side (cylinder 23 inner wall side) (from the radially outer side to the inner side of the cylinder 23). Here, the central axis of rotation of the eccentrically rotating piston is called the rotation axis.

The compression mechanism 20 also includes an elastic body 31 provided on at least one of the end of the vane 26 on the outer wall side of the cylinder 23 and the opposing portion of the inner wall surface of the cylinder 23 that faces the vane 26. The elastic body 31 has a smaller modulus of longitudinal elasticity than both the vane 26 and the cylinder 23.

In the case of an electric motor, the prime mover 10 generates an electromagnetic force to rotate the crankshaft of the compression mechanism 20, compressing the gas (refrigerant in the case of an air conditioner) in the compression mechanism 20. FIG. 1 shows a cross-sectional view of a rotary compressor 1 having two compression chambers 52 for compressing the gas. However, at least one compression chamber is sufficient. The rotary compressor 1 also has a sealed container 40 that covers the prime mover 10 and the compression mechanism 20. A discharge pipe 41 that discharges the compressed gas into a pipe (not shown) outside the sealed container 40 is arranged on the side of the sealed container 40 opposite the side where the compression mechanism 20 is arranged, toward the prime mover 10.

In the case of an electric motor, the prime mover 10 includes a stator 11 and a rotor 12. The stator 11 is fixed to the inner circumferential surface of the sealed container 40. The rotor 12 is disposed on the inner circumferential surface of the stator 11 with a gap between it and the stator 11. The rotation axis of the rotor 12 is a common axis with the rotation axis of the piston 22. In the example of FIG. 1, the rotation axis of the rotor 12 is an axis of the crankshaft of the compression mechanism 20 extending toward the prime mover 10. That is, the rotor 12 forms a hollow cylindrical shape, and the crankshaft 21 is fixed to the inner periphery of this hollow cylindrical shape. The crankshaft 21 is coupled to the piston 22 so that the piston 22 rotates eccentrically. With the above structure, the crankshaft 21 rotates with the rotation of the rotor 12, and the piston 22 rotates eccentrically within the cylinder 23.

In the example of Fig. 1, the compression mechanism 20 has two compression chambers in the direction of the rotation axis. A cylinder 23 is provided for each compression chamber, and the cylinders 23 are separated in the direction of the rotation axis by a plate 27. The cylinders 23 are arranged in two rows in the longitudinal direction of the sealed container 40, i.e., in the direction of the rotation axis.

Of the two cylinders 23, the first cylinder 23a on the motor unit 10 side is provided on the end surface on the motor unit 10 side with a first bearing 24a that rotatably holds the crankshaft 21. In addition, the second cylinder 23b is provided on the opposite side of the rotation axis direction from the first cylinder 23a (motor unit 10 side) of the two cylinders 23 via a plate 27. The second bearing 24b that holds the crankshaft 21 is provided on the end surface of the second cylinder 23b opposite the plate 27. The first bearing 24a and the second bearing 24b hold the crankshaft 21 as a pair. The first bearing 24a and the second bearing 24b have a hollow cylindrical through hole with a diameter larger than the shaft diameter of the crankshaft 21, and are arranged to cover the crankshaft 21 and rotatably hold the crankshaft 21. Furthermore, the first bearing 24a on the motor unit 10 side has a discharge port 29 for discharging the refrigerant compressed in the cylinder 23. The refrigerant discharged from the discharge port 29 passes through a piping (not shown) and is output from the sealed container 40 through a discharge pipe 41 .

2 is a cross-sectional view of the compression mechanism 20 of the rotary compressor according to the first embodiment, taken along a plane perpendicular to the rotation axis. In this figure, the cylinder 23, the piston 22, the vane 26, and the vane 26 of the spring and parts that may come into contact with the vane 26 are shown as the main parts of the compression mechanism 20. Although the figure is shown as a cross-sectional view, for the sake of convenience, the spring, the vane 26, and the elastic body 31 are shown as having parts that protrude forward from the cut surface of the other parts. In the figure, the crankshaft 21 is shown with a crankshaft eccentric part 21a that is eccentric from the rotation axis, and the piston 22 is provided on the outer periphery of the crankshaft eccentric part 21a. The outer periphery of the piston 22 is provided with a cylinder 23 having a cylindrical through hole that follows the rotation trajectory of the outer periphery of the piston 22 when the crankshaft 21 rotates. In a through hole provided inside the cylinder 23 in the direction of the rotational axis, the crankshaft eccentric portion 21a and the piston 22 rotate eccentrically, and when the piston 22 rotates eccentrically inside the through hole, the space between the inside of the through hole of the cylinder 23 and the piston 22 changes.

The cylindrical inner wall surface of the cylinder 23 is provided with a vane groove 32, which is a groove along which the vane 26 slides in the radial direction of the cylinder 23 (perpendicular to the rotation axis). At the radial outer end of the vane groove 32, there is an inner wall that is almost parallel to the outer wall surface of the cylinder 23, i.e., the radial end of the cylinder 23. The radial depth of the vane groove 32 is such that the radial end of the vane 26 does not come into sufficient contact with the piston 22 even if the vane 26 moves in this radial direction while maintaining contact with the piston 22. That is, the vane groove 32 has an inner wall surface (the inner wall surface on the radial outer side of the cylinder 23) on the radial outer side of the cylinder 23. This inner wall is also called the radial outer end of the vane groove 32, or the radial outer side of the cylinder 23. If the spring 30 were not present, when the vane 26 slid along the vane groove 32 and moved radially outward, it would come into contact with the radially outer end of the vane groove 32 or the radially outer side of the cylinder 23 .

Here, the radially outer side of the cylinder 23 is the part where a cross section perpendicular to the movement direction of the vane 26 of the vane groove 32 provided in the cylinder 23 is projected onto the inner wall surface of the cylinder 23 in the direction of the same movement. As a result, assuming that there is no spring 30, the radially outer side of the cylinder 23 is the part that comes into contact with the inner wall surface of the cylinder 23 at the back of the vane groove 32 when the vane 26 slides in the vane groove 32 and moves radially outward of the cylinder 23. If there is an end face on the innermost side of the vane groove 32 in the vane movement direction, this contact part can be said to be the radially outer end of the vane groove 32.

A cylindrical hole (recess) or through hole may be provided in the radially outer portion of the vane groove 32 of the cylinder 23 toward the radially outer side of the cylinder 23. Also, the cylinder 23 may be arranged inside the sealed container 40, and the through hole at the radially outer end of the groove of the cylinder 23 may be blocked by a lid portion, which is a means for blocking a hole, such as the inner wall of the sealed container 40 or a bolt. The cylindrical hole (recess) or through hole in the radially outer portion of the vane groove 32 of the cylinder 23 may be regarded as a spring storage hole described later. Also, a vane groove axial hole that penetrates in the rotation axis direction may be provided in the middle of the groove portion in the radial direction of the cylinder 23.

The space between the piston 22 and the inside of the through hole provided in the rotation axis direction of the cylinder 23 is separated into a suction chamber 51 and a compression chamber 52 by the vane 26. That is, the vane 26 is a partition plate that separates the space between the inner wall of the cylinder 23 and the piston 22 into the suction chamber 51 and the compression chamber 52. The vane 26 is arranged in a groove so as to be movable in the radial direction of the cylinder 23, and the radially inner side of the cylinder contacts the piston 22. A spring 30 is provided on the radially outer end face of the vane 26 of the cylinder 23 to bias the vane 26 against the inner wall surface of the cylinder 23 or the sealed container 40 so that the vane 26 is always in contact with the piston 22. That is, the vane 26 is pressed against the piston 22 located radially inward by the spring force of the spring 30 provided radially outward.

In addition, one end of the spring 30 in the extension direction contacts the vane 26. The other end of the spring 30 in the extension direction may be arranged so that the end of the spring 30 on the radially outer side of the cylinder 23 enters a hole (recess) or through hole provided at the end of the vane groove 32 on the radially outer side of the cylinder 23. Furthermore, if the width of the spring 30 is greater than the thickness of the vane groove 32, a spring storage hole 33 is provided that is larger than the thickness of the vane groove 32 and stores the spring 30 so that the spring 30 can be extended and contracted. If this spring storage hole 33 is configured to communicate with a hole or through hole provided at the end of the vane groove 32 on the radially outer side of the cylinder 23, there is no step or other catch, and the spring 30 can be smoothly extended and contracted. The cross section of the spring storage hole 33 perpendicular to the extension direction of the spring 30 may be cylindrical in accordance with the shape of the spring 30, if the external shape of the spring 30 is approximately cylindrical. Incidentally, even if the spring storage hole 33 is provided in the vane groove 32, the vane groove 32 that regulates the movement of the vane 26 still exists, and the radially outer end of the vane groove 32 or the radially outer side of the cylinder 23 exists.

In addition, the cylinder 23 is provided with an intake port 28 for drawing in the refrigerant, which penetrates the cylinder 23 in the radial direction. The outer peripheral surface of the cylinder 23 in the radial direction may be fixed to the inner peripheral surface of the sealed container 40.

Next, we will explain the surrounding structure where the vanes 26 may come into contact with each other, i.e., the vane groove 32 in the cylinder 23 and the structure that causes the vane 26 to slide using the spring 30 (hereinafter also referred to as the "vane sliding structure").

Figure 3 is a cross-sectional view of the vane sliding structure of embodiment 1, cut in the thickness direction of the cylinder 23 (cut along a plane parallel to the rotation axis and the radial direction). In the figure, a piston 22 is disposed on the outer periphery of the eccentric portion 21a of the crankshaft 21, and a vane 26 is pressed against and held in place by the spring force of a spring 30 against the outer periphery of the piston 22. The vane 26 moves in the radial direction of the cylinder 23 in response to the rotation of the crankshaft 21 and the piston 22.

The spring 30 is disposed inside the spring storage hole 33 of the vane groove 32 in the radial direction of the cylinder 23. In the example of Fig. 3, the spring 30 has a tapered shape in which the coil outer diameter becomes thinner as it approaches the radial inside of the cylinder 23. The end of the spring 30 on the side not in contact with the vane 26 (the radial outside of the cylinder 23) may be fixed by a crimping force caused by pressing between the cylinder radial end of the spring storage hole 33 and the outer circumferential surface of the spring 30 coil, or it may not be fixed.

<Explanation of vane flying>
In the rotary compressor 1, when the internal pressure of the compression chamber 52 suddenly rises, pressure (load) is applied to the vane 26, which is a partition plate separating the suction chamber 51 and the compression chamber 52 inside the cylinder 23. When the inertial force generated by the pressure of the vane 26 becomes greater than the spring force of the spring 30, the piston 22 and the vane 26 separate, and the vane 26 moves radially outward of the cylinder 23 at high speed. This phenomenon is called vane jump.

In particular, in rotary compressors for air conditioners, liquid refrigerant may be mixed into the suction chamber 51 inside the cylinder 23 during operation. When the piston 22 rotates with liquid refrigerant mixed into the suction chamber 51, the internal pressure rises suddenly. When the internal pressure rises suddenly, pressure is applied to the vane 26, which is a partition plate separating the suction chamber 51 and the compression chamber 52 inside the cylinder 23. Before the refrigerant is discharged from the discharge port 29, the pressure due to the liquid refrigerant rises suddenly, and the inertial force of the vane 26 becomes greater than the spring force of the spring, which may cause the phenomenon known as vane jumping. Note that, although the above example shows the mixed liquid being a refrigerant, it may also be a liquid other than a refrigerant.

Due to the phenomenon called vane jump, the vane 26, which moves radially outward at high speed, collides with the radially outer wall of the cylinder 23 or the radially outer end of the vane groove 32. If the speed at which the vane 26 collides with the wall increases, the vane 26 and the spring 30, which are normally in contact due to the spring force, may separate when the vane 26 collides with the radially outer wall of the cylinder 23 or the radially outer end of the vane groove 32, and the spring 30 may deform until the adjacent windings (spirals) of its own wire are in full contact with each other.

When a load is applied to the vane 26 that causes the spring 30 to completely stick, the wire of the spring 30 may penetrate into the radial inside (or outside) of the adjacent winding (spirals), causing excessive stress. Also, if the external shape of the spring 30 has a parallel section parallel to the direction in which the spring 30 expands and contracts, and a tapered section that forms an angle with the direction in which the spring 30 expands and contracts, the parallel section may penetrate into the tapered section, causing excessive stress.

If the wire of the spring 30 itself is repeatedly deformed to overcome the adjacent helix or to enter the inside of the helix, the spring 30 may be damaged by fatigue. If the spring 30 is not fixed to the vane 26, the vane 26 side of the spring 30 continues to move when the vane 26 collides with the cylinder 23 (or the vane groove 32). For this reason, the spring 30 may be damaged by fatigue due to intense vibration (abnormal vibration, surging) in which the winding (spiral) of the spring 30 repeatedly comes into contact with and separates from the adjacent winding. Surging is a phenomenon that occurs when an external force with a frequency component close to the natural frequency of the spring is applied.

In addition, if the spring 30 is fixed to the vane 26, the movement of the vane 26 stops when the vane 26 collides with the cylinder 23, but the inertial force generated in the spring 30 causes stress to concentrate at the fixed portion of the spring 30 with the vane 26. Repeated impact loads caused by this stress concentration may cause early fatigue failure of the spring 30.

Next, a configuration for preventing excessive stress, violent vibration, and fatigue failure occurring in the spring 30 as described above will be described with reference to Figures 3, 4, and 5. Figure 3 is a cross-sectional view of the sliding structure of the vane 26 taken along a plane perpendicular to the rotation axis, Figure 4 is an oblique projection of the sliding structure of the vane 26, and Figure 5 is an oblique projection showing the mounting state of the cylinder-side outer elastic body 31b to the cylinder 23.

In the present disclosure, the compression mechanism 20 includes an elastic body 31 (31a, 32b) provided on at least one or both of the end of the vane 26 on the outer wall side of the cylinder 23 and the opposing portion facing the vane 26 on the inner wall surface of the cylinder 23. The elastic body 31 (31a, 32b) has a smaller modulus of longitudinal elasticity than both the vane 26 and the cylinder 23. This will be described in detail below.

The vane 26 is provided with an elastic body 31 (31a) at the outermost end on the radial outside of the cylinder 23. The portion where the elastic body 31 is provided is the portion where the radially outer end of the vane 26 comes into contact with the radially outer end of the cylinder 23 of the vane groove 32 (cylinder 23) when the spring 30 is compressed (or assuming that the spring 30 is not present) and the vane 26 moves radially outward from the cylinder 23.

In addition, an elastic body 31 (31b) may be provided at the radially outer end of the vane groove 32 of the cylinder 23, at the portion that comes into contact with the radially outer wall surface of the cylinder 23 (vane groove 32) when the vane 26 moves radially outward. The portion that comes into contact with the radially outer wall surface of the cylinder 23 (vane groove 32) is the portion surrounded by a dotted line in Figure 5. This portion of the cylinder outer elastic body 31b comes into contact with the portion of the vane end elastic body 31a surrounded by the dotted line in Figure 4.

Furthermore, the elastic body 31 may be attached to either or both of the radially outer end of the vane 26 and the radially outer end of the cylinder 23 of the vane groove 32. Here, the Young's modulus of elasticity of the elastic body 31 (31a, 31b) is smaller than the Young's modulus of elasticity of the vane 26 and the cylinder 23.

The elastic body 31 (31a, 31b) is preferably made of a rubber or gel material. The elastic body 31 may have a modulus of longitudinal elasticity that is approximately 1×10 ⁻⁵ to 1×10 ⁻² that of the vane 26 and the cylinder 23.

Figure 3 shows a case in which the elastic body 31 is arranged on both the vane 26 surface where the vane 26 comes into contact with the cylinder 23 when vane flying occurs on the side opposite to the surface in contact with the piston 22, and on the surface of the radially outer end of the cylinder 23 (the radially outer end of the vane groove 32) that comes into contact with the vane 26, but it is sufficient if the elastic body 31 is arranged on at least one of them.

The elastic body 31 may be attached by means of an adhesive. Alternatively, the elastic body 31 may be attached by forming a recess in the radially outer end of the vane 26 or cylinder 23 (the radially outer end of the vane groove 32) and elastically deforming the elastic body 31 itself to press it in.

In the above figures, the shape of the elastic body 31 (31a, 31b) is described as a rectangular parallelepiped shape, but this is not limited to this. For example, an example is shown in which the elastic body 31 (31a, 31b) is annular or a part thereof. For example, the elastic body 31 (31a, 31b) may be a so-called O-ring rubber material cut to the same thickness as the vane 26, i.e., the plate thickness (thickness in the rotation axis direction), and attached to the end face of the vane 26 opposite the side that contacts the piston 22, i.e., the radial outer side of the cylinder 23. By configuring in this way, when the vane jumps, the cut part of the rubber material of the O-ring contacts the radial outer end of the cylinder 23 of the vane groove 32. The above configuration can reduce material by using the cut part of the rubber material of the O-ring for the elastic body 31 (31a).

Figure 6 shows an example in which the elastic body 31 is made of rubber O-ring. In the figure, an O-ring with an annular outer shape equal to or smaller than the plate thickness of the vane 26 is attached as the elastic body 31a to the end face of the vane 26, which is the radially outer side of the cylinder 23.

In addition, in the figure, an O-ring as elastic body 31b is attached to the radially outer side of cylinder 23. In this case, the O-ring is provided at a position that surrounds the spring storage hole on the radially outer side of cylinder 23 and contacts the end face of vane 26 on the radially outer side of cylinder 23. In this example, the O-ring, which is elastic body 31b, is not only located on the radially outer side of vane groove 32 (the part where vane 26 is projected radially outward), but also around this area. However, if a circular groove is provided around the cross section of the spring storage hole and pressed in, it has the effect of making assembly easier.

The cross-sectional shape of the elastic body 31 (31a, 31b) may be circular as shown in Fig. 6. In Fig. 6, the elastic body 31 (31a, 31b) is provided on both the radially outer end face of the vane 26 and the radially outer side of the cylinder 23, but the elastic body 31 may be provided on either the radially outer end face of the vane 26 or the radially outer side of the cylinder 23, or on both.

In the above, the elastic body 31 (31a, 31b) is disposed outside the outer diameter of the spring 30, but it may be disposed inside the wire windings of the spring 30. For example, as shown in Fig. 7, the vane end elastic body 31a may have a hole that engages with an arrowhead-shaped protrusion provided on the radially outer end of the cylinder 23 of the vane 26, and may be shaped to enter inside the windings of the spring 30 while engaged with the arrowhead-shaped protrusion.

When the vane end elastic body 31a is provided inside the winding of the spring 30, as shown in FIG. 7, the cylinder outer elastic body 31b is configured to be shaped to enter inside the winding of the wire at the radially outer end of the cylinder 23 of the spring 30 and to be fixed to the cylinder 23. The fixing method is to first provide a cylinder outer wall opening that opens to the radially outer side of the cylinder 23 at the spring storage hole 33 in the cylinder 23. Next, the cylinder outer elastic body 31b can be pressed from the outer periphery side to the inner periphery side of the radially outer part of the cylinder 23 to be fixed. At this time, the outermost part of the radially outer part of the cylinder 23 at the spring storage hole 33 may be chamfered, and the cylinder radially outer end of the cylinder outer elastic body 31b may be bulged to engage with the chamfer. Furthermore, the bulged part of the cylinder radially outer end of the cylinder outer elastic body 31b is firmly fixed by engaging the sealed container 40 with the cylinder 23.

Alternatively, the fixing method may be such that, instead of providing the vane end elastic body 31a, the cylinder outer elastic body 31b that fits inside the wire windings of the spring 30 is inserted into the cylinder outer wall opening from the radially outside of the cylinder 23 in the spring storage hole 33 and fixed. In this case, the cylinder outer elastic body 31b comes into direct contact with the vane 26 when vane flying occurs. When assembling this configuration, there is no need to attach the vane end elastic body 31a to the vane 26 side, and it is simple to simply insert the cylinder outer elastic body 31b into the spring storage hole 33 from the outside of the cylinder 23.

8, a cylinder outer wall opening that opens radially outward of the cylinder 23 may be provided, a lid 42 may be attached that engages with the opening to close the opening, and the cylinder outer elastic body 31b may be fixed to a protrusion provided on the lid 42. By configuring in this way, there is less deformation such as buckling than if the entire structure were made of elastic body 31, and the impact speed can be more effectively suppressed.

By arranging it inside the wire windings of the spring 30 as described above, the volume of the elastic body 31 (31a, 31b) itself can be made larger, which is expected to absorb more impact and reduce the collision speed.

Next, the radial dimension of the elastic body 31 in the cylinder 23 will be described. First, the position of the vane 26 in contact with the piston 22 when the gap between the outer periphery of the piston 22 and the inner periphery of the cylinder 23 is at a minimum in the arrangement position of the vane 26 (or vane groove 32) in the cylinder 23 is set as the reference position. At least in the reference position of the vane 26, the dimension of the elastic body 31 (31a, 31b) in the moving direction of the vane 26 is the dimension of the vane 26 that does not come into contact with any parts in the moving direction of the vane 26 and does not come into contact with any parts with a design clearance.

According to the configuration of this embodiment, even if a phenomenon called vane flying occurs and the vane 26 is thrown radially outward from the cylinder 23 and comes into contact with the cylinder 23, the vane 26 collides with the cylinder 23 via the elastic body 31 (31a, 31b), so the collision speed (acceleration (deceleration) on the deceleration side at the time of collision) can be mitigated. Since the collision speed between the vane 26 and the radial outer part of the cylinder 23 (the radial outer end of the vane groove 32) can be reduced by the acceleration (deceleration) on the deceleration side at the time of collision, excessive stress generated in the spring is suppressed.

In addition, since the collision speed between the vane 26 and the radially outer portion of the cylinder 23 (the radially outer end of the vane groove 32) can be reduced by the acceleration (deceleration) on the deceleration side during the collision, fatigue failure due to repeated impact loads at the fixed portion of the spring 30 can be prevented. In addition, fatigue failure due to repeated deformation of the wire of the spring 30 itself overcoming adjacent spirals or the wire penetrating inside the spiral portion can be prevented.

Furthermore, since the collision speed (acceleration (deceleration) on the deceleration side at the time of collision) between the vane 26 and the radially outer portion of the cylinder 23 (the radially outer end portion of the vane groove 32) can be reduced, it is expected that fatigue failure of the spring 30 can be prevented by suppressing violent vibrations (abnormal vibrations, surging) in which the winding (spiral) of the spring 30 itself repeatedly comes into contact with and separates from the adjacent winding.

In addition, according to the configuration of this embodiment, instead of a large-scale structure, an elastic body 31 is provided partially in a part of the vane sliding structure, so it is believed that it is possible to prevent breakage of the spring 30 caused by the vane flying without increasing the size of the rotary compressor 1 or increasing the sliding resistance during normal operation.

Furthermore, if the mass of the elastic body 31a provided at the radial end of the vane 26 is reduced, or if the density of the elastic body 31a is lower than that of the vane 26, the mass that moves together with the vane 26 is reduced, and the inertial force of the thing that moves together with the vane 26 is reduced. This reduces the inertial force, which is one of the causes of the phenomenon known as vane jumping, making the phenomenon known as vane jumping less likely to occur. Or, even if vane jumping does occur, the above problems caused by it will not occur, or it is thought that the occurrence of the problems will be further suppressed.

In the above, an example was also shown in which the elastic body 31, which has a smaller modulus of longitudinal elasticity than the vane 26 and the cylinder 23, is provided on both the radially outer end face of the cylinder 23 of the vane 26 and the radially outer end of the cylinder 23 (vane groove 32). In the example in which the elastic body 31 (31a, 32b) is provided on both the radially outer end face of the vane 26 and the radially outer end of the vane groove 32, when the vane 26 and the cylinder 23 come into contact, the thickness of the elastic body 31 in the moving direction of the vane 26 becomes thicker than when the elastic body 31 is attached to only one side. By attaching the elastic body 31 to both sides, the thickness (particularly the radial thickness) of the elastic body 31a, 32b can be made thicker, so the amount of impact energy absorption can be increased. By configuring in this way, the amount of mitigation of the impact speed (acceleration (deceleration) on the deceleration side at the time of impact) can be increased, and the above problems such as fatigue failure due to repeated impact loads at the fixed part of the spring 30 can be prevented.

Embodiment 2.
In the first embodiment, the radially outer end of the spring 30 of the cylinder 23 may or may not be fixed in the radially outer hole of the cylinder 23 by crimping force. In the present embodiment, an example will be described in which the side of the spring 30 that contacts the vane 26 is fixed. Unless otherwise specified, the same reference numerals and terms are used in the same manner as in the above embodiment. Therefore, the structure of this embodiment also has the piston 22, the cylinder 23, the vane 26, the spring 30, the elastic body 31 (31a or 31b), the vane groove 32, and the spring storage hole 33.

Figure 9 shows a cross-sectional view of the vane sliding structure of embodiment 2. In the example shown, the spring 30 has a portion at the end that comes into contact with the vane 26 where adjacent windings of the wire of the spring 30 are in contact with each other. In other words, when no load is applied to the spring 30, the end of the spring 30 that comes into contact with the vane 26 has a portion where there is no pitch between the windings. This portion where there is no pitch between the windings of the end of the spring 30 that comes into contact with the vane 26 is fixed to the radially outer end of the cylinder 23 of the vane 26.

Specifically, the vane 26 and the non-pitch portion of the end of the spring 30 that comes into contact with the vane 26 are fixed by crimping force by pressing the outer coil surface of the non-pitch portion of the spring 30 between the protrusions at both ends of the width direction of the radially outer peripheral end of the cylinder 23 of the vane 26. An elastic body 31a may be provided radially outward of the protrusion at the radially outer peripheral end of the cylinder 23 of the vane 26.

On the other hand, the radially outer end of the cylinder 23 of the spring 30 may be configured to be pressed against the radially outer end of the cylinder 23 of the spring storage hole 33 (when the inner wall of the cylinder 23 is located at the innermost part of the spring storage hole 33) or against the inner wall surface of the sealed container 40 radially outside the cylinder 23 of the spring storage hole 33 by the spring force of the spring 30 (not fixed in the radial direction). Alternatively, the radially outer end of the cylinder 23 of the spring 30 may be fixed to the radially outer end of the cylinder 23 of the spring storage hole 33.

The spring 30 is fixed by a crimping force caused by pressing in the above description, but this is not limited to this. The fixing method may also be by brazing, welding, solvent, resin or adhesive.

In addition, the elastic body 31 is provided on at least one or both of the end portion of the vane 26 on the outer wall side of the cylinder 23 (vane end elastic body 31a) and the opposing portion facing the vane 26 on the inner wall surface of the cylinder 23 (cylinder outer elastic body 31b).

According to this embodiment, even if vane flying occurs, causing the vane 26 to fly and come into contact with the cylinder 23, the vane 26 will collide with the cylinder 23 via the elastic body 31. By making contact via this elastic body 31, the collision speed between the vane 26 and the cylinder 23 can be reduced, and fatigue failure due to repeated impact loads at the fixed portion of the spring 30 can be prevented.

In addition, even if the vane flies off, the collision speed between the vane 26 and the cylinder 23 can be mitigated, preventing the wire of the spring 30 from repeatedly deforming to overcome adjacent spirals or to penetrate inside the spiral, which would cause fatigue failure. This prevents the spring 30 from breaking due to the vane flying off, without causing a large structural change that would increase the size of the compressor or increase the sliding resistance during normal operation.

In addition, because the vane 26 and the spring 30 are fixed together, the vane 26 and the spring 30 do not separate, and wear caused by adhesion between the wires due to separation can be prevented. Also, in the case where the radially outer end of the spring 30 of the cylinder 23 is not fixed to the radially outer end of the cylinder 23 of the spring storage hole 33, the process of fixing the spring 30 to the cylinder 23 during manufacturing can be eliminated.

Embodiment 3.
In the first embodiment, the radially outer end of the spring 30 of the cylinder 23 may or may not be fixed in the radially outer hole of the cylinder 23 by a crimping force. In the second embodiment, an example in which the side of the spring 30 that contacts the vane 26 is fixed is described. In the present embodiment, an example in which the side of the spring 30 that contacts the vane 26 is fixed and the radially outer side of the spring 30 of the cylinder 23 is fixed to the cylinder 23 is shown. Unless otherwise specified, the same reference numerals and terms are used to refer to the same as in the above embodiment. Therefore, the structure of this embodiment also has the piston 22, the cylinder 23, the vane 26, the spring 30, the elastic body 31 (31a or 31b), the vane groove 32, and the spring storage hole 33.

Figure 10 shows a cross-sectional view of the vane sliding structure of this embodiment. In the example shown, the spring 30 has a portion at the end on the side that contacts the vane 26 where adjacent windings of the wire of the spring 30 are in contact with each other. In other words, when no load is applied to the spring 30, the end of the spring 30 that contacts the vane 26 has a portion where there is no pitch between the windings. This portion of the end of the spring 30 that contacts the vane 26 where there is no pitch between the windings is fixed to the radially outer end of the cylinder 23 of the vane 26. This is the same as in embodiment 2.

On the other hand, in the figure, the radially outer end of the spring 30 on the cylinder 23 is fixed to the radially outer end of the spring storage hole 33 on the cylinder 23. Specifically, the end of the spring 30 on the side not in contact with the vane 26 (the radially outer side of the cylinder 23) has a portion where adjacent windings of the wire of the spring 30 are in contact with each other, i.e., a portion where there is no pitch between the windings. This portion where there is no pitch between the windings at the radially outer end of the spring 30 on the cylinder 23 is fixed by the crimping force caused by the press fit between the radial end of the spring storage hole 33 and the outer circumferential surface of the spring 30 coil.

Also, as shown in the figure, the outer diameter of the center part of the spring 30 in the extension/contraction direction in the direction perpendicular to the extension/contraction direction may be smaller than both ends in the extension/contraction direction, and a drum-shaped taper may be provided.

As described above, in this embodiment, the spring 30 has both ends, the end that contacts the vane 26 and the end that is radially outer of the cylinder 23, fixed to the vane 26 and the spring storage hole 33 or the radially outer end of the cylinder 23, respectively.

The spring 30 is fixed by a crimping force caused by pressing in the above description, but the fixing method is not limited to this. The fixing method may also be by using brazing material, welding, a solvent, resin, or an adhesive.

In addition, the elastic body 31 is provided at least one or both of the radially outer end of the vane 26 on the cylinder 23 (vane end elastic body 31a) and an opposing position within the cylinder 23 that faces the vane 26 in the cylinder radial direction (cylinder outer elastic body 31b).

According to the configuration of this embodiment, even if vane flying occurs, causing the vane 26 to fly and come into contact with the cylinder 23, the vane 26 will collide with the cylinder 23 via the elastic body 31. By making contact via this elastic body 31, the collision speed between the vane 26 and the cylinder 23 can be reduced, and fatigue damage due to repeated impact loads at the spring 30 fixing portion can be prevented.

Even if the vane flies off, the collision speed between the vane 26 and the cylinder 23 can be mitigated, preventing the wire of the spring 30 from repeatedly deforming to overcome the adjacent spiral or to penetrate inside the spiral, which would cause fatigue failure. This prevents the spring 30 from breaking due to the vane flying off, without causing the compressor to become larger due to major structural changes or an increase in sliding resistance during normal operation.

In addition, even if the impact from the vane flying remains through the elastic body 31, both ends of the spring 30 in the extension direction are fixed, so even if a load is applied that separates the ends of the spring 30, they remain fixed in place, preventing wear caused by the wires of the spring 30 coming into close contact with each other due to the separation.

Embodiment 4.
In the first embodiment, an example is shown in which the radially outer end of the cylinder 23 of the vane 26 is in direct contact with the spring 30. In this embodiment, an example is shown in which an elastic body 31 is provided between the radially outer end of the cylinder 23 of the vane 26 (the surface of the vane 26 opposite to the side contacting the piston 22) and the spring 30. Unless otherwise specified, the same reference numerals and terms are used to refer to the same as in the above embodiment. Therefore, the structure of this embodiment also includes the piston 22, the cylinder 23, the vane 26, the spring 30, the elastic body 31 (31a or 31b), the vane groove 32, and the spring storage hole 33.

Figure 11 shows a cross-sectional view of the vane sliding structure of this embodiment. In the figure, the vane 26 side of the winding closest to the vane 26 side of the wire of the spring 30 is configured to contact the elastic body 31 (vane end elastic body 31a) provided at the radially outer end of the cylinder 23 of the vane 26. Here, the vane end elastic body 31a is also provided on the surface that contacts the vane 26 side of the winding closest to the vane 26 side of the wire of the spring 30 at the radially outer end of the cylinder 23 of the vane 26. Specifically, the vane end elastic body 31a has protruding parts that protrude toward the radially outer side of the cylinder 23 on both sides of the width direction on the radially outer side of the spring 30, and is shaped to surround the vane side end of the spring 30. In other words, the vane end elastic body 31a is integrally formed of a convex portion that protrudes radially outward of the cylinder 23 on both sides of the widthwise end of the vane 26 perpendicular to the movement direction and thickness direction of the vane 26, and a concave portion that contacts the spring 30 at the center of the vane width direction.

The vane end elastic body 31a may be assembled to the radially outer end of the cylinder 23 of the vane 26 by providing a protrusion on the radially outer end of the cylinder 23 of the vane 26 and assembling the vane end elastic body 31a having a hole that engages with this protrusion.

The vane end elastic body 31a restricts the widthwise movement of the vane 26 of the spring 30 whose end contacts the recessed portion by the convex portion at the widthwise end of the vane 26. The recessed portion of the vane 26 of the vane end elastic body 31a receives the spring force from the spring 30 and pushes the vane 26 toward the piston 22. In addition, the recessed portion of the vane 26 of the vane end elastic body 31a receives the spring force from the spring 30 and elastically deforms at the contact portion with the spring 30, which also has the effect of restricting the movement of the vane 26 in a direction perpendicular to the moving direction.

In addition, when vane flying occurs, the widthwise protrusion of the vane end elastic body 31a comes into contact with and collides with the radially outer end side of the vane groove 32 (cylinder 23) of the cylinder 23. At this time, a cylinder outer elastic body 31b may be provided on the radially outer end side of the vane groove 32 (cylinder 23) of the cylinder 23 so as to come into contact with the widthwise protrusion of the vane end elastic body 31a.

Furthermore, the vane end elastic body 31a may be combined with the form in which the elastic body 31 (31a, 31b) is provided inside the wire windings of the spring 30, as shown as an example in the first embodiment. The cylinder outer elastic body 31b in the first embodiment is shaped to fit inside the wire windings at the radially outer end of the cylinder 23 of the spring 30. This cylinder outer elastic body 31b can be combined with the vane end elastic body 31a in which the convex portion at the vane width direction end and the concave portion at the vane width direction center are integrated.

In this combination, when vane flying occurs, there are two possible contacts. One is contact between the convex part at the vane width direction end of the vane end elastic body 31a and the radially outer end of the cylinder 23. The other is contact between the cylinder outer elastic body 31b provided inside the wire winding of the spring 30 and the concave part at the center of the vane width direction of the vane end elastic body 31a. The dimensions of the vane movement direction of the vane end elastic body 31a and the cylinder outer elastic body 31b may be set so that these two contacts occur simultaneously. The dimensions to be set are the convex part at the vane width direction end of the vane end elastic body 31a, the concave part at the center of the vane width direction, and the dimensions of the cylinder outer elastic body 31b in the vane 26 movement direction. Alternatively, the dimensions of the vane 26 movement direction may be set so that one of these two contacts comes into contact first, and the other comes into contact when the vane 26 advances further.

These dimensions are adjusted by adjusting the outer distance in the vane movement direction between the convex portion of the vane width direction end of the vane end elastic body 31a and the radial outer end of the cylinder 23 at the reference position of the vane 26, and the inner distance in the vane movement direction between the cylinder outer elastic body 31b provided inside the wire winding of the spring 30 and the concave portion in the vane width direction center of the vane end elastic body 31a. To make the two contacts occur simultaneously, the outer distance and the inner distance are made to be the same. Also, to make the convex portion of the vane width direction end of the vane end elastic body 31a contact the radial outer end of the cylinder 23 first, the outer distance is made smaller than the inner distance.

If the dimensions are set so that the above two contacts occur simultaneously, the impact speed of the vane 26 can be instantly suppressed. If the dimensions are set so that one of the two contacts occurs first and then the other contacts when the vane 26 continues to move forward, the impact speed of the vane 26 is suppressed in two stages, which is thought to result in a smaller impact on the equipment.

The modulus of elasticity of the convex portion at the end of the vane width direction of the vane end elastic body 31a may be different from the overall modulus of elasticity of the concave portion at the center of the vane width direction of the vane end elastic body 31a and the cylinder outer elastic body 31b provided inside the wire winding of the spring 30. This is because, when the dimensions are set so that one of the two contacts comes into contact first and the other contacts when the vane 26 advances further, the impact speed is reduced by the first contact, and then the second contact more strongly suppresses the impact speed, so that the impact is thought to be smaller.

In addition, a widthwise central convex portion of the elastic body 31 that protrudes radially outward of the cylinder 23 may be provided at the widthwise central portion of the vane end elastic body 31a, inside the winding of the spring 30. Here, the vane end elastic body 31a is integral with convex portions that protrude radially outward of the cylinder 23 at both ends in the vane width direction perpendicular to the movement direction and thickness direction of the vane 26, a concave portion that contacts the spring 30 at the vane width central portion, and the widthwise central convex portion provided in this concave portion.

If the vane end elastic body 31a with the widthwise central convex portion is used, when the vane jumps, the cylinder outer elastic body 31b provided inside the wire windings at the radially outer end of the cylinder 23 of the spring 30 comes into contact with the widthwise central convex portion of the vane end elastic body 31a. In this case, the effect of the elastic body 31 is improved by the volume of the widthwise central convex portion of the vane end elastic body 31a, and the collision speed between the vane 26 side and the radially outer end side of the cylinder 23 (acceleration (deceleration) on the deceleration side at the time of collision) is mitigated.

According to the configuration of this embodiment, even if vane flying occurs, causing the vane 26 to fly and come into contact with the cylinder 23, the vane 26 will collide with the cylinder 23 via the elastic body 31. By making contact via this elastic body 31, the collision speed between the vane 26 and the cylinder 23 can be reduced, and fatigue damage due to repeated impact loads at the spring 30 fixing portion can be prevented.

Even if the vane flies off, the collision speed between the vane 26 and the cylinder 23 can be mitigated, preventing the wire of the spring 30 from repeatedly deforming to overcome the adjacent spiral or to penetrate inside the spiral, which would cause fatigue failure. This prevents the spring 30 from breaking due to the vane flying off, without causing the compressor to become larger due to major structural changes or an increase in sliding resistance during normal operation.

In addition, the radially outer end of the cylinder 23 of the vane 26 is formed of a vane end elastic body 31a that contacts the spring 30, and the contacting vane end elastic body 31a is pressed against the vane 26 by the spring force of the spring 30, making it difficult for the vane end elastic body 31a to come off the vane 26.

In addition, as shown in FIG. 11, by having an elastic body 31 (vane end elastic body 31a) between the radial outer end of the cylinder 23 of the vane 26 and the spring 30, the elastic body 31 (vane end elastic body 31a) to be attached can be made into a single component (elastic body), thereby reducing the number of processes for assembling the elastic body.

Embodiment 5.
In the above embodiment, there is no particular definition for the shape of the surface parallel to the vane movement direction which is the outer shape of the elastic body 31. In the present embodiment, an example will be described in which projections and recesses are provided on the surface parallel to the vane movement direction which is the outer shape of the elastic body 31.

Figure 12 (1) is a cross-sectional view of the vane sliding structure of this embodiment. In the figure, the elastic body 31 (vane end elastic body 31a, cylinder outer elastic body 31b) has unevenness in the direction perpendicular to the moving direction of the vane 26, and the concave portion has a convex portion of the vane 26 or a convex portion of the cylinder 23, and is configured to mesh with it. Figure 12 (2) shows a partial enlarged view of the convex portion of the vane 26. Also, Figure 12 (3) shows an enlarged view of one side of the vane end elastic body 31a. In this example, the elastic body 31 has a concave portion on both ends in the thickness direction of the vane 26, and meshes with the convex portions provided on both ends in the thickness direction of the radially outer protrusion of the vane 26.

In the above example, the cross-sectional area of the elastic body 31 in a section perpendicular to the sliding direction of the vane 26 changes from the piston 22 side toward the radially outer side of the cylinder 23. To fit (interlock) with this, the shape of the radially outer protrusion of the vane 26 or the outer end of the cylinder 23 changes in response to the change in the cross-sectional area of the elastic body 31.

Because the elastic body 31 has convex and concave portions in the direction perpendicular to the moving direction of the vane 26, even if a load is applied to the elastic body 31 (vane end elastic body 31a, cylinder outer elastic body 31b) that would cause it to come off the vane 26 or cylinder 23 when the vane 26 moves in the moving direction, the concave portion of the elastic body 31 engages with the convex portion of the vane 26 or the convex portion of the cylinder 23, preventing the elastic body 31 from coming off the vane 26 or cylinder 23. In addition, during assembly, the elastic body 31 (vane end elastic body 31a, cylinder outer elastic body 31b) flexibly deforms, so that the concave portion of the elastic body 31 can engage with the convex portion of the vane 26 or the convex portion of the cylinder 23.

Embodiment 6.
In the first embodiment, an example was shown in which the radially outer end of the spring 30 of the cylinder 23 is fixed to the spring storage hole 33 by a crimping force due to press-fitting. In the second embodiment, an example was shown in which the end of the spring 30 that contacts the vane 26 is fixed between the protrusions provided at both ends of the vane 26 in the width direction by a crimping force due to press-fitting. In this embodiment, a protrusion is provided at the width direction center of the radially outer end of the cylinder 23 of the vane 26, or at a cover portion that closes the cylinder outer wall opening of the spring storage hole 33 that opens to the radially outer side of the cylinder 23, and the inner circumference of the coil (winding) of the spring 30 is press-fitted to the protrusion to fix it. Unless otherwise specified, the same reference numerals and terms are used to refer to the same as in the above embodiment. Therefore, the structure of this embodiment also has the piston 22, the cylinder 23, the vane 26, the spring 30, the elastic body 31 (31a or 31b), the vane groove 32, and the spring storage hole 33.

Figure 13 shows a cross-sectional view of the vane sliding structure of this embodiment. In the figure, the spring 30 is fixed by pressing the inner peripheral surface of the coil (winding) rather than the outer peripheral surface of the coil (winding) at the end of the spring 30. First, the fixing of the spring 30 to the vane 26 will be described. The vane 26 has a protrusion that protrudes radially outward from the cylinder 23 at the widthwise center of the radially outer end of the cylinder 23. This protrusion is formed into a shape that is pressed into the inner peripheral surface of the coil (winding) at the vane 26 side end of the spring 30. In other words, the spring 30 is pressed into the protrusion provided at the widthwise center of the vane 26.

An example of fixing the spring 30 to the radially outer end of the cylinder 23 in the spring storage hole 33 will be described. A cylinder outer wall opening that opens radially outward of the cylinder is provided at the radially outer end of the cylinder 23 in the spring storage hole 33. A lid portion (press-fit plate) 42 that closes this cylinder outer wall opening is provided. This lid portion (press-fit plate) 42 has a protrusion that protrudes toward the piston 22. This protrusion is formed into a shape that is pressed into the inner circumferential surface of the coil (winding) at the radially outer end of the cylinder 23 of the spring 30. That is, the spring 30 is pressed into the protrusion provided on the lid portion (press-fit plate) 42 that closes the cylinder outer wall opening.

According to this embodiment, by fixing the inner circumferential surface of the coil (winding) of the spring 30, even if a spring with a constant coil outer diameter (without a tapered coil outer diameter) is used, it is possible to prevent the spring 30 from coming into contact with the through hole of the cylinder 23. Therefore, the coil diameter of the tapered portion can be made the same as that of the parallel portion, and the stress generated in the spring 30 can be reduced.

Embodiment 7.
In the above embodiment, an example was shown in which the elastic body 31 is made of a rubber or gel material. In the present embodiment, an example will be described in which the elastic body 31 is a spring. Unless otherwise specified, the same reference numerals and terms are used to refer to the same as in the above embodiment. Therefore, the structure of this embodiment also has the piston 22, the cylinder 23, the vane 26, the spring 30, the elastic body 31 (31a or 31b), the vane groove 32, and the spring storage hole 33.

Figure 14 shows a cross-sectional view of the vane sliding structure of this embodiment. In the figure, a coiled elastic body 31a, which expands and contracts in the same direction as the spring 30, is provided on the outer periphery of the winding of the spring 30, which is connected to the radially outer end of the cylinder 23 of the vane 26. In the example shown in the figure, the coiled elastic body 31a is fixed by a crimping force caused by pressing into protrusions provided on both widthwise ends of the radially outer end of the cylinder 23 of the vane 26.

In addition, a coiled elastic body 31b having the same extension direction as the spring 30 is provided around the spring storage hole 33 at the radially outer end of the cylinder 23 in the vane groove 32. In the example shown in the figure, the coiled elastic body 31b is fixed by a crimping force due to press fitting into a circular groove provided at the radially outer end of the cylinder 23 in the vane groove 32 of the cylinder 23.

In the above, the method of fixing is described as being by a clamping force caused by press-fitting, but this is not limited to this. The fixing method may also be by using brazing material, welding, a solvent, resin, or adhesive.

Furthermore, the coiled elastic body 31a and the coiled elastic body 31b may each be replaced with a leaf spring. Instead of the coiled elastic body 31a, a curved leaf spring elastic body 31a may be used in which one end of the leaf spring is pressed into a groove provided at both widthwise ends of the radially outer end of the cylinder 23 of the vane 26, and the other end is a free end. In this case, when the vane jumps, the curved part of the curved leaf spring elastic body 31a is made to come into contact with the radially outer end of the cylinder 23 of the vane groove 32.

In addition, instead of the coil-shaped elastic body 31b, a curved leaf spring elastic body 31b may be used in which one end of the leaf spring is pressed into a groove provided at the radially outer end of the cylinder 23 of the vane groove 32, and the other end is a free end. In this case, when the vane jumps, the curved part of the curved leaf spring elastic body 31b is made to come into contact with the radially outer end of the cylinder 23 of the vane 26.

The coil-shaped elastic body 31a, the coil-shaped elastic body 31b and the leaf spring elastic body 31a, the leaf spring elastic body 31b may be located on either or both of the vane 26 side and the radially outer side of the cylinder 23.

According to this embodiment, the coil-shaped elastic body 31a, the coil-shaped elastic body 31b and the leaf spring elastic body 31a, the leaf spring elastic body 31b are all made of spring steel, which provides high environmental resistance and durability, thereby enabling the compressor to have a long life.

1 Rotary compressor 10 Prime mover (electric motor)
11 stator 12 rotor 20 compression mechanism 21 crankshaft 21a crankshaft eccentric portion 22 piston 23, 23a, 23b cylinder 24, 24a, 24b bearing 26 vane 27 plate 28 intake port 29 discharge port 30 spring 31 elastic body 31a vane end elastic body 31b cylinder outer elastic body 32 vane groove 33 spring storage hole 40 sealed container 52 compression chamber.

Claims (13)

A cylinder forming a compression chamber therein, and a piston that rotates eccentrically inside the cylinder;
a vane that is slidably disposed from the piston side toward the outside in the radial direction of the cylinder and divides the compression chamber;
a vane groove defining a sliding direction of the vane and having an opening on the inside of the cylinder;
a spring that presses the vane toward the piston from the radially outer side of the cylinder;
an elastic body provided at least one of an outer end of the vane in the radial direction of the cylinder and a position in the cylinder facing the vane in the radial direction of the cylinder, the elastic body having a smaller modulus of longitudinal elasticity than both the vane and the cylinder;
The elastic body is made of a rubber material or a gel material.
The elastic body has projections and recesses in a direction perpendicular to a moving direction of the vane,
A rotary compressor, wherein the concave portions of the concave and convex portions of the elastic body mesh with the convex portions provided on the vane or the cylinder. A cylinder forming a compression chamber therein, and a piston that rotates eccentrically inside the cylinder;
a vane that is slidably disposed from the piston side toward the outside in the radial direction of the cylinder and divides the compression chamber;
a vane groove defining a sliding direction of the vane and having an opening on the inside of the cylinder;
a spring that presses the vane toward the piston from the radially outer side of the cylinder;
an elastic body provided at least one of an outer end of the vane in the radial direction of the cylinder and a position in the cylinder facing the vane in the radial direction of the cylinder, the elastic body having a smaller modulus of longitudinal elasticity than both the vane and the cylinder;
The elastic body is made of a rubber material or a gel material.
a spring storage hole for storing the spring within the cylinder;
the elastic body is disposed in the spring storage hole and inside the wire winding of the spring;
the spring storage hole has a cylinder outer wall opening that opens radially outward of the cylinder,
A rotary compressor, wherein a radially outer end of the elastic body is fixed to an opening in an outer wall of the cylinder. A cylinder forming a compression chamber therein, and a piston that rotates eccentrically inside the cylinder;
a vane that is slidably disposed from the piston side toward the outside in the radial direction of the cylinder and divides the compression chamber;
a vane groove defining a sliding direction of the vane and having an opening on the inside of the cylinder;
a spring that presses the vane toward the piston from the radially outer side of the cylinder;
an elastic body provided at least one of an outer end of the vane in the radial direction of the cylinder and a position in the cylinder facing the vane in the radial direction of the cylinder, the elastic body having a smaller modulus of longitudinal elasticity than both the vane and the cylinder;
The elastic body is made of a rubber material or a gel material.
The elastic body is provided at both ends or at the center in the width direction of the radially outer end of the cylinder of the vane,
The elastic body includes a portion provided between the vane and the spring. The rotary compressor according to claim 1 or 2, wherein the elastic body is provided at both ends in the width direction of the radially outer end of the cylinder of the vane. The rotary compressor according to claim 1 or 2, wherein the elastic body is provided at the width center of the radially outer end of the cylinder of the vane. The rotary compressor according to claim 1 or 3, wherein the elastic body is provided on the inner wall of the cylinder radially outside the vane groove. a spring storage hole for storing the spring within the cylinder;
4. The rotary compressor according to claim 1, wherein the elastic body is provided in the spring housing hole and inside the wire winding of the spring. the spring storage hole has a cylinder outer wall opening that opens radially outward of the cylinder,
8. The rotary compressor according to claim 7, wherein a radially outer end of said elastic body in the cylinder is fixed to a lid that engages with an opening in an outer wall of said cylinder. The rotary compressor according to any one of claims 1 to 3, wherein the elastic body has a ring shape. The rotary compressor according to any one of claims 1 to 3, wherein the vane and the spring are fixedly attached. The rotary compressor according to any one of claims 1 to 3, wherein the radially outer end of the spring and the cylinder are fixed to each other. The rotary compressor according to claim 10, wherein the vane and the spring are fixed by pressing the inner or outer periphery of the end of the spring into the vane. The rotary compressor according to claim 10, wherein the vane and the spring are secured together by brazing, welding, a solvent, a resin, or an adhesive.

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