JP7013138B2 - Compressor and refrigeration cycle equipment - Google Patents

Description

Embodiments of the present invention relate to a compressor and a refrigeration cycle device including the compressor.

Refrigeration cycle devices such as air conditioners are equipped with a compressor that compresses the working fluid. The compressor has a compression chamber that compresses the working fluid, a closed container to which the working fluid compressed in the compression chamber is supplied, and a discharge hole in the compression chamber when the pressure in the compression chamber becomes higher than the pressure in the closed container. It is equipped with a discharge valve that opens. In order to increase the efficiency of the refrigeration cycle, it is preferable that the discharge valve responds quickly even if the pressure difference between the pressure in the compression chamber and the pressure in the closed container is small.

The responsiveness of the discharge valve depends on the pressure receiving area of the discharge valve. Patent Document 1 proposes a rotary compressor in which a widening portion is formed in a discharge hole to increase the pressure receiving area of a discharge valve. The widening portion of Patent Document 1 is characterized in that the widening angle α is 30 ° ≦ α ≦ 60 °, and is formed so as to widen in the discharge direction. However, the discharge valve is formed very thin. When the pressure receiving area of the discharge valve is increased, the responsiveness of the discharge valve is improved, but the discharge valve is easily cracked and damaged.

Japanese Unexamined Patent Publication No. 2011-43084

An object of the present invention is to provide a compressor provided with a discharge valve which responds even with a small differential pressure and is not easily broken even when subjected to a large differential pressure, and a refrigeration cycle device provided with the compressor.

The compressor of one embodiment includes a compression chamber, a rotating shaft, a bearing, a discharge hole, a discharge valve, and a discharge valve seat. The compression chamber compresses the working fluid. The axis of rotation rolls a roller arranged in the compression chamber. The bearing rotatably supports the axis of rotation. The discharge hole is formed in the recess of the bearing, which is lower than the upper surface of the bearing, and discharges the compressed working fluid. The discharge valve opens or closes the discharge hole. With the discharge hole closed, the discharge valve can be deformed between the first shape and the second shape. The first shape bends toward the compression chamber. The second shape has a smaller amount of deflection than the first shape. The discharge valve seat is formed in an annular shape around the discharge hole. The discharge valve seat has an inner ring portion that surrounds the discharge hole , a circular ridge line that protrudes from the upper surface of the recess and connects the apex farthest from the upper surface of the recess, and is arranged on the outer periphery of the inner ring portion and spreads inward from the ridge line. It has a support portion having a shape that abuts on the discharge valve of the first shape but does not abut on the discharge valve of the second shape, and an outer ring portion that extends outward from the ridgeline . The shape of the support portion is a conical surface inclined so as to approach the compression chamber from the outer peripheral side toward the center of the discharge hole. The inner ring portion smoothly connects the discharge hole and the conical surface of the support portion. The first-shaped discharge valve comes into surface contact with the support portion. The second-shaped discharge valve makes line contact with the ridgeline of the discharge valve seat. The pressure receiving area where the first-shaped discharge valve receives pressure from the working fluid is smaller than the pressure receiving area where the second-shaped discharge valve receives pressure from the working fluid because it is in contact with the support portion .

The refrigeration cycle apparatus of one embodiment includes the above-mentioned compressor and a refrigeration cycle circuit. In the refrigeration cycle circuit, a radiator, an expansion device, and a heat absorber are connected in order, and a working fluid circulates. The compressor is connected to a refrigeration cycle circuit between the radiator and the heat absorber.

FIG. 1 is a cross-sectional view showing an example of a compressor of one embodiment. FIG. 2 is a cross-sectional view of the first cylinder chamber shown in FIG. FIG. 3 is a plan view of the discharge hole shown in FIG. FIG. 4 is a cross-sectional view taken along the line F4-F4 in FIG. FIG. 5 is a cross-sectional view illustrating the first shape and the second shape of the discharge valve.

Hereinafter, the compressor of one embodiment will be described with reference to FIGS. 1 to 5. FIG. 1 is a cross-sectional view showing an example of the compressor 2 of one embodiment. FIG. 1 also shows the refrigeration cycle circuit of the refrigeration cycle apparatus 1 provided with the compressor 2.

As shown in FIG. 1, the refrigerating cycle device 1 includes a compressor 2, a condenser 3 which is a radiator, an expansion device 4, and an evaporator 5 which is a heat absorber as main elements. The condenser 3, the expansion device 4, and the evaporator 5 are sequentially connected by a refrigerant pipe 7. The compressor 2 is connected between the condenser 3 and the evaporator 5. An accumulator 6 is attached to the compressor 2. The main element of the refrigeration cycle device 1 constitutes a refrigeration cycle circuit in which the working fluid circulates.

The compressor 2 includes a closed container 10, an electric motor unit 11, a compression mechanism unit 12, and a rotating shaft 13. The closed container 10 is formed in a hollow cylindrical shape. The motor unit 11 and the compression mechanism unit 12 are housed in a closed container 10 and are connected to each other via a rotating shaft 13. The closed container 10 is an example of a housing, the motor unit 11 is an example of a driving element, and the compression mechanism unit 12 is an example of a compression element.

In the example shown in FIG. 1, the compressor 2 is configured as a vertical rotary compressor. The compressor 2 is not limited to the vertical type but may be a horizontal type. In the description of FIG. 1, the direction from the motor unit 11 to the compression mechanism unit 12 along the rotating shaft 13 is referred to as "downward" or "downward", and the opposite direction is referred to as "upward" or "upper". Further, the length of the rotating shaft 13 in the axial direction is simply referred to as "height".

Lubricating oil is stored in the bottom of the closed container 10, and the remaining space is filled with a gas refrigerant as a working fluid. The suction pipes 14 and 15 and the discharge pipe 16 are attached to the closed container 10. The suction pipes 14 and 15 penetrate the body of the closed container 10 and allow the inside and outside of the closed container 10 to communicate with each other. The discharge pipe 16 penetrates the lid portion of the closed container 10 and communicates the inside and outside of the closed container 10. The suction pipes 14 and 15 are connected to the evaporator 5 via an accumulator 6. The discharge pipe 16 is connected to the condenser 3.

The motor unit 11 includes a stator 17 and a rotor 18. The stator 17 is fixed to the inner peripheral surface of the closed container 10. The rotor 18 is fixed to the rotating shaft 13. The outer peripheral surface of the rotor 18 faces the inner peripheral surface of the stator 17 with a slight gap.

The compression mechanism unit 12 is located below the motor unit 11. The compression mechanism unit 12 includes, for example, a first cylinder 21, a second cylinder 22, an intermediate partition plate 23, a main bearing 24, an auxiliary bearing 25, and valve covers 26, 27, 28. The first cylinder 21 is fixed to the inner peripheral surface of the closed container 10 by welding, for example. The main bearing 24 may be fixed to the inner peripheral surface of the closed container 10 instead of the first cylinder 21. The valve covers 26 and 27, the main bearing 24, the first cylinder 21, the intermediate partition plate 23, the second cylinder 22, the auxiliary bearing 25 and the valve cover 28 are sequentially stacked from the motor portion 11 side and fixed to each other by, for example, co-tightening. ing.

The main bearing 24 and the auxiliary bearing 25 rotatably support the rotating shaft 13. Discharge holes 41 and 42 are formed in the main bearing 24 and the auxiliary bearing 25, respectively. The discharge hole 41 of the main bearing 24 is covered with the valve covers 26 and 27, and the discharge hole 42 of the auxiliary bearing 25 is covered with the valve cover 28.

The first cylinder 21 is formed with a circular first cylinder chamber 31 sandwiched between the main bearing 24 and the intermediate partition plate 23. The second cylinder 22 is formed with a circular second cylinder chamber 32 sandwiched between the intermediate partition plate 23 and the auxiliary bearing 25. The rotating shaft 13 has eccentric portions 13A and 13B protruding in a direction orthogonal to the axial direction. The eccentric portions 13A and 13B are arranged so as to be offset by, for example, 180 ° in the rotation direction of the rotation shaft 13. Cylindrical rollers 33 and 34 are fitted to the eccentric portions 13A and 13B, respectively.

The eccentric portion 13A and the roller 33 are arranged in the first cylinder chamber 31. The eccentric portion 13B and the roller 34 are arranged in the second cylinder chamber 32. When the rotating shaft 13 rotates, the roller 33 rolls in contact with the first cylinder chamber 31, and the roller 34 rolls in contact with the cylinder chamber 32.

FIG. 2 is a cross-sectional view of the first cylinder chamber 31. The second cylinder chamber 32 has substantially the same shape and function as the first cylinder chamber 31. Therefore, the first cylinder chamber 31 will be described in detail as a representative, and the duplicate description of the second cylinder chamber 32 will be omitted. As shown in FIG. 2, the first cylinder 21 is formed with a vane slot 35 extending in the radial direction of the first cylinder chamber 31.

The vane 36 is housed in the vane slot 35 so as to be retractable. The tip of the vane 36 is slidably in contact with the outer peripheral surface of the roller 33, and divides the first cylinder chamber 31 into two. The base end of the vane 36 is urged toward the first cylinder chamber 31 by a coil spring 37 installed in the vane slot 35.

The first cylinder 21 is formed with a suction hole 40 that allows the inside and outside of the first cylinder chamber 31 to communicate with each other. The suction pipe 14 shown in FIG. 1 is connected to the suction hole 40. The working fluid supplied from the refrigeration cycle circuit is guided from the suction hole 40 to the first cylinder chamber 31. The working fluid is compressed in the first and second cylinder chambers 31 and 32 as the rotating shaft 13 rotates. The first and second cylinder chambers 31 and 32 are examples of compression chambers for compressing the working fluid.

As shown in FIG. 1, the working fluid compressed in the first cylinder chamber 31 is discharged into the valve cover 27 through the discharge hole 41. The working fluid compressed in the second cylinder chamber 32 is discharged into the valve cover 28 through the discharge hole 42 of the auxiliary bearing 25. The intermediate partition plate 23 may have a hollow structure and the working fluid may be discharged into the intermediate partition plate 23. In that case, the same discharge holes as the discharge holes 41 and 42 are formed in the intermediate partition plate 23.

The inside of the valve cover 28 communicates with the inside of the valve cover 27 through a communication passage 43 (shown in FIG. 2) penetrating the auxiliary bearing 25, the second cylinder 22, the intermediate partition plate 23, the first cylinder 21, and the main bearing 24. .. The working fluid discharged from the first and second cylinder chambers 31 and 32 into the valve covers 27 and 28 is supplied into the closed container 10 through the opening formed in the valve cover 26.

The working fluid in the closed container 10 is guided to the condenser 3 through the discharge pipe 16 and the refrigerant pipe 7, and is condensed in the evaporator 3. The condensed working fluid is expanded and depressurized in the expansion device 4, then evaporated in the evaporator 5, and gas-liquid separated in the accumulator 6. The working fluid separated by the accumulator 6 is supplied to the first and second cylinder chambers 31 and 32 through the suction pipes 14 and 15, respectively. The working fluid supplied to the first and second cylinder chambers 31 and 32 is compressed again and supplied into the closed container 10.

The discharge hole 41 of the main bearing 24 is provided with a discharge valve mechanism 50 that opens or closes the discharge hole 41. Hereinafter, the discharge valve mechanism 50 according to the present embodiment will be described in detail with reference to FIGS. 3 to 5. The discharge valve mechanism 50 provided in the discharge holes of the auxiliary bearing 25 and the intermediate partition plate 23 has substantially the same shape and function as the discharge valve mechanism 50 provided in the discharge hole 41. Therefore, the discharge valve mechanism 50 provided in the discharge hole 41 will be described in detail as a representative, and the overlapping description of the discharge valve mechanism 50 provided in the other discharge holes will be omitted.

FIG. 3 is a plan view of the discharge hole 41 formed in the main bearing 24. The main bearing 24 is formed with a discharge hole 41 that communicates with the first cylinder chamber 31. As shown in FIG. 3, the discharge hole 41 is formed in a recess 44 lower than the upper surface 24A of the main bearing 24. The upper surface 24A and the recess 44 of the main bearing 24 are smoothly continuous with the guide groove 45. The discharge valve mechanism 50 is provided in the recess 44.

The discharge valve mechanism 50 includes a discharge valve seat 51, a discharge valve 52, and a valve retainer 53. The discharge valve seat 51 is formed in an annular shape around the discharge hole 41. The discharge valve 52 is formed in a strip shape from an elastic body such as spring steel. The base end (fixed end) 52P of the discharge valve 52 is fixed to the main bearing 24.

The tip (free end) 52D of the discharge valve 52 is formed in a circular shape larger than the discharge hole 41. While the pressure in the first cylinder chamber 31 is lower than the pressure in the closed container 10, the tip 52D sits on the discharge valve seat 51 and closes the discharge hole 41. The pressure in the first cylinder chamber 31 gradually increases with the rotation of the rotating shaft 13. When the pressure in the first cylinder chamber 31 and the pressure in the closed container 10 are reversed and the pressure in the first cylinder chamber 31 becomes higher than the pressure in the closed container 10, the tip 52D is moved from the discharge valve seat 51. Ascend to open the discharge hole 41.

The tip 52D may have a film having a hardness lower than that of the material forming the discharge valve seat 51. The discharge valve seat 51 is made of, for example, a steel material. The film of the discharge valve 52 is formed of, for example, resin, and cushions the impact when the discharge valve 52 is closed. The valve retainer 53 faces the tip 52D of the discharge valve 52 from above with an interval, and regulates the maximum opening degree of the discharge valve 52. In the example shown in FIG. 3, the valve retainer 53 is a steel plate thicker than the discharge valve 52 formed in a strip shape curved upward.

FIG. 4 is a cross-sectional view taken along the line F4-F4 in FIG. As shown in FIG. 4, the discharge valve seat 51 projects from the upper surface 44A of the recess 44. In the discharge valve seat 51, the line connecting the vertices farthest from the upper surface 44A of the recess 44 is referred to as a ridge line 51R. The ridge line 51R is circular.

The discharge valve seat 51 has an inner ring portion 54 surrounding the discharge hole 41, a support portion 55 extending inward from the ridge line 51R, and an outer ring portion 56 extending outward from the ridge line 51R. The inner ring portion 54, the support portion 55, and the outer ring portion 56 are each formed in an annular shape. The inner ring portion 54 smoothly connects the discharge hole 41 and the support portion 55. The outer ring portion 56 smoothly connects the ridge line 51R and the upper surface 44A of the recess 44. The support portion 55 may have a film having a hardness lower than that of the material forming the discharge valve seat 51. The film of the support portion 55 is formed of, for example, resin, like the film of the discharge valve 52, and cushions the impact when the discharge valve 52 is closed.

The support portion 55 is slightly inclined toward the center 41X of the discharge hole 41 so as to approach the first cylinder chamber 31. That is, the support portion 55 is formed on a conical surface recessed toward the first cylinder chamber 31 side. The gradient of the conical surface of the support portion 55 with respect to the plane including the ridge line 51R of the discharge valve seat 51 is defined as the inclination angle θ. The length from the center 41X of the discharge hole 41 to the ridge line 51R is defined as the maximum radius a of the support portion 55.

FIG. 5 is a cross-sectional view illustrating the first shape S1 and the second shape S2 of the discharge valve 52. As shown in FIG. 5, the tip 52D of the discharge valve 52, which is an elastic body, has the pressure in the closed container 10 and the first cylinder in a state where the discharge hole 41 is closed, that is, when the discharge valve seat 51 is seated. It is configured to be deformable according to the differential pressure with the pressure in the chamber 31.

FIG. 5 shows an example of the first shape in which the pressure difference between the pressure in the closed container 10 and the pressure in the first cylinder chamber 31 is large and the tip 52D of the discharge valve 52 is greatly bent toward the first cylinder chamber 31. It is indicated by S1 inside. An example of the second shape in which the differential pressure between the pressure in the closed container 10 and the pressure in the first cylinder chamber 31 gradually becomes smaller, and the amount of bending of the tip 52D of the discharge valve 52 becomes smaller than that in the first shape S1. Is shown by S2 in FIG.

である。
Ｐ：先端５２Ｄに作用する最大差圧［Ｎ／ｍ^２］
ａ：支持部５５の最大半径［ｍ］
ν：先端５２Ｄのポアソン比
Ｄ：先端５２Ｄの曲げ剛性［Ｎｍ］
ここで、吐出弁５２の先端５２Ｄの曲げ剛性Ｄは、

である。
Ｅ：吐出弁５２の先端５２Ｄの縦弾性係数［Ｎ／ｍ^２］
ｈ：吐出弁５２の先端５２Ｄの厚み［ｍ］
ｒ＝ａにおけるたわみ曲線の傾きｗ´_ｒ＝ａは、ｗをｒで微分して、

となる。 The shape of the tip 52D of the discharge valve 52 when receiving the maximum differential pressure is calculated.
When the tip 52D of the discharge valve 52 receives the maximum differential pressure, the deflection curve w with respect to the radius r of the circular tip 52D is

Is.
P: Maximum differential pressure acting on the tip 52D [N / m ² ]
a: Maximum radius of the support portion 55 [m]
ν: Poisson's ratio of tip 52D
D: Flexural rigidity of the tip 52D [Nm]
Here, the bending rigidity D of the tip 52D of the discharge valve 52 is

Is.
E: Young's modulus of the tip 52D of the discharge valve 52 [N / m ² ]
h: Thickness [m] of the tip 52D of the discharge valve 52
The slope w'r = a of the deflection curve at _{r = a} is obtained by differentiating w with r.

Will be.

となる形状を有していることが特徴である。
仮に、支持部５５の傾斜角度θが、

であれば、
吐出弁５２が最大差圧を受けても、支持部５５と吐出弁５２とは接触しない。
本実施形態のように、支持部５５の傾斜角度θが、

であれば、
吐出弁５２が最大差圧を受ける前に、支持部５５と吐出弁５２とは接触する。 The support portion 55 according to the present embodiment has an inclination angle θ.

It is characterized by having a shape that becomes.
Temporarily, the inclination angle θ of the support portion 55 is

If,
Even if the discharge valve 52 receives the maximum differential pressure, the support portion 55 and the discharge valve 52 do not come into contact with each other.
As in the present embodiment, the inclination angle θ of the support portion 55 is

If,
The support portion 55 and the discharge valve 52 come into contact with each other before the discharge valve 52 receives the maximum differential pressure.

In FIGS. 4 and 5, the deformation of the discharge valve 52 and the inclination angle θ are exaggerated for the sake of explaining the invention, but the actual inclination angle θ may be a slight angle (not shown). The inclination angle θ is appropriately selected depending on the operating pressure of the compressor 2 and the material of the discharge valve 52, and is, for example, about 1 to 2 °, and at most 5 ° or less.

In the example shown in FIG. 5, the discharge valve 52 of the first shape S1 is in contact with the support portion 55 in a state where the discharge valve 52 is seated on the discharge valve seat 51. That is, the discharge valve seat 51 and the discharge valve 52 of the first shape S1 are in surface contact with each other at the support portion 55. The pressure receiving area where the discharge valve 52 of the first shape receives pressure from the working fluid in the closed container 10 and the first cylinder chamber 31 is shown by A1 in FIG.

On the other hand, the discharge valve 52 of the second shape S2, which has a smaller amount of deflection than the first shape S1, does not abut on the support portion 55. The discharge valve seat 51 and the tip 52D of the second shape S2 are in line contact with each other at the ridge line 51R. The pressure receiving area where the second-shaped discharge valve 52 receives pressure from the working fluid in the closed container 10 and the first cylinder chamber 31 is shown by A2 in FIG.

The pressure receiving area A2 of the discharge valve 52 of the second shape S2 in line contact with the ridge line 51R is larger than the pressure receiving area A1 of the discharge valve 52 of the first shape S1 in surface contact with the support portion 55. The force received by the discharge valve 52 is determined by the product of the pressure receiving area of the discharge valve 52 and the differential pressure in the closed container 10 and the first cylinder chamber 31. If it is desired to prevent the discharge valve 52 from being damaged even if it receives a large differential pressure, the pressure receiving area of the discharge valve 52 may be reduced. If it is desired that the discharge valve 52 responds quickly even with a small differential pressure, the pressure receiving area of the discharge valve 52 may be increased.

The compressor 2 of the present embodiment configured as described above has a support portion 55 having a shape in which the discharge valve 52 of the first shape S1 abuts but the discharge valve 52 of the second shape S2 does not abut. There is. The pressure receiving area A1 of the discharge valve 52 of the first shape S1 is smaller than the pressure receiving area A2 of the discharge valve 52 of the second shape S2 by the amount of contact with the support portion 55.

In the first shape S1 that receives a large differential pressure, the pressure receiving area A1 of the discharge valve 52 can be reduced, so that the force received by the discharge valve 52 can be reduced to prevent damage to the discharge valve 52. At this time, the discharge valve seat 51 and the discharge valve 52 are in surface contact with each other. Since the force received by the discharge valve seat 51 can be dispersed over the entire support portion 55, local cracking of the discharge valve 52 can be prevented. Since the discharge valve seat 51 and the discharge valve 52 come into contact with each other on a surface having a width instead of a line, it is possible to reduce the leakage loss that flows back from the closed container 10 to the first cylinder chamber 31.

Further, the pressure receiving area A2 of the discharge valve 52 of the second shape S2 is larger than the pressure receiving area A1 of the discharge valve 52 of the first shape S1 by the amount not in contact with the support portion 55. In the second shape S2 in which the pressure difference between the pressure in the closed container 10 and the pressure in the first cylinder chamber 31 is small, the pressure receiving area A2 of the discharge valve 52 can be increased, so that the pressure in the first cylinder chamber 31 can be increased. When the pressure becomes higher than the pressure in the closed container 10, the discharge hole 41 can be quickly opened without loss of time. As a result, it is possible to reduce the overcompression loss of the first cylinder chamber 31 and the noise caused by opening and closing the discharge valve 52.

The discharge valve seat 51 and the discharge valve 52 of the second shape S2 are in line contact with each other at the ridge line 51R. If the discharge valve seat 51 to which the lubricating oil is attached and the discharge valve 52 are in surface contact with each other, the response of the discharge valve 52 may be delayed due to the adhesive force of the lubricating oil. In the present embodiment, since the discharge valve 52 is not in close contact with the discharge valve seat 51, the discharge hole 41 can be quickly opened without loss of time.

となる形状を有していることが特徴である。
本実施形態によれば、吐出弁５２が最大差圧を受ける前の第１形状Ｓ１において、支持部５５と吐出弁５２とを確実に接触させることができる。 If the inclination angle θ is as large as 30 ° ≦ θ ≦ 60 °, the discharge valve 52 cannot be supported by the support portion 55.
On the other hand, the support portion 55 according to the present embodiment has an inclination angle θ.

It is characterized by having a shape that becomes.
According to the present embodiment, the support portion 55 and the discharge valve 52 can be reliably brought into contact with each other in the first shape S1 before the discharge valve 52 receives the maximum differential pressure.

Either one or both of the support portion 55 and the discharge valve 52 has a film having a hardness lower than that of the material forming the discharge valve seat 51. The film formed on the support portion 55 and the discharge valve 52 alleviates the impact when the discharge valve 52 closes and prevents the discharge valve 52 from being damaged. Further, when the differential pressure between the pressure in the closed container 10 and the pressure in the first cylinder chamber 31 is large, the film is deformed and the adhesion between the support portion 55 and the discharge valve 52 is improved, so that the leakage loss can be reduced. ..

When forming a film on the discharge valve 52, since the discharge valve 52 is a member that can be fixed afterwards, there is an advantage that it is easier to manufacture than forming a film on the support portion 55. On the other hand, if a film is formed on the support portion 55 instead of forming a film on the discharge valve 52, the discharge valve 52 becomes lighter and has an advantage that the responsiveness of the discharge valve 52 can be improved.

According to the present embodiment, the compressor 2 is provided with a high-performance and highly reliable compressor 2 because it is provided with a discharge valve 52 that responds even with a small differential pressure and is not easily broken even with a large differential pressure. The refrigeration cycle device 1 can be provided.
Although some embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other embodiments, and various omissions, replacements, and changes can be made without departing from the gist of the invention. These embodiments and variations thereof are included in the scope and gist of the invention, and are also included in the scope of the invention described in the claims and the equivalent scope thereof.

For example, in the above description, an example of a two-cylinder type rotary compressor has been given, but a single-cylinder type or a multi-cylinder type having three or more cylinders may be used. As an example of rolling a roller as a rotary compressor, a swing type that swings a roller integrated with a vane may be used, or a scroll type that swings a spiral blade instead of a roller may be used.

1 ... Refrigeration cycle device, 2 ... Compressor, 3 ... Condenser (example of radiator), 4 ... Expansion device, 5 ... Evaporator (example of heat absorber), 31, 32 ... 1st and 2nd cylinder chambers (1) Example of compression chamber), 41, 42 ... Discharge hole, 51 ... Discharge valve seat, 52 ... Discharge valve, 55 ... Support part, a ... Maximum radius of support part, h ... Discharge valve thickness, S1 ... First shape, S2 ... second shape, θ ... tilt angle.

Claims (4)

A compression chamber that compresses the working fluid,
A rotating shaft that rolls the rollers arranged in the compression chamber, and
A bearing that rotatably supports the axis of rotation,
A discharge hole formed in the recess of the bearing, which is lower than the upper surface of the bearing, and discharges the compressed working fluid.
A discharge valve that opens or closes the discharge hole,
In a compressor provided with an annular discharge valve seat formed around the discharge hole.
The discharge valve can be deformed between a first shape that bends toward the compression chamber and a second shape that bends less than the first shape while the discharge hole is closed. And
The discharge valve seat has an inner ring portion that surrounds the discharge hole , a circular ridge line that protrudes from the upper surface of the recess and connects the apex farthest from the upper surface of the recess, and is arranged on the outer periphery of the inner ring portion from the ridge line . It has a support portion that spreads inward and abuts on the discharge valve of the first shape but does not abut on the discharge valve of the second shape, and an outer ring portion that extends outward from the ridgeline. ,
The shape of the support portion is a conical surface inclined so as to approach the compression chamber from the outer peripheral side toward the center of the discharge hole.
The inner ring portion smoothly connects the discharge hole and the conical surface of the support portion.
The first-shaped discharge valve is in surface contact with the support portion, the second-shaped discharge valve is in line contact with the ridgeline, and the first-shaped discharge valve applies pressure from the working fluid. The compressor is characterized in that the pressure receiving area is smaller than the pressure receiving area where the discharge valve having the second shape receives pressure from the working fluid by the amount of contact with the support portion . The inclination angle θ of the conical surface of the support portion is

P: Maximum differential pressure acting on the discharge valve [N / m ² ]
a: Maximum radius of the support [m]
ν: Poisson's ratio of the discharge valve D: Flexural rigidity of the discharge valve [Nm]
The compressor according to claim 1, wherein the compressor is characterized by satisfying the above conditions. The compressor according to claim 1 or 2, wherein at least one of the support portion and the discharge valve has a film having a hardness lower than that of the material forming the discharge valve seat. A refrigeration cycle circuit in which a radiator, an inflator, and a heat absorber are connected in order and the working fluid circulates,
The compressor according to any one of claims 1 to 3, which is connected to the refrigeration cycle circuit between the radiator and the heat absorber.
Refrigeration cycle device equipped with.

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