KR19980063759A - Intake valve device of refrigerant compressor - Google Patents

Abstract

According to the refrigerant flow rate, an inlet valve device of a refrigerant compressor for varying the opening area of the suction passage communicating the suction port and the suction chamber can be suppressed only in high speed operation. A movable valve is disposed in the suction passage, and moves in accordance with the change in the flow rate of the refrigerant gas flowing into the suction passage from the suction passage, thereby changing the opening area of the suction passage. When the pressurizing member presses the movable valve in a predetermined direction and the refrigerant gas flow rate reaches a first predetermined value, the refrigerant member contracts by the pressure of the refrigerant gas and moves the movable valve to the first position so that the suction valve moves to the first position. When the opening area is increased and the refrigerant gas flow rate exceeds the first predetermined value and reaches the second predetermined value, the refrigerant valve further contracts by the pressure of the larger refrigerant gas, thereby moving the movable valve to the second position. The opening area of the suction passage is reduced.

Description

Intake valve device of refrigerant compressor

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a suction valve device of a refrigerant compressor, and more particularly, to a suction valve device of a refrigerant compressor capable of preventing reverse rotation of a rotor when a ben-type compressor is stopped and suppressing a refrigerant flow rate at a high speed operation. It is about.

In a swash type compressor or wobble type compressor, the refrigerant gas is sucked into the suction chamber from the suction port of the compressor housing, and the refrigerant gas in the suction chamber is sucked into the compression chamber when the suction valve mounted on the suction port is opened.

On the other hand, in the Ben type compressor, the compression chamber and the suction chamber communicate with each other through the suction port only from the start of the suction stroke to the end of the suction stroke, and after the compression stroke starts, the compression chamber and the suction chamber are in a non-communication state. The suction gas and the discharge gas do not mix with each other.

As described above, since the ben-type compressor does not have a suction valve, the resistance when suctioning refrigerant gas into the compression chamber is smaller than that of other compressors, and the volumetric efficiency at high speed operation is high. However, since the flow rate at the time of high speed operation increases, there is a problem that the cooling capacity is excessive (exceeds the heat exchange capacity of the everpolator) and the power loss is systematically large.

Therefore, in the fixed capacity type ben type compressor, the diaphragm is provided in the suction passage which connects the suction port, the suction port, and the suction chamber to suppress the cooling ability during high speed operation.

By the way, in the method of installing the diaphragm, the capability at the time of high speed operation is not limited, but there is a problem that the capability is suppressed over the entire speed range.

On the other hand, the variable displacement compressor does not have such a problem, but there is a problem in that the capacity change mechanism is complicated and the cost of the compressor is increased.

SUMMARY OF THE INVENTION An object of the present invention is to provide an intake valve device of a refrigerant compressor which can change the opening area of the suction passage in accordance with the refrigerant flow rate, and can suppress the cooling capability only at high speed.

In order to achieve the above object, according to the present invention, there is provided a suction valve device of a compressor having a housing, a suction port formed in the housing, a suction chamber formed in the housing, and a suction passage communicating the suction port and the suction chamber.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a longitudinal sectional view of a refrigerant compressor (bench compressor) having a suction valve device according to a first embodiment of the present invention.

2A to 2C are enlarged cross-sectional views for explaining the operation of the intake valve device, wherein a is a state at the time of stopping the compressor, b is a state at low and medium speed, and c is a state diagram at high speed.

3 is a cross-sectional view taken along the line III-III of FIG.

4 is an enlarged cross-sectional view of a suction valve device of a second embodiment of the present invention;

5A to 5B are explanatory views of a suction valve device according to a third embodiment of the present invention, where a is an enlarged sectional view of the suction valve device, and b is a plan view of the stopper.

* Explanation of symbols for main parts of the drawings

1: Cam ring 2: Rotor

3: front side block 4: rear side block

5: front head 6: rear head

7: rotating shaft 8, 9: bearing

10 discharge chamber 11 suction chamber

12: compression space 13: benhom

14: Ben 16: discharge port

17: discharge valve cover 19: discharge valve

20: suction valve accommodation chamber 21: partition wall

22: refrigerant suction passage 30: suction valve device

31: movable valve 32: pressure member

34 opening 35 coil spring (first spring)

36: coil spring (second spring)

Intake valve device of the present invention,

A movable valve disposed in the suction passage and moving in accordance with a change in the flow rate of the refrigerant gas flowing into the suction passage from the suction passage to change the opening area of the suction passage; And

A pressurizing member for pressurizing the movable valve in a predetermined valve closing position direction. When the refrigerant gas flow rate reaches a first predetermined value, the movable valve contracts by the pressure of the refrigerant gas and moves the movable valve to the first position. When the opening area of the suction passage is increased and the refrigerant gas flow rate exceeds the first predetermined value and reaches the second predetermined value, the suction valve is further contracted by the pressure of the larger refrigerant gas, thereby causing the second movable valve to become second. It is characterized by consisting of a pressing member to move to the position of the small opening area of the suction passage.

In this suction valve apparatus, when the compressor is stopped, the movable valve is pushed to a predetermined valve closing position by the pressing force of the pressure member to close the suction passage and remain in non-communication state with the suction port and the suction chamber. When the flow rate of the refrigerant gas reaches the first predetermined value at the start of the compressor operation, the movable valve is pushed in the direction opposite to the position in which the predetermined valve is closed by the pressure of the introduced refrigerant gas, so that the pressure member contracts and the movable valve is removed. The suction port and the suction chamber communicate with each other by moving to a predetermined position of 1 to increase the opening area of the suction passage. In addition, during the high speed operation, when the flow rate of the refrigerant gas increases and reaches the second predetermined value beyond the first predetermined value, the movable valve is pushed in the opposite direction to the predetermined direction by the pressure of the refrigerant gas flowing therein, so that the pressure member is further increased. The movable valve moves to the second predetermined position by contraction, and the opening area of the suction passage is smaller than in the low and medium speed operation, and the amount of refrigerant gas flowing into the suction chamber is reduced. In other words, the opening area of the suction passage is maximized in the low and medium speed operation, and the opening area of the suction passage is smaller in the high speed operation than in the low and medium speed operation, so that the amount of the refrigerant gas flowing into the suction chamber becomes smaller. The cooling capacity of the compressor is suppressed, the power consumption is reduced, and the cooling capacity of the compressor is not suppressed at low and medium speed operation, so that a good cooling effect can be obtained throughout the entire period from low to medium speed operation to high speed operation. Moreover, since a structure is simple, manufacturing cost can be suppressed.

Preferably, the pressing member is composed of at least two springs each having a different spring constant.

According to this preferred aspect, the pressurizing member consists of at least two springs each having a different spring constant, so that the movable valve can be moved in stages in accordance with the first and second flow rates of the incoming refrigerant gas. Done.

That is, the at least two springs are formed of a first spring having a first spring constant contracted by the pressure of the refrigerant gas by the flow rate of the refrigerant gas at the first predetermined value, and the second predetermined value. It is preferable to have a 2nd spring constant larger than the said 1st spring constant contracted by the pressure of the said refrigerant gas by the said refrigerant gas flow volume.

According to this preferred aspect, when the refrigerant gas flow rate reaches a first predetermined value, only the first spring contracts, the movable valve moves, the suction port communicates with the suction chamber, and the refrigerant gas flow rate is increased. When the first predetermined value is exceeded and the second predetermined value is reached, the second spring also contracts and the movable valve moves to reduce the opening area of the suction passage, thereby reducing the amount of refrigerant gas flowing into the suction chamber. Less.

For example, the at least two springs are arranged in series.

Or the said at least 2 springs are arrange | positioned in parallel, and the spring with a smaller spring constant is longer than the spring with a larger spring constant.

Preferably, the suction passage comprises a suction valve accommodating chamber for communicating with the suction port and accommodating the movable valve, and a passage penetrating the suction valve accommodating chamber and the partition wall separating the suction chamber. When in the first position, the opening area of the opening of the passage is maximized, and the opening area of the opening is reduced when in the second position.

Preferably, the movable valve has a cylindrical shape having a circumferential wall in which a plurality of through holes are formed in the circumferential direction, and the area in which any one of the plurality of through holes communicates with the passage at the first position is maximized. As a result, an area in which any one of the plurality of through holes communicates with the passage at the second position is reduced.

Preferably, the stopper is fixed to the inlet port and includes a stopper having at least one hole as a stopper for restricting movement of the movable valve toward the inlet port. And the stopper is in contact with the stopper so that at least one hole of the stopper and at least one hole of the movable valve do not communicate with each other by the pressing member when the compressor is not in operation.

More preferably, the pressing member is disposed in the movable valve.

Preferably, the movable valve has a partition wall formed integrally with the circumferential wall to partition the movable valve into a suction valve portion and a bottom portion, and the plurality of through holes are formed on the suction valve side.

For example, the at least two springs are disposed in the bottom portion.

In that case, the at least two springs are preferably arranged in series through the intermediate member.

Or it is good that the said at least 2 springs are arrange | positioned in parallel, and the spring with a smaller spring constant is longer than the spring with a large spring constant.

Or the at least two springs are disposed in the suction valve side portion and the bottom portion.

The above and other objects, features and advantages of the present invention will become more apparent from the following detailed description of the embodiments based on the accompanying drawings.

(Example)

EMBODIMENT OF THE INVENTION Hereinafter, the Example of this invention is described based on drawing.

1 is a longitudinal sectional view showing a ben-type compressor having a suction valve device according to a first embodiment of the present invention, and FIG. 3 is a sectional view taken along line III-III of FIG.

The ben-type compressor has a cam ring (1), a front side block (3) and a rear side block (4) fixed to close both ends of the cam ring (1), and a rotor rotatably housed in the cam ring (1). (2), the front head 5 and the rear head (compressor housing) 6 fixed to the end surfaces of both side blocks 3 and 4, respectively, and the rotating shaft 7 of the rotor 2 are provided. . The rotating shaft 7 is rotatably supported by bearings 8 and 9 provided on both side blocks 3 and 4, respectively.

The discharge head 5a of the refrigerant gas is formed in the front head 5, and the suction port 6a of the refrigerant gas is formed in the rear head 6, respectively. The discharge port 5a communicates with the discharge chamber 10 formed by the front head 5 and the front side block 3, and the suction port 6a is formed by the rear head 6 and the rear side block 4. It is possible to communicate with the suction chamber 11 through the suction valve accommodating chamber 20 and the refrigerant suction passage 22.

The suction valve accommodation chamber 20 is formed between the suction port 6a and the suction chamber 11, and the suction chamber 11 and the suction valve accommodation chamber 20 are partitioned by the partition wall 21, and the partition wall ( The suction chamber 11 and the suction valve accommodation chamber 20 communicate with each other through the refrigerant suction passage 22 and the passage 23 provided in the 21. In the suction valve accommodation chamber 20, a suction valve device 30 to be described later is housed. The suction valve accommodation chamber 20 and the refrigerant suction passage 22 constitute a suction passage communicating the suction port and the suction chamber.

As shown in FIG. 3, two upper and lower compression spaces 12 are formed between the inner circumferential surface 1a of the cam ring 1 and the outer circumferential surface of the rotor 2 (one compression space in FIG. 1). (12) is only seen). A plurality of ben grooves 13 are provided in the rotor 2, and the ben 14 is inserted in the ben grooves 13 so as to be slidable. The compression space 12 is partitioned by the ben 14 to form a compression chamber, and the volume of the compression chamber changes with the rotation of the rotor 2.

In addition, two discharge ports 16 corresponding to the two compression spaces 12 are provided on the outer circumferential surface of the cam ring 1 (only one discharge port 16 is shown in FIG. 1). In addition, a discharge valve cover 17 having a valve fixing portion 17a is fixed to the outer circumferential surface of the cam ring 1 by bolts 18. A discharge valve 19 supported on the discharge valve cover 17 side is mounted between the outer circumferential surface of the cam ring 1 and the valve fixing portion 17a. When the discharge port 16 is opened, the compressed refrigerant gas in the compressor 12 is discharged through the discharge port 16, the communication paths 1b and 3a, the discharge chamber 10, and the discharge port 5a.

The rear side block 4 is provided with two upper and lower suction ports (not shown) corresponding to the two upper and lower compression spaces 12. The suction chamber 11 and the compression space 12 communicate with each other through the suction port.

2A to 2C are enlarged cross-sectional views for explaining the structure and operation of the intake valve device, wherein a is a state at the time of stopping the compressor, b is a state at low and medium speeds, and c is a state diagram at high speed.

The suction valve device 30 includes a movable valve 31 slidably accommodated in the suction valve accommodation chamber 20 and a pressure member for pressing the movable valve 31 upward (predetermined direction) of FIGS. 2A to 2C. (32) and an annular stopper (33) fixed to the suction port (6a) to regulate the upward movement of the movable valve (31).

The movable valve 31 is comprised from the upper cylinder part 31a, the lower cylinder part 31c, and the partition board part 31b which partitions both cylinder parts 31a and 31c up and down. A plurality of openings 34 are formed in the upper cylinder portion 31a in the circumferential direction. The suction valve accommodating chamber 20 is partitioned into two upper and lower spaces by the partition plate part 31b, and the upper space communicates with the suction port 6a, and the lower space communicates with the passage 23. As shown in FIG.

The pressing member 32 is accommodated in the lower cylinder part 31c. The pressing member 32 is connected in series to the coil spring (first spring) 35 and the coil spring (second spring) 36 through the intermediary member 37. Both springs 35 and 36 each have a unique spring constant. The spring constant of the coil spring 36 is larger than the spring constant of the coil spring 35.

Next, the operation of this ben-type compressor will be described.

When the rotational power of the engine (not shown) is transmitted to the rotation shaft 7, the rotor 2 rotates. When the flow rate of the refrigerant gas flowing out from the outlet from the ever-shower not shown exceeds a predetermined value, the movable valve 31 of the suction valve device 30 is pushed downward in FIGS. The movable valve 31 is lifted by contraction. When the movable valve 31 is lifted downward, the suction port 6a and the suction chamber 11 communicate with the suction valve accommodation chamber 20 through the refrigerant suction passage 22. As a result, the refrigerant gas enters the suction chamber 11 from the suction port 6a and is sucked from the suction chamber 11 into the compression space 12 through the suction port. The compression space 12 is partitioned by the ben 14, and the volume of each compression chamber changes with the rotation of the rotor 2, so that the refrigerant gas trapped between the ben 14 is compressed and compressed. The gas opens the discharge valve 19, flows out from the discharge port 16 to the discharge chamber 10 through the communication paths 1b and 3a, and is discharged from the discharge port 5a again.

Next, the operation of the suction valve device 30 will be described.

As shown in FIG. 2A when the compressor is stopped, the movable valve 31 is pushed upward in FIG. 2A by the pressing force of the pressing member 32 so that the upper cylinder portion 31a of the movable valve 31 is stopped. Pushed to the underside. At this time, the refrigerant suction passage 22 is closed by the lower cylinder portion 31c of the movable valve 31 so that the suction valve accommodating chamber 20 (which communicates with the suction port 6a) and the suction chamber 11 are not in communication. It is a state. In this way, since the suction valve device 30 functions as a check valve, the reverse rotation of the rotor 2 is prevented.

At the start of the operation of the compression chamber, if the flow rate of the refrigerant gas exceeds the first predetermined value, the movable valve 31 is pushed downward in FIG. 2A, so that only the coil spring 35 of the pressurizing member 32 contracts and the movable valve ( 31) is pushed down to the position in FIG. 2B. The first predetermined value is a value (nearly zero) of a very small flow rate of the refrigerant gas at the start of the compressor operation. Therefore, when the operation of the compressor is actually started, the movable valve 31 is opened immediately. When the movable valve 31 is lifted downward, the refrigerant suction passage 22 and the entire opening 34 of the movable valve 31 face each other, and the opening area of the refrigerant suction passage 22 becomes the maximum (suction opening ( The suction valve accommodating chamber 20 and the suction chamber 11 communicating with 6a) communicate with each other, and the refrigerant gas flows into the suction chamber 11.

Since the flow rate of the refrigerant gas is not large during low and medium speed operation, only the coil spring 35 contracts, and the coil spring 36 hardly deforms, and the state of FIG. 2B (the opening area of the refrigerant suction passage 22 is the largest). Status) is maintained. Therefore, the capability of the ben type compressor in low and medium speed operation is not suppressed.

When the flow rate of the refrigerant gas increases during the high speed operation and reaches the second predetermined value beyond the first predetermined value, the movable valve 31 is pushed downward in the state of FIG. 2B, as shown in FIG. 2C, The coil spring 36 of the pressing member 32 contracts, and the movable valve 31 is further lifted downward. When the movable valve 31 is lifted, the refrigerant suction passage 22 and the opening 34 of the movable valve 31 are shifted in the vertical direction, so that the opening area of the refrigerant suction passage 22 is reduced by almost half. The amount of refrigerant gas flowing into the suction chamber 11 from the suction port 6a is reduced. Therefore, the capacity of the ben-type compressor in high speed operation is suppressed, and power consumption is reduced.

In the case of changing from the high speed operation to the low medium speed operation and from the low medium speed operation to the stopped state, the operation state of the intake valve device 30 is reversed from that described above, that is, in the state of FIG. 2C. It changes to the state of 2b, and changes to the state of FIG. 2a from the state of FIG. 2b again.

According to the suction valve device of the ben-type compressor of the first embodiment, the opening area of the refrigerant suction passage 22 is variable, so that the cooling capacity of the compressor is suppressed only in high speed operation, so that the power consumption is reduced, and the compressor is operated at low and medium speed operation. Since the cooling capacity of is not suppressed, a good cooling effect can be obtained over the entire period from low to medium speed operation to high speed operation.

Further, the suction valve device of the first embodiment has the same structure as that of the conventional check valve, and since the structure is not complicated, the high performance ben-type compressor can be manufactured at low cost.

4 is a sectional view of a suction valve device of a second embodiment of the present invention. The same parts as those in the first embodiment described above are denoted by the same reference numerals and description thereof will be omitted.

In the above-described first embodiment, a case where the coil spring (first spring) 35 and the coil spring (second spring) 36 are connected in series through the intermediary member 37 as the pressing member 32 is used. Although described in the second embodiment, the coil spring (first spring) 135 having a large axial dimension and an outer diameter, without using the intermediate member 37 as the pressing member 132 as shown in FIG. 4, The coil spring 136 is disposed inside the coil spring 135 using only the coil spring (second spring) 136 having a smaller axial dimension and outer diameter than the coil spring 135.

Both springs 135 and 136 each have a unique spring constant, which is the same as the first embodiment in that the spring constant of the coil spring 136 is larger than the spring constant of the coil spring 135.

When the compressor is stopped, the upper cylinder portion 31a of the movable valve 31 is pushed to the lower surface of the stopper 33 by the pressing force of the coil spring 135, so that the refrigerant suction passage 22 is connected to the movable valve 31. Closed by the lower cylinder part 31c, the suction valve accommodation chamber 20 (in communication with the suction port 6a) and the suction chamber 11 are in a non-communication state.

At the start of the compressor, only the coil spring 135 contracts and the movable valve 31 is lifted downward, so that the refrigerant suction passage 22 and the entire opening 34 of the movable valve 31 face each other and the refrigerant suction passage ( The opening area of 22 is maximized, and the suction valve accommodating chamber 20 (which communicates with the suction port 6a) and the suction chamber 11 communicate with each other.

In the high speed operation, the coil spring 136 also contracts and the movable valve 31 is lifted further downward, whereby the refrigerant suction passage 22 and the opening 34 of the movable valve 31 are displaced, and the refrigerant suction passage 22 Since the opening area of decreases in about half, the amount of refrigerant gas flowing into the suction chamber 11 is reduced.

According to the intake valve device of the ben-type compressor of the second embodiment, the same effects as in the first embodiment can be obtained.

5A and 5B are explanatory views of a suction valve device according to a third embodiment of the present invention, where a is a sectional view of the suction valve device and b is a plan view of the stopper. The same parts as those in the above-described embodiment are denoted by the same reference numerals and description thereof will be omitted.

In this third embodiment, the suction valve device 230 includes a bottomed cylindrical movable valve 231 which is slidably accommodated in the suction valve accommodating chamber 20, and the movable valve 231 at the top of FIG. Sliding to the inner circumferential surface of the movable member 232 and the stopper 233 fixed to the suction port 6a to restrict the upward movement of the movable valve 231, and the movable valve 231. And a movable member 50 which partitions the inside in a vertical direction.

The pressing member 232 connects the coil spring (first spring) 235 and the coil spring (second spring) 236 in series through the movable member 50.

Both springs 235 and 236 each have a unique spring constant, and the spring constant of the coil spring 236 is larger than the spring constant of the coil spring 235.

The role of the coil spring 235 is the same as the coil springs 35 and 135 of the first and second embodiments, and the role of the coil spring 236 is the same as the coil springs 36 and 136 of the first and second embodiments.

A plurality of openings 234 are formed in the outer circumferential surface of the movable valve 231 along the circumferential direction, and a round hole 238 is formed in the center of the bottom surface of the movable valve 231.

The stopper 233 is formed with a plurality of openings 233a along the circumferential direction.

When the movable valve 231 lifts downward, the refrigerant gas flows from the plurality of openings 233a of the stopper 233 to the round hole 238 of the movable valve 231, the inside of the movable valve 231, and the movable valve 231. The suction chamber 11 is sucked into the suction chamber 11 through the opening 234.

According to the suction valve device of the ben-type compressor of the third embodiment, the same effects as those of the first embodiment can be obtained, and the sheet area of the movable valve 231 and the stopper 233 is increased, so that the sealing property is improved.

In each of the above embodiments, the case where two springs (coil springs 35, 36, etc.) are used as the pressing member has been described, but three or more springs may be used, and one spring (for example, a nonlinear spring). You may use only.

The two or more springs may be arranged in series or in parallel as in the embodiment of Figs. 1 and 5. In the case of parallel arrangement, one spring may be accommodated in the other spring as in the embodiment of FIG. In parallel arrangements, lengthen the spring with the smaller spring constant and shorten the spring with the larger spring constant. The parallel arrangement makes it easier to share the function or set the operation of each spring than the serial arrangement.

The above is a preferable aspect of this invention, and it will be clear for those skilled in the art for various changes to be possible, without leaving | separating the mind and range of this invention.

According to the intake valve device of the ben-type compressor of the present invention, the opening area of the refrigerant suction passage is variable, so that the cooling capacity of the compressor is suppressed only at high speed, the consumption power is reduced, and the cooling capacity of the compressor is suppressed at low and medium speed operation. Therefore, not only can a good cooling effect be obtained throughout the entire period from low to medium speed operation to high speed operation, but also the structure is not complicated, so that a high performance ben-type compressor can be manufactured at low cost.

Claims (18)

A suction device of a compressor having a housing, a suction port formed in the housing, a suction chamber formed in the housing, and a suction passage communicating the suction port and the suction chamber, A movable valve disposed in the suction passage and moving in accordance with a change in the flow rate of the refrigerant gas flowing into the suction passage from the suction passage to change the opening area of the suction passage; A pressurizing member for pressurizing the movable valve in a predetermined valve opening position. When the refrigerant gas flow rate reaches a first predetermined value, the movable valve contracts by the pressure of the refrigerant gas and moves the movable valve to the first position. When the opening area of the suction passage is increased, and the flow rate of the refrigerant gas exceeds the first predetermined value and reaches the second predetermined value, the suction valve is further contracted by the pressure of the larger refrigerant gas, and the movable valve is moved to the second position. A suction valve device of a refrigerant compressor, characterized in that the pressure member is made to move up to a small opening area of the suction passage. The intake valve device according to claim 1, wherein the pressing member comprises at least two springs each having a different spring constant. The said at least two spring is a 1st spring which has a 1st spring constant which contracts by the pressure of the said refrigerant gas by the said refrigerant gas flow volume of a said 1st predetermined value, and said 2nd predetermined And a second spring having a second spring constant greater than an integer of the first spring contracted by the pressure of the refrigerant gas due to the flow rate of the refrigerant gas. The intake valve device according to claim 2, wherein the at least two springs are arranged in series. The intake valve device according to claim 2, wherein the at least two springs are arranged in parallel, and the smaller spring of the spring constant is longer than the larger spring of the spring constant. The suction valve of claim 1, wherein the suction passage communicates with the suction port and includes a suction valve accommodating chamber accommodating the movable valve, and a passage penetrating the suction valve accommodating chamber and the partition wall separating the suction chamber. And the opening area of the opening of the passage is maximized when in the first position, and the opening area of the opening is reduced when in the second position. The suction valve device according to claim 2, wherein the suction valve device is the same as that of Claim 6. 7. The movable valve of claim 6, wherein the movable valve has a cylindrical shape having a circumferential wall having a plurality of through holes formed in the circumferential direction, and an area in which the one of the plurality of through holes communicates with the passage at the first position is maximum. And an area in which any one of the plurality of through holes and the passage communicates at the second position is reduced. The suction valve device according to claim 7, wherein the suction valve device is the same as that of claim 8. The stopper of claim 8, which is fixed to the inlet port and regulates movement of the movable valve toward the inlet port, the stopper having at least one hole, wherein the movable valve has at least one hole formed at an inlet side thereof, And the stopper is brought into contact with the stopper so that at least one hole of the stopper and at least one hole of the movable valve do not communicate with each other by the pressing member when the compressor is not in operation. The suction valve device according to claim 9, wherein the suction valve device is the same as that of claim 10. The suction valve device according to claim 8, wherein the pressure member is disposed in the movable valve. The suction valve device according to claim 9, wherein the suction valve device is the same as that of claim 12. The method of claim 13, wherein the movable valve is formed integrally with the circumferential wall has a partition wall partitioning the movable valve to the suction valve side portion and the bottom portion, characterized in that the plurality of through holes are formed in the suction valve side. Suction valve device. The intake valve device according to claim 14, wherein the at least two springs are disposed in the bottom portion. 16. The suction valve device according to claim 15, wherein the at least two springs are arranged in series through an intermediate member. 16. The intake valve device according to claim 15, wherein the at least two springs are arranged in parallel, and the smaller spring of the spring constant is longer than the larger spring of the spring constant. 15. The suction valve device according to claim 14, wherein the at least two springs are disposed in the suction valve side portion and the bottom portion.