JP7088113B2 - Piston compressor - Google Patents

Description

The present invention relates to a piston type compressor.

Patent Document 1 discloses a conventional piston type compressor (hereinafter, simply referred to as a compressor). The compressor includes a housing, a drive shaft, a fixed swash plate, a plurality of pistons, a discharge valve, a moving body, and a control valve.

The housing has a cylinder block. In the cylinder block, a plurality of cylinder bores are formed, and a first communication passage communicating with the compression chamber is formed. Further, the housing is formed with a discharge chamber, a swash plate chamber, a shaft hole, and a control pressure chamber. Refrigerant with suction pressure is sucked into the swash plate chamber from the outside of the compressor. As a result, the swash plate chamber has a suction pressure atmosphere, and the pressure is lower than that of the discharge chamber. In addition, the swash plate chamber communicates with the shaft hole. The control pressure chamber is the control pressure.

The drive shaft is rotatably supported in the shaft hole. The fixed swash plate can be rotated in the swash plate chamber by the rotation of the drive shaft, and the inclination angle with respect to the plane perpendicular to the drive shaft is constant. The piston forms a compression chamber in the cylinder bore and is connected to a fixed swash plate. A reed valve type discharge valve for discharging the refrigerant in the compression chamber to the discharge chamber is provided between the compression chamber and the discharge chamber.

The moving body has a drive shaft inserted through it. As a result, the moving body is provided on the drive shaft and is arranged in the shaft hole. The moving body separates the shaft hole and the control pressure chamber. The moving body rotates integrally with the drive shaft in the shaft hole, and can move with respect to the drive shaft in the direction of the drive axis center of the drive shaft based on the control pressure. Further, a second continuous passage is formed on the outer peripheral surface of the moving body. The second communication passage extends in the circumferential direction of the moving body, and intermittently communicates with the first communication passage as the drive shaft rotates. The control valve regulates the control pressure.

In this compressor, the drive shaft rotates and the fixed swash plate rotates, so that the piston reciprocates in the cylinder bore between top dead center and bottom dead center. Here, when the piston at the top dead center starts to move toward the bottom dead center, the compression chamber becomes a re-expansion stroke in which the refrigerant remaining inside re-expands. Then, by communicating the first communication passage and the second communication passage, the compression chamber shifts from the re-expansion stroke to the suction stroke. At this time, in the second passage, the refrigerant in the shaft hole, that is, in the swash plate chamber is sucked into the compression chamber through the first passage. Then, the compression chamber becomes a compression stroke for compressing the sucked refrigerant while the piston moves from the top dead center to the bottom dead center, and further shifts to a discharge stroke for discharging the compressed refrigerant to the discharge chamber.

Then, in this compressor, the communication angle around the drive shaft center in which the first communication passage and the second communication passage communicate with each other per rotation of the drive shaft according to the position in the drive axis direction of the moving body with respect to the drive shaft. Changes. As a result, in this compressor, it is possible to change the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber by changing the flow rate of the refrigerant sucked into the compression chamber.

Japanese Unexamined Patent Publication No. 5-306680

By the way, when the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber is maximum (hereinafter referred to as the maximum flow rate), the refrigerant discharged from the compression chamber to the discharge chamber becomes high pressure and remains in the compression chamber. The refrigerant used is also high pressure. Therefore, if the first communication passage and the second communication passage communicate with each other before the refrigerant remaining in the compression chamber becomes lower than the suction pressure atmosphere due to the re-expansion stroke, the refrigerant remaining in the compression chamber becomes the first. It flows back from the communication passage to the second communication passage and eventually to the suction pressure atmosphere side.

Here, the piston that moves from the top dead center side to the bottom dead center side when the compressor operates utilizes the pressure in the compression chamber as a part of the power. Therefore, when the refrigerant remaining in the compression chamber flows back into the second passage and the compression chamber is rapidly depressurized, it becomes difficult for the piston to move from the top dead center side to the bottom dead center side. Therefore, in order to move the piston, it is necessary to increase the rotational driving force of the drive shaft. Further, since the refrigerant remaining in the compression chamber flows back to the suction pressure atmosphere side, the pressure fluctuation on the suction pressure atmosphere side becomes large, so that the suction pulsation also becomes large.

The present invention has been made in view of the above-mentioned conventional circumstances, and has solved the present invention to provide a piston type compressor capable of suppressing an increase in the rotational driving force of a drive shaft during operation and suppressing suction pulsation. It is an issue that should be done.

The piston type compressor of the present invention has a cylinder block in which a plurality of cylinder bores are formed, and has a discharge chamber, a swash plate chamber, and a housing in which a shaft hole is formed.
A drive shaft rotatably supported in the shaft hole and
A fixed swash plate that can be rotated in the swash plate chamber by rotation of the drive shaft and has a constant inclination angle with respect to a plane perpendicular to the drive shaft.
A piston that forms a compression chamber in the cylinder bore and is connected to the fixed swash plate,
A discharge valve that discharges the refrigerant in the compression chamber to the discharge chamber,
A moving body provided on the drive shaft, located in the shaft hole, rotated integrally with the drive shaft, and movable with respect to the drive shaft in the direction of the drive shaft center based on the control pressure.
A control valve for controlling the control pressure is provided.
The cylinder block is formed with a first communication passage that communicates with the compression chamber.
The moving body extends in the circumferential direction of the moving body and intermittently communicates with the first communication passage as the drive shaft rotates, so that the refrigerant is sucked into the compression chamber through the first communication passage. The second passage is formed,
A piston type compressor in which the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber changes according to the position of the moving body in the drive axis direction.
The second passage has a tip edge located on the leading side in the rotational direction of the moving body and a trailing edge edge located on the trailing side in the rotational direction with respect to the tip edge.
The tip edge is discharged from the compression chamber to the discharge chamber and a first edge portion facing the first continuous passage when the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber is maximum. It has a second edge facing the first passage when the flow rate of the refrigerant is less than the maximum.
The first edge portion is characterized in that it is located on the trailing side in the rotation direction with respect to the second edge portion.

In the piston type compressor of the present invention, the tip edge of the second connecting passage has a first edge portion and a second edge portion, and the first edge portion is in the rotation direction of the drive shaft rather than the second edge portion. It is located on the trailing side. Therefore, at the maximum flow rate, the timing at which the first passage and the second passage communicate with each other is delayed as compared with the case where the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber is smaller than that at the maximum flow rate. Therefore, the timing at which the compression chamber shifts from the re-expansion stroke to the suction stroke is delayed.

Therefore, in this compressor, the refrigerant remaining in the compression chamber at the maximum flow rate can be sufficiently depressurized in the re-expansion stroke, so that the refrigerant remaining in the compression chamber when the first passage and the second passage communicate with each other. Can be suppressed from flowing back into the second passage. As a result, even if the first communication passage and the second communication passage communicate with each other, the pressure in the compression chamber does not easily drop sharply, so that the piston easily moves at the maximum flow rate and the increase in the rotational driving force of the drive shaft is suppressed. can. Further, since the refrigerant remaining in the compression chamber is suppressed from flowing back into the second passage, the suction pulsation at the maximum flow rate can be suppressed.

Then, in this compressor, when the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber is smaller than that at the maximum flow rate, the timing at which the first passage and the second passage communicate with each other is higher than at the maximum flow rate. By accelerating, the timing at which the compression chamber shifts from the re-expansion stroke to the suction stroke becomes earlier.

Therefore, in this compressor, when the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber is smaller than that at the maximum flow rate, it is possible to prevent the compression chamber from becoming lower than the suction pressure due to the re-expansion stroke. As a result, even when the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber is smaller than that at the maximum flow rate, the piston can easily move and an increase in the rotational driving force of the drive shaft can be suppressed. Further, by preventing the pressure inside the compression chamber from becoming lower than the suction pressure, the compressor can suppress the suction pulsation when the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber is smaller than that at the maximum flow rate. ..

Therefore, according to the piston type compressor of the present invention, it is possible to suppress an increase in the rotational driving force of the drive shaft during operation and also to suppress suction pulsation.

The drive shaft may be formed with a guide window for movably arranging the moving body in the direction of the drive axis. Further, the moving body may have a first moving body arranged in the guide window and a second moving body arranged in the moving axis while forming the second continuous passage. Further, the first moving body can communicate the first communication passage and the second communication passage. Then, it is preferable that the first communication passage and the second communication passage are not communicated with each other by the drive shaft.

In this compressor, the high-pressure refrigerant compressed in the compression stroke flows toward the second passage through the first communication passage communicating with the compression chamber in the compression stroke and the discharge stroke. Here, in this compressor, since the first-passage and the second-passage are not communicated by the drive shaft, the load due to the high-pressure refrigerant compressed in the compression chamber (hereinafter referred to as the compression load) is. It acts on the drive shaft through the first passage. As a result, the drive shaft receives the compressive load, so that the compressive load is unlikely to act on the moving body. Therefore, since the moving body easily moves in the direction of the drive axis, the controllability can be improved with this compressor. Further, in this compressor, when moving the moving body in the direction of the drive axis, an excessively large thrust is not required, and it is not necessary to increase the size of the moving body to secure a large pressure receiving area for the control pressure. Therefore, this compressor can be miniaturized.

It is preferable that the first edge portion and the second edge portion are continuous while gradually changing in the rotation direction. Further, it is also preferable that the first edge portion and the second edge portion have a step and are continuous. In these cases, while increasing the degree of freedom in designing the second passage, including the tip edge, the communication timing between the first and second passages at the maximum flow rate and compression compared to the maximum flow rate. It is possible to suitably set the communication timing between the first communication passage and the second communication passage when the flow rate of the refrigerant discharged from the chamber to the discharge chamber is small.

According to the piston type compressor of the present invention, it is possible to suppress an increase in the rotational driving force of the drive shaft during operation and also to suppress suction pulsation.

FIG. 1 is a cross-sectional view of the piston type compressor of the first embodiment at the minimum flow rate. FIG. 2 is a cross-sectional view of the piston type compressor of the first embodiment at the maximum flow rate. FIG. 3 is an exploded view showing a drive shaft, a moving body, and the like according to the piston type compressor of the first embodiment. FIG. 4 is a cross-sectional view showing a cap of the piston type compressor of the first embodiment. FIG. 5 is an enlarged cross-sectional view showing a CC cross section of FIG. 4 relating to the piston type compressor of the first embodiment. FIG. 6 is an enlarged front view of the first moving body as viewed from the front side of the compressor according to the piston type compressor of the first embodiment. FIG. 7 is an enlarged rear view of the second moving body as viewed from the rear side of the compressor according to the piston type compressor of the first embodiment. FIG. 8 is an enlarged cross-sectional view of a main part of the piston type compressor of the first embodiment, showing a drive shaft, a moving body, and the like at the minimum flow rate. FIG. 9 is an enlarged cross-sectional view of a main part of the piston type compressor of the first embodiment, showing a drive shaft, a moving body, and the like at the maximum flow rate. FIG. 10 is an enlarged cross-sectional view of a main part showing a cross section taken along the line AA of FIG. 1 according to the piston type compressor of the first embodiment. FIG. 11 is an enlarged cross-sectional view of a main part similar to FIG. 10, showing a state in which the moving body is moved backward from the position shown in FIG. 1 with respect to the piston type compressor of the first embodiment. FIG. 12 is an enlarged cross-sectional view of a main part showing the BB cross section of FIG. 2, relating to the piston type compressor of the first embodiment. FIG. 13 is a schematic diagram showing the positional relationship between the first moving body and the first continuous passage at the time of the minimum flow rate according to the piston type compressor of the first embodiment. FIG. 14 is a schematic diagram showing the positional relationship between the first moving body and the first continuous passage at the time of an intermediate flow rate, relating to the piston type compressor of the first embodiment. FIG. 15 is a schematic diagram showing the positional relationship between the first moving body and the first continuous passage at the maximum flow rate, relating to the piston type compressor of the first embodiment. FIG. 16 is a side view showing the first moving body according to the piston type compressor of the second embodiment. FIG. 17 is a side view showing the first moving body according to the piston type compressor of the third embodiment. FIG. 18 is a side view showing the first moving body of the piston type compressor of the fourth embodiment. FIG. 19 is an enlarged cross-sectional view of a main part showing a DD cross section of FIG. 18 related to the piston type compressor of the fourth embodiment. FIG. 20 is a side view showing the first moving body according to the piston type compressor of the fifth embodiment.

Hereinafter, Examples 1 to 5 embodying the present invention will be described with reference to the drawings. These compressors are single-headed piston compressors. These compressors are mounted on the vehicle and constitute a refrigerating circuit of an air conditioner.

(Example 1)
As shown in FIGS. 1 and 2, the compressor of the first embodiment includes a housing 1, a drive shaft 3, a fixed swash plate 5, a plurality of pistons 7, a valve forming plate 9, a moving body 10, and a moving body 10. It is provided with a control valve 13. The valve forming plate 9 is an example of the "discharge valve" of the present invention.

The housing 1 has a front housing 17, a rear housing 19, and a cylinder block 21. In this embodiment, the side where the front housing 17 is located is the front side of the compressor, and the side where the rear housing 19 is located is the rear side of the compressor, and the front-rear direction of the compressor is defined. Further, the upper part of the paper surface of FIGS. 1 and 2 is the upper side of the compressor, and the lower part of the paper surface is the lower side of the compressor, which defines the vertical direction of the compressor. Then, in FIGS. 3 and 3, the front-back direction and the up-down direction are displayed corresponding to FIGS. 1 and 2. The front-rear direction and the like in the embodiment are examples, and the posture of the compressor of the present invention is appropriately changed according to the vehicle on which the compressor is mounted.

The front housing 17 has a front wall 17a extending in the radial direction and a peripheral wall 17b integrally with the front wall 17a and extending rearward from the front wall 17a in the drive axis O direction of the drive shaft 3. It has a cylindrical shape. The drive axis O extends parallel to the front-rear direction of the compressor.

The front wall 17a is formed with a first boss portion 171, a second boss portion 172, and a first shaft hole 173. The first boss portion 171 projects forward in the drive axis O direction. A shaft sealing device 25 is provided in the first boss portion 171. The second boss portion 172 projects rearward in the drive axis O direction in the swash plate chamber 31, which will be described later. The first shaft hole 173 penetrates the front wall 17a in the drive shaft center O direction.

The rear housing 19 is formed with a suction chamber 28, a suction port 28a, a discharge chamber 29, a discharge port 29a, and a third connection path 26c. The suction chamber 28 is located on the center side of the rear housing 19. The suction port 28a communicates with the suction chamber 28 and extends in the axial direction of the rear housing 19 and opens to the outside of the rear housing 19. The suction port 28a is connected to the evaporator via a pipe. As a result, the suction chamber 28 sucks the low-pressure refrigerant gas that has passed through the evaporator, that is, the refrigerant gas having the suction pressure from the suction port 28a. In this way, the suction chamber 28 has a suction pressure. The discharge chamber 29 is formed in an annular shape and is located on the outer peripheral side of the suction chamber 28. The discharge port 29a communicates with the discharge chamber 29, extends in the radial direction of the rear housing 19, and opens to the outside of the rear housing 19. The discharge port 29a is connected to the condenser via a pipe. The shapes of the suction port 28a and the discharge port 29a can be appropriately designed. The piping, evaporator and condenser are not shown. The third connection path 26c is connected to the suction chamber 28 at a position different from that of the suction port 28a.

The cylinder block 21 is located between the front housing 17 and the rear housing 19. As shown in FIGS. 10 to 12, the cylinder blocks 21 are formed with cylinder bores 21a to 21f. The cylinder bores 21a to 21f are arranged at equal angular intervals in the circumferential direction. As shown in FIGS. 1 and 2, the cylinder bores 21a to 21f extend in the drive axis O direction, respectively. The number of cylinder bores 21a to 21f can be appropriately designed.

The cylinder block 21 is joined to the front housing 17 to form a swash plate chamber 31 between the front wall 17a and the peripheral wall 17b of the front housing 17. The swash plate chamber 31 communicates with the suction chamber 28 by a communication passage (not shown).

Further, a second shaft hole 23 is formed in the cylinder block 21. The first shaft hole 173 and the second shaft hole 23 are examples of the "shaft hole" of the present invention. The second shaft hole 23 is located on the center side of the cylinder block 21 and penetrates the cylinder block 21 in the drive axis O direction. The rear side of the second shaft hole 23 is located in the suction chamber 28 by joining the cylinder block 21 to the rear housing 19 via the valve forming plate 9. As a result, the second shaft hole 23 communicates with the suction chamber 28.

On the other hand, an annular groove 24 is formed on the front side of the second shaft hole 23. The annular groove 24 is recessed in the second shaft hole 23 in an annular shape and faces the inner peripheral surface of the second shaft hole 23. The annular groove 24 is connected to the first connecting path 26a and is also connected to the second connecting path 26b at a position different from that of the first connecting path 26a. The first and second connection paths 26a and 26b are formed in the cylinder block 21 and the rear housing 19. Further, the first connection path 26a is connected to the discharge chamber 29 on the opposite side of the annular groove 24. As a result, the first connection path 26a communicates the annular groove 24 with the discharge chamber 29.

Further, as shown in FIGS. 10 to 12, the cylinder block 21 is formed with the first continuous passages 22a to 22f. The first continuous passages 22a to 22f are located between the cylinder bores 21a to 21f and the second shaft hole 23. The first continuous passages 22a to 22f connect the cylinder bores 21a to 21f and the second shaft hole 23, respectively.

As shown in FIGS. 1 and 2, the valve forming plate 9 is provided between the rear housing 19 and the cylinder block 21. The rear housing 19 and the cylinder block 21 are joined via the valve forming plate 9.

The valve forming plate 9 has a valve plate 90, a discharge valve plate 92, and a retainer plate 93. The valve plate 90 is formed with six discharge holes 911 communicating with the cylinder bores 21a to 21f. The cylinder bores 21a to 21f communicate with the discharge chamber 29 through the discharge holes 911.

The discharge valve plate 92 is provided on the rear surface of the valve plate 90. The discharge valve plate 92 is provided with six discharge reed valves 92a that can open and close each discharge hole 911 by elastic deformation. The retainer plate 93 is provided on the rear surface of the discharge valve plate 92. The retainer plate 93 regulates the maximum opening degree of the discharge lead valve 92a.

The drive shaft 3 is composed of a drive shaft main body 33 and a cap 35, and extends from the front side to the rear side of the housing 1 in the drive shaft center O direction. The drive shaft main body 33 and the cap 35 are made of steel and have rigidity against the compressive load of the high-pressure refrigerant gas. The drive shaft main body 33 constitutes a front portion of the drive shaft 3. The drive shaft main body 33 has a screw portion 33a, a first shaft portion 33b, and a second shaft portion 33c. The threaded portion 33a is located at the front end of the drive shaft main body 33, that is, at the front end of the drive shaft 3. The drive shaft 3 is connected to a pulley, an electromagnetic clutch, or the like (not shown) via the screw portion 33a. In this way, the drive shaft 3 obtains a rotational driving force from the vehicle.

The first shaft portion 33b is continuous with the rear end of the screw portion 33a and extends in the drive axis O direction. The second shaft portion 33c is continuous with the rear end of the first shaft portion 33b and extends in the drive axis O direction. The second shaft portion 33c is formed to have a smaller diameter than the first shaft portion 33b. As shown in FIG. 3, a first axle path 33d is formed in the second shaft portion 33c. The first axle path 33d extends in the second shaft portion 33c in the drive axis O direction, and is open to the rear end surface of the second shaft portion 33c, that is, the rear end surface of the drive shaft main body 33. Further, a first route 33e is formed on the second shaft portion 33c. As shown in FIGS. 9 and 10, the first route 33e extends in the radial direction of the drive shaft 3 in the second shaft portion 33c while communicating with the first axis 33d, and the second shaft portion 33c. It is open to the outer peripheral surface.

As shown in FIGS. 1 and 2, the cap 35 constitutes a rear portion of the drive shaft 3. As shown in FIGS. 1 to 5, the cap 35 has a cylindrical shape having substantially the same diameter as the second shaft hole 23, and extends in the drive shaft center O direction. As shown in FIGS. 4 and 5, a guide window 35a is formed on the cap 35. As shown in FIG. 5, the guide window 35a is formed with the cap 35 extending around half a circumference in the circumferential direction, and extends in the drive axis O direction. On the other hand, in the cap 35, the portion located on the opposite side of the guide window 35a across the drive shaft center O is the main body portion 35b. The main body portion 35b has a semi-circular gutter shape extending in the drive axis O direction facing the guide window 35a. The guide window 35a may be formed larger than half a circumference in the circumferential direction of the cap 35, or may be formed smaller than half a circumference in the circumferential direction of the cap 35.

As shown in FIG. 4, a second axis path 35c is formed in the cap 35. The second axis 35c extends in the drive axis O direction and penetrates the cap 35 back and forth. The second axis 35c is composed of a first diameter portion 351, a second diameter portion 352, and a third diameter portion 353. The first diameter portion 351 and the second diameter portion 352 and the third diameter portion 353 are coaxial with each other.

The first diameter portion 351 is formed to have substantially the same diameter as the second shaft portion 33c of the drive shaft main body 33. The first diameter portion 351 is open to the front end surface of the cap 35 and extends rearward. The second diameter portion 352 is connected to the rear end of the first diameter portion 351 and extends rearward. The second diameter portion 352 has substantially the same diameter as the first axis path 33d shown in FIG. 3, and is formed to have a smaller diameter than the first diameter portion 351. As a result, the first step portion 354 shown in FIG. 4 is formed between the first diameter portion 351 and the second diameter portion 352. Further, the first diameter portion 351 and the second diameter portion 352 communicate with the guide window 35a. As a result, the first and second diameter portions 351 and 352 communicate with the outside of the cap 35 at the portion communicating with the guide window 35a. The third diameter portion 353 is connected to the rear end of the second diameter portion 352 and extends rearward, and is open to the rear end surface of the cap 35. The third diameter portion 353 is formed to have a smaller diameter than the second diameter portion 352. As a result, a second step portion 355 is formed between the second diameter portion 352 and the third diameter portion 353.

Further, a first annular concave groove 356 and a second annular concave groove 357 are formed on the front end side of the cap 35. The first annular groove 356 is provided with a first seal ring 358, and the second annular groove 357 is provided with a second seal ring 359. The first and second seal rings 358 and 359 are made of a resin such as PTFE. Further, on the front end side of the cap 35, a second position is located between the first annular groove 356 and the second annular groove 357, that is, between the first seal ring 358 and the second seal ring 359. A route 35d is formed. The second route 35d extends in the cap 35 in the radial direction while communicating with the first diameter portion 351 and opens to the outer peripheral surface of the cap 35.

Further, as shown in FIGS. 3 to 5, the cap 35 has a first regulation surface 301, a second regulation surface 302, a first end surface 303, and a second end surface 304. As shown in FIG. 4, the first regulation surface 301 extends in a plane from the inner peripheral side of the cap 35 toward the outer peripheral side, and faces the guide window 35a backward. The second regulation surface 302 extends in a plane from the inner peripheral side to the outer peripheral side of the cap 35 while facing the first regulation surface 301, and faces the guide window 35a forward. As shown in FIG. 3, the first end surface 303 and the second end surface 304 are located in the guide window 35a, that is, between the first regulation surface 301 and the second regulation surface 302. The first end surface 303 and the second end surface 304 are arranged so as to sandwich the drive axis O, and extend in a plane in the drive axis O direction in parallel with each other. As a result, the first end surface 303 and the second end surface 304 are connected to the first regulation surface 301 and the second regulation surface 302, respectively. The first end surface 303 and the second end surface 304 constitute an end surface of the main body portion 35b.

As shown in FIGS. 8 and 9, the second shaft portion 33c of the drive shaft main body 33 is press-fitted into the cap 35. More specifically, the rear end side of the second shaft portion 33c is press-fitted into the first diameter portion 351 of the second shaft path 35c. Then, the rear end of the second shaft portion 33c comes into contact with the first stage portion 354, so that the second shaft portion 33c is positioned within the first diameter portion 351. At this time, the first route 33e and the second route 35d are aligned so that they communicate with each other. In this way, the drive shaft 3 is formed by integrating the drive shaft main body 33 and the cap 35.

As shown in FIGS. 1 and 2, in the drive shaft 3, the first shaft portion 33b of the drive shaft main body 33 is supported by the first shaft hole 173, and the cap 35 is supported by the second shaft hole 23. It is rotatably inserted into the housing 1. As a result, the drive shaft 3 can rotate around the drive shaft center O. Specifically, the drive shaft 3 rotates in the R1 direction shown in FIGS. 10 to 12 and the like.

Here, by supporting the cap 35 in the second shaft hole 23, as shown in FIGS. 8 and 9, the annular groove 24 and the second path 35d and the first path 33e face each other. As a result, the annular groove 24 and the first axial path 33d communicate with each other through the first and second path 33e and 35d. Then, the inside of the second shaft hole 23 and the annular groove 24 are sealed by the first and second seal rings 358 and 359. Further, when the cap 35 is supported by the second shaft hole 23, the rear end of the cap 35 is in a state of extending into the suction chamber 28 while protruding from the inside of the second shaft hole 23. As a result, the second axis 35c is connected to the suction chamber 28 through the third diameter portion 353. On the other hand, as shown in FIGS. 1 and 2, the drive shaft 3 is inserted into the shaft sealing device 25 in the first boss portion 171. As a result, the shaft sealing device 25 seals between the inside of the housing 1 and the outside of the housing 1.

Further, since the cap 35 is supported by the second shaft hole 23, the guide window 35a and the main body portion 35b face the first continuous passages 22a to 22f as shown in FIGS. 10 to 12. Specifically, the guide window 35a faces the first communication passages 22a to 22f communicating with the compression chambers 45a to 45f in the re-expansion stroke or the suction stroke among the first communication passages 22a to 22f. On the other hand, the main body portion 35b faces the first communication passages 22a to 22f communicating with the compression chambers 45a to 45f in the compression stroke or the discharge stroke among the first communication passages 22a to 22f. The compression chambers 45a to 45f will be described later.

As shown in FIGS. 1 and 2, the fixed swash plate 5 is fixed to the drive shaft main body 33 by being press-fitted into the second shaft portion 33c of the drive shaft main body 33. At this time, the fixed swash plate 5 is positioned with respect to the drive shaft main body 33 by abutting on the step portion 33f formed between the second shaft portion 33c and the first shaft portion 33b. In this way, the fixed swash plate 5 is arranged in the swash plate chamber 31, and by rotating the drive shaft 3, the fixed swash plate 5 can rotate together with the drive shaft 3 in the swash plate chamber 31. Here, the fixed swash plate 5 has a constant inclination angle with respect to a plane perpendicular to the drive shaft 3. Further, in the swash plate chamber 31, a thrust bearing 6 is provided between the second boss portion 172 and the fixed swash plate 5.

Each piston 7 is housed in the cylinder bores 21a to 21f. As shown in FIGS. 10 to 12, compression chambers 45a to 45f are formed in the cylinder bores 21a to 21f by the piston 7 and the valve forming plate 9, respectively. The compression chambers 45a to 45f communicate with the first communication passages 22a to 22f, respectively.

As shown in FIGS. 1 and 2, an engaging portion 7a is formed on each piston 7. Hemispherical shoes 8a and 8b are provided in the engaging portion 7a, respectively. The piston 7 is connected to the fixed swash plate 5 by these shoes 8a and 8b. As a result, the shoes 8a and 8b function as a conversion mechanism that converts the rotation of the fixed swash plate 5 into the reciprocating motion of the piston 7. Therefore, the piston 7 can reciprocate in the cylinder bores 21a to 21f between the top dead center of the piston 7 and the bottom dead center of the piston 7, respectively.

As shown in FIG. 3, the moving body 10 is composed of a first moving body 11 and a second moving body 12. As shown in FIGS. 10 to 12, the moving body 10 rotates around the drive shaft center O together with the drive shaft 3 by being attached to the drive shaft 3. As a result, the first moving body 11 is defined to have a leading side in the rotation direction and a trailing side in the rotation direction with the drive axis O interposed therebetween. The attachment of the moving body 10 to the drive shaft 3 will be described later.

As shown in FIGS. 6 and 10 to 12, the first moving body 11 has a peripheral wall portion 11a and a vertical wall portion 11b. The peripheral wall portion 11a is formed in a substantially semicircular gutter shape having substantially the same diameter as the cap 35, and extends in the drive axis O direction. As shown in FIGS. 8 and 9, the length in the drive axis O direction of the first moving body 11, that is, the length in the front-rear direction of the first moving body 11, is compared with the length in the front-rear direction in the guide window 35a. Is set short.

As shown in FIG. 6, the peripheral wall portion 11a has a front surface 111 and a back surface 112. A second continuous passage 41 is formed in the peripheral wall portion 11a. The second passage 41 is formed by a hole 41a penetrating from the front surface 111 to the back surface 112. As shown in FIGS. 13 to 15, the second continuous passage 41 is formed in the peripheral wall portion 11a so as to extend in the front-rear direction. The second passage 41 is formed so as to gradually extend from the rear end to the front end in the circumferential direction of the peripheral wall portion 11a, that is, from the leading side to the trailing side in the rotational direction of the first moving body 11. Has been done. That is, the first portion 411 formed small in the rotation direction of the first moving body 11 is located on the rear end side of the second continuous passage 41, and is formed large in the rotation direction of the first moving body 11. The portion 412 is located on the front end side of the second passage 41.

By forming the second continuous passage 41 on the peripheral wall portion 11a in such a shape, the second continuous passage 41 has a front end edge 61, a rear end edge 63, a first connection edge 65, and a second connection edge. It has 67 and. The tip edge 61 is located on the most leading side in the rotation direction of the first moving body 11, and extends in the drive axis O direction, that is, in the front-rear direction of the first moving body 11. The rear end edge 63 is located on the trailing side of the drive shaft 3 and the moving body 10 in the rotational direction with respect to the tip edge 61, and extends in the front-rear direction of the second continuous passage 41. The trailing edge 63 has a shape that moves away from the tip edge 61 toward the trailing side in the rotational direction toward the front of the second passage 41. First connection edge 65 and. The second connection edge 67 extends in the circumferential direction of the first moving body 11 and is connected to the front end edge 61 and the rear end edge 63, respectively.

The tip edge 61 is composed of a first edge portion 61a, a second edge portion 61b, and a third edge portion 61c. The first edge portion 61a constitutes the front end side of the tip edge 61 and is connected to the first connection edge 65. The first edge portion 61a faces the first communication passages 22a to 22f when the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 is maximum, that is, at the maximum flow rate. ..

The third edge portion 61c constitutes the rear end side of the tip edge 61 and is connected to the second connection edge 67. The third edge portion 61c faces the first communication passages 22a to 22f when the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 is the minimum (hereinafter referred to as the minimum flow rate). It has become.

The second edge portion 61b is located between the first edge portion 61a and the third edge portion 61c, and is connected to the first edge portion 61a and the third edge portion 61c. The second edge portion 61b has a first continuous passage when the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 is less than the maximum and more than the minimum (hereinafter referred to as an intermediate flow rate). It is designed to face 22a to 22f. Here, the intermediate flow rate has a constant range between the maximum flow rate and the minimum flow rate. As a result, the second edge portion 61b extends longer in the front-rear direction than the first edge portion 61a and the third edge portion 61c. The opposition between the first to third edge portions 61a to 61c and the first communication passages 22a to 22f at the maximum flow rate, the minimum flow rate, and the intermediate flow rate will be described later. Further, by forming the second edge portion 61b so as to face the first continuous passages 22a to 22f from the time of the minimum flow rate to the time of the intermediate flow rate, the tip edge 61 is formed by the first edge portion 61a and the second edge portion 61b. It may be configured.

Here, the first edge portion 61a is located on the trailing side in the rotational direction of the drive shaft 3 and the moving body 10 as compared with the second edge portion 61b and the third edge portion 61c. Further, the first edge portion 61a has a curved portion 611 that curves toward the leading side in the rotational direction toward the second edge portion 61b. The first edge portion 61a is connected to the second edge portion 61b through the curved portion 611. In this way, the first edge portion 61a and the second edge portion 61b are continuous while gradually changing in the rotation direction. As shown in FIG. 15, the curved portion 611 is formed with a curvature along the shape of the first continuous passages 22a to 22f. On the other hand, there is no difference in the position in the rotation direction between the second edge portion 61b and the third edge portion 61c.

As shown in FIGS. 6, 8 and 9, the standing wall portion 11b is integrally formed with the back surface 112 of the peripheral wall portion 11a, and is arranged on the rear side of the first moving body 11. The vertical wall portion 11b has a plate shape extending vertically at right angles to the drive axis O direction. As shown in FIG. 6, the vertical wall portion 11b has an end face 113. The end face 113 is located on the opposite side of the peripheral wall portion 11a. Further, the vertical wall portion 11b is formed with a notch portion 114 forming a semicircle. The shape of the notch 114 can be appropriately designed, and the formation of the notch 114 can be omitted. Further, in FIGS. 13 to 15, the standing wall portion 11b and the notch portion 114 are not shown for the sake of simplicity. The same applies to FIGS. 16 to 18 and 20 which will be described later.

As shown in FIGS. 3 and 7 to 9, the second moving body 12 is formed in a substantially cylindrical shape having substantially the same diameter as the second diameter portion 352 of the first axis path 33d and the second axis path 35c. There is. At the rear end of the second moving body 12, a planar engaging portion 12a is formed. Further, a connecting path 120 is formed in the second moving body 12.

As shown in FIGS. 8 and 9, the connecting path 120 extends in the second moving body 12 in the direction of the drive axis O, and is open to the rear end of the second moving body 12. Further, the engaging portion 12a side of the connecting path 120 is open to the outer peripheral surface of the second moving body 12. Here, the connecting path 120 does not penetrate the inside of the second moving body 12 in the drive axis O direction, and does not open to the front end of the second moving body 12. As a result, the first surface 121 and the second surface 122 forming a planar shape are formed on the second moving body 12. The first surface 121 constitutes the front end surface of the second moving body 12 and faces forward. The second surface 122 is located in front of the connecting path 120 and faces the rear. The shape of the engaging portion 12a can be appropriately designed as long as it can be engaged with the standing wall portion 11b.

Further, in the second moving body 12, a ring groove 12b is formed between the first surface 121 and the second surface 122, that is, at a position on the front side of the connecting path 120. The ring groove 12b is provided with an O-ring 37.

The second moving body 12 is arranged in the second diameter portion 352 of the cap 35 with the engaging portion 12a facing the guide window 35a side, that is, the connecting path 120 facing the guide window 35a. There is. Further, in the cap 35, the second moving body 12 has the front end side entered into the first axis road 33d. As a result, a control pressure chamber 27 partitioned by the drive shaft main body 33 and the second moving body 12 is formed in the first shaft path 33d, that is, in the drive shaft 3. The control pressure chamber 27 communicates with the annular groove 24 through the first path 33e and the second path 35d. The air supply passage 13a is formed by the one connecting path 26a, the annular groove 24, and the first and second diameter paths 33e and 35d. The discharge chamber 29 and the control pressure chamber 27 communicate with each other by the air supply passage 13a. Further, the control pressure chamber 27 and the second diameter portion 352 are sealed by an O-ring 37.

Here, since the annular groove 24 is recessed in the second shaft hole 23 in an annular shape, the annular groove 24 and the second path 35d and the first path 33e are always in contact with each other even if the drive shaft 3 rotates. opposite. Therefore, even if the drive shaft 3 rotates, the annular groove 24 and the control pressure chamber 27 always communicate with each other.

The first moving body 11 is provided in the guide window 35a with the vertical wall portion 11b facing the second moving body 12. As a result, the first moving body 11 is attached to the cap 35, and the peripheral wall portion 11a is located in the second shaft hole 23 on the opposite side of the main body portion 35b with the drive shaft center O interposed therebetween. Here, since the peripheral wall portion 11a has a semicircular gutter shape having substantially the same diameter as the cap 35, the first moving body 11 is provided in the guide window 35a, and is shown in FIGS. 10 to 12. As described above, a cylindrical body having substantially the same diameter as the second shaft hole 23 is formed together with the main body portion 35b. As a result, the first moving body 11 aligns with the second shaft hole 23 together with the main body portion 35b.

Further, as shown in FIGS. 8 and 9, in the state where the first moving body 11 is provided in the guide window 35a, the standing wall portion 11b is brought into contact with the engaging portion 12a of the second moving body 12. .. As a result, the standing wall portion 11b and the engaging portion 12a are engaged with each other, so that the first moving body 11 and the second moving body 12 are assembled. In this way, the moving body 10 is attached to the cap 35. Then, the second communication passage 41 communicates with the communication path 120 while facing the communication path 120.

Further, a suction passage 39 is formed in the cap 35, that is, in the drive shaft 3, by the second diameter portion 352, the third diameter portion 353, and the notch portion 114. The communication path 120 communicates with the suction chamber 28 through the suction passage 39. As a result, the suction passage 39 and the connecting path 120 have suction pressure. Further, the connecting passage 120 communicates the second communication passage 41 with the suction chamber 28 through the suction passage 39. On the other hand, the suction passage 39 is partitioned from the control pressure chamber 27 by the second moving body 12. As a result, the suction passage 39 and the connecting path 120 are not communicated with the control pressure chamber 27.

In this compressor, the drive shaft 3 rotates around the drive shaft center O, so that the rotation of the drive shaft 3 is transmitted to the first moving body 11 through the first end surface 303. As a result, the moving body 10 including the first moving body 11 can rotate around the drive axis O together with the drive shaft 3. Here, by engaging the vertical wall portion 11b and the engaging portion 12a, the second moving body 12 becomes independent of the first moving body 11 in the first axis path 33d and in the second diameter portion 352. Rotation around the drive axis O is restricted.

Further, in the cap 35, suction pressure acts on the standing wall portion 11b of the first moving body 11 and the second surface 122 of the second moving body 12. On the other hand, a control pressure acts on the first surface 121 of the second moving body 12. The control pressure will be described later.

Then, by engaging the vertical wall portion 11b and the engaging portion 12a, the first moving body 11 and the second moving body 12 can move integrally in the drive axis O direction. In this way, the first moving body 11 can move back and forth in the guide window 35a in the drive axis O direction. On the other hand, the second moving body 12 can move back and forth in the drive axis O direction by sliding in the first shaft path 33d and the second diameter portion 352. In this way, the moving body 10 can move back and forth in the second shaft hole 23 in the drive axis O direction with respect to the drive shaft 3.

Further, the second communication passage 41 intermittently communicates with the first communication passages 22a to 22f as shown in FIGS. 10 to 12 by rotating the drive shaft 3. The second communication passage 41 communicates with the first communication passages 22a to 22f per rotation of the drive shaft 3 around the drive shaft center O, depending on the position of the first moving body 11 in the guide window 35a. The angle changes. In the following, the communication angle around the drive shaft center O in which the first communication passages 22a to 22f and the second communication passage 41 communicate with each other per rotation of the drive shaft 3 will be simply referred to as a communication angle. In FIGS. 4 to 9, for the sake of simplicity, the cap 35 and the first and second moving bodies 11 in a state where the drive shaft 3 and the fixed swash plate 5 are rotated from the positions shown in FIGS. 1 and 2. , 12 are illustrated. Further, in FIGS. 8 to 12, in order to facilitate the explanation, the shape and the like of the second passage 41 are shown in a simplified manner.

As shown in FIGS. 8 and 9, an urging spring 43 is provided between the second stage portion 355 and the moving body 10 in the cap 35. The urging spring 43 urges the moving body 10 toward the front of the cap 35.

As shown in FIGS. 1 and 2, the control valve 13 is provided in the rear housing 19. The control valve 13 is connected to the second connection path 26b. As a result, the control valve 13 is connected to the annular groove 24 and, by extension, the control pressure chamber 27 through the second connecting path 26b. Further, the control valve 13 is connected to the third connection path 26c. As a result, the control valve 13 is connected to the suction chamber 28 through the third connection path 26c. In this way, the second connecting path 26b and the third connecting path 26c are connected through the control valve 13. In this way, the second connecting path 26b and the third connecting path 26c form an bleed air passage 13b. That is, in this compressor, the control pressure chamber 27 and the suction chamber 28 are connected by the bleed air passage 13b and the control valve 13. Further, the control valve 13 is also connected to the suction chamber 28 by a detection passage (not shown).

In this compressor, a part of the refrigerant gas in the discharge chamber 29 flows to the control pressure chamber 27 through the air supply passage 13a. Further, the refrigerant gas in the control pressure chamber 27 flows to the suction chamber 28 through the bleed air passage 13b. Then, the control valve 13 adjusts the valve opening degree by sensing the suction pressure in the suction chamber 28 through the detection passage. As a result, the control valve 13 adjusts the flow rate of the refrigerant gas flowing through the bleed air passage 13b by adjusting the opening degree of the bleed air passage 13b. Specifically, the control valve 13 increases the flow rate of the refrigerant gas flowing from the control pressure chamber 27 to the suction chamber 28 via the bleed air passage 13b by increasing the valve opening degree. On the other hand, the control valve 13 reduces the flow rate of the refrigerant gas flowing from the control pressure chamber 27 to the suction chamber 28 via the bleed air passage 13b by reducing the valve opening degree. In this way, the control valve 13 changes the flow rate of the refrigerant gas flowing from the control pressure chamber 27 to the suction chamber 28 with respect to the flow rate of the refrigerant gas flowing from the discharge chamber 29 to the control pressure chamber 27, thereby causing the control pressure chamber. The control pressure, which is the pressure of the refrigerant gas of 27, is controlled. The third connecting passage 26c is connected to the swash plate chamber 31 instead of the suction chamber 28 to connect the control valve 13 and the swash plate chamber 31 through the third connecting passage 26c, that is, the bleed air passage 13b and the control valve. 13 may be configured to connect the control pressure chamber 27 and the swash plate chamber 31.

In the compressor configured as described above, the drive shaft 3 rotates around the drive shaft center O, so that the fixed swash plate 5 rotates in the swash plate chamber 31. As a result, the piston 7 reciprocates in the cylinder bores 21a to 21f between the top dead center and the bottom dead center. Hereinafter, the movement of the piston 7 from the top dead center to the bottom dead center in the cylinder bores 21a to 21f is referred to as an outward path. Further, the movement of the piston 7 from the bottom dead center to the top dead center in the cylinder bores 21a to 21f is referred to as a return path. Then, when the piston 7 is on the outward path, in the compression chambers 45a to 45f, the refrigerant gas remaining inside (hereinafter referred to as residual gas) re-expands, and further, the first communication passages 22a to 22f and the first. By communicating with the two communication passages 41, the process shifts to the suction process of sucking the refrigerant gas. On the other hand, when the piston 7 is on the return path, the compression chambers 45a to 45f perform a compression stroke for compressing the internal refrigerant gas, and then shift to a discharge stroke for discharging the compressed refrigerant gas to the discharge chamber 29. When the piston 7 is on the return path, the first communication passages 22a to 22f and the second communication passage 41 are not communicated with each other. Further, the refrigerant gas discharged to the discharge chamber 29 by the discharge stroke is discharged to the condenser via the discharge port 29a.

Specifically, in this compressor, when the drive shaft 3 is at the rotation angle shown in FIGS. 1, 2 and 10 to 12, the piston 7 is the outward path in the compression chambers 45a to 45c. That is, in the compression chamber 45a, the piston 7 is in the initial stage of the outward path, in the compression chamber 45b, the piston 7 is in the middle stage where the piston 7 is advanced from the initial stage of the outward path, and in the compression chamber 45c, the piston 7 is in the middle stage where the piston 7 is advanced from the middle stage of the outward path. It will be a stage. On the other hand, in the compression chambers 45d to 45f, the piston 7 is the return path. That is, in the compression chamber 45d, the piston 7 is in the initial stage of the return path, and is in the initial stage of the compression stroke. Further, in the compression chamber 45e, the piston 7 is in the middle stage of the return path, and is in the middle stage of the compression stroke. Then, in the compression chamber 45f, the piston 7 enters the late stage of the return path, and shifts from the late stage of the compression stroke to the discharge stroke. In FIGS. 10 to 12, the piston 7 is not shown for the sake of simplicity.

In this compressor, the first moving body 11 is provided in the guide window 35a, so that the first moving body 11 has the compression chamber 45a to which the piston 7 is in the outward path among the first communication passages 22a to 22f. It faces the first communication passages 22a to 22f communicating with 45f. More specifically, when the drive shaft 3 is at the rotation angle shown in FIGS. 1, 2 and 10 to 12, the first moving body 11 is compressed with the first communication passage 22a communicating with the compression chamber 45a. It faces the first communication passage 22b communicating with the chamber 45b and the first communication passage 22c communicating with the compression chamber 45c. If the drive shaft 3 rotates further in the R1 direction than in the state shown in FIG. 10 or the like, the piston 7 becomes the outward path in the compression chamber 45f and the piston 7 becomes the return path in the compression chamber 45c. The first communication passage 22f communicating with the compression chamber 45f, the first communication passage 22a communicating with the compression chamber 45a, and the first communication passage 22b communicating with the compression chamber 45b face each other. As the drive shaft 3 rotates in this way, the first moving body 11 sequentially faces the first communication passages 22a to 22f in which the piston 7 communicates with the compression chambers 45a to 45f in the outward path.

As a result, the compression chambers 45a to 45 in which the piston 7 is on the outward path shift from the re-expansion stroke to the suction stroke. As a result, the refrigerant gas in the suction chamber 28 is sucked into the compression chambers 45a to 45f in the suction stroke through the suction passage 39, the connecting passage 120, the second communication passage 41, and the first communication passages 22a to 22f. That is, the first moving body 11 sequentially faces the first communication passages 22a to 22f communicating with the compression chambers 45a to 45f in the re-expansion stroke or the suction stroke.

On the other hand, the main body portion 35b of the cap 35 is located on the opposite side of the guide window 35a with the drive shaft center O interposed therebetween, that is, on the opposite side of the first moving body 11. Therefore, the main body portion 35b faces the first communication passages 22a to 22f in which the piston 7 communicates with the compression chambers 45a to 45f in the return path among the first communication passages 22a to 22f. More specifically, when the drive shaft 3 is at the rotation angle shown in FIGS. 1, 2 and 10 to 12, the main body portion 35b has a first communication passage 22d communicating with the compression chamber 45d and a compression chamber 45e. The first communication passage 22e communicating with the compression chamber 45f and the first communication passage 22f communicating with the compression chamber 45f face each other. In this way, the main body 35b has the first communication passage 22a in which the piston 7 communicates with the compression chambers 45a to 45f in the return path, that is, the compression chambers 45a to 45f in the compression stroke or the discharge stroke by the rotation of the drive shaft 3. It faces up to 22f in sequence.

Then, in this compressor, by moving the moving body 10 in the drive axis O direction with respect to the drive shaft 3, the refrigerant sucked from the suction chamber 28 into the compression chambers 45a to 45f per rotation of the drive shaft 3. The flow rate of gas can be changed. Thereby, in this compressor, the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 can be changed.

Specifically, when reducing the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29, the control valve 13 increases the valve opening degree and the opening degree of the bleed air passage 13b. Therefore, the flow rate of the refrigerant gas flowing from the control pressure chamber 27 to the suction chamber 28 is increased. In this way, the control valve 13 reduces the control pressure of the control pressure chamber 27. As a result, the variable differential pressure, which is the differential pressure between the control pressure and the suction pressure, becomes small.

Therefore, in the moving body 10, the second moving body 12 moves forward in the first shaft path 33d and the second diameter portion 352 in the drive axis O direction from the position shown in FIG. 9 by the urging force of the urging spring 43. Start moving to. Further, the first moving body 11 also starts to move forward in the guide window 35a in the drive axis O direction by the urging force of the urging spring 43. Therefore, the second passage 41 moves forward relative to the first passages 22a to 22f. Thus, in this compressor, the communication angle gradually decreases.

Then, the control valve 13 further reduces the control pressure of the control pressure chamber 27, so that the variable differential pressure is minimized. As a result, as shown in FIG. 8, in the moving body 10, the first moving body 11 is in a state of moving most forward in the guide window 35a and comes into contact with the first regulation surface 301. As a result, the forward movement of the first moving body 11 in the guide window 35a is restricted. Further, the forward movement of the second moving body 12 in the first axis path 33d and the second diameter portion 352 through the first moving body 11 is also restricted. As described above, the first moving body 11 moves to the frontmost in the guide window 35a, so that the second communication passage 41 communicates with the first communication passages 22a to 22f at the first portion 411. This minimizes the communication angle in this compressor.

Therefore, when the drive shaft 3 is at the rotation angle shown in FIG. 10, the first moving body 11 communicates the first communication passage 22a and the second communication passage 41. Then, the first moving body 11 makes the first communication passages 22b and 22c non-communication with the second communication passage 41 by the peripheral wall portion 11a. That is, the first moving body 11 communicates with the second communication passage 41 only in the first communication passages 22a to 22f in which the piston 7 communicates with the compression chambers 45a to 45f in the initial stage of the outward path. On the other hand, the main body portion 35b of the cap 35 does not communicate between the first communication passages 22d to 22f and the second communication passage 41. In this way, the main body portion 35b makes the first communication passages 22a to 22f communicating with the compression chambers 45a to 45f in the compression stroke or the discharge stroke non-communication with the second communication passage 41.

Explaining the first communication passage 22a communicating with the compression chamber 45a and the compression chamber 45a as an example, when the variable differential pressure is the minimum and the communication angle is the minimum, the first moving body 11 moves forward in the guide window 35a. By moving, as shown in FIG. 13, in the second communication passage 41, the third edge portion 61c of the tip edge 61 faces the first communication passage 22a. Then, as the first moving body 11 rotates together with the drive shaft 3, the first continuous passage 22a moves relative to the trailing side in the rotation direction with respect to the third edge portion 61c, that is, from the lower side to the upper side of the paper surface of FIG. do. In this way, the first communication passage 22a communicates with the second communication passage 41 until it faces the rear end edge 63. Therefore, the compression chamber 45a shifts from the re-expansion stroke to the suction stroke. Then, the suction stroke is completed when the first continuous passage 22a faces the rear end edge 63.

As described above, by minimizing the communication angle, the suction passage 39, the communication path 120, the second communication passage 41, and the first communication are connected to the compression chambers 45a to 45f only when the piston 7 is in the initial stage of the outward path. Refrigerant gas is sucked from the suction chamber 28 through the passages 22a to 22f. Therefore, the flow rate of the refrigerant gas sucked from the suction chamber 28 into the compression chambers 45a to 45f is the smallest. In this way, in this compressor, the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 has the minimum flow rate.

On the other hand, when increasing the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29, the control valve 13 controls by reducing the valve opening degree and the opening degree of the bleed air passage 13b. The flow rate of the refrigerant gas flowing from the pressure chamber 27 to the suction chamber 28 is reduced. In this way, the control valve 13 increases the control pressure of the control pressure chamber 27. As a result, the variable differential pressure becomes larger than the minimum.

Therefore, in the moving body 10, the second moving body 12 resists the urging force of the urging spring 43 and drives the drive shaft center O in the first axis 33d and in the second diameter portion 352 from the position shown in FIG. Start moving backwards in the direction. As a result, the first moving body 11 also starts to move backward in the guide window 35a in the drive axis O direction while resisting the urging force of the urging spring 43. Therefore, the second passage 41 moves rearward with respect to the first passages 22a to 22f. Thus, in this compressor, the communication angle is greater than the minimum and smaller than the maximum.

Therefore, when the drive shaft 3 is at the rotation angle shown in FIG. 11, the first moving body 11 communicates the first communication passages 22a and 22b with the second communication passage 41. Then, the first moving body 11 makes the first communication passage 22c and the second communication passage 41 non-communication by the peripheral wall portion 11a. That is, the first moving body 11 has the first communication passages 22a to 22f in which the piston 7 communicates with the compression chambers 45a to 45f in the initial stage of the outward path, and the compression chambers 45a to 45f in which the piston 7 communicates with the compression chambers 45a to 45f in the middle stage of the outward path. The first communication passages 22a to 22f and the second communication passage 41 are communicated with each other. Further, also in this case, by making the first communication passages 22d to 22f and the second communication passage 41 non-communication, the first communication passages 22a to communicate with the compression chambers 45a to 45f in the compression stroke or the discharge stroke. The 22f and the second communication passage 41 are not communicated with each other.

Explaining the compression chamber 45a and the first continuous passage 22a as an example, the variable differential pressure becomes larger than the minimum, and the first moving body 11 moves backward in the guide window 35a as shown by the black arrow in FIG. As a result, in the second continuous passage 41, the second edge portion 61b of the tip edge 61 faces the first continuous passage 22a. Then, as the first moving body 11 rotates together with the drive shaft 3, the first continuous passage 22a moves relative to the trailing side in the rotation direction with respect to the second edge portion 61b. In this way, the first communication passage 22a communicates with the second communication passage 41 until it faces the rear end edge 63. Here, when the second edge portion 61b faces the first continuous passage 22a, the trailing end edge 63 faces the trailing side in the rotation direction as compared with the case where the third edge portion 61c faces the first continuous passage 22a. Located in. As a result, when the second edge portion 61b faces the first communication passage 22a, the communication angle becomes larger than the minimum.

As described above, when the communication angle becomes larger than the minimum, the suction passage 39, the communication path 120, and the second communication passage are provided in the compression chambers 45a to 45f while the piston 7 is in the initial stage to the middle stage of the outward route. Refrigerant gas is sucked from the suction chamber 28 through the 41 and the first continuous passages 22a to 22f. Therefore, the flow rate of the refrigerant gas sucked from the suction chamber 28 into the compression chambers 45a to 45f is larger than the minimum. In this way, in this compressor, the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 has an intermediate flow rate. Here, as shown in FIGS. 13 and 14, there is no difference in the position in the rotation direction between the second edge portion 61b and the third edge portion 61c. Therefore, the timing at which the compression chambers 45a to 45f shift from the re-expansion stroke to the suction stroke, that is, the position of the piston 7 on the outward path is the same between the minimum flow rate and the intermediate flow rate.

Then, the control valve 13 further increases the control pressure of the control pressure chamber 27, so that the variable differential pressure becomes maximum. Therefore, as shown in FIG. 8, in the moving body 10, the first moving body 11 is in a state of moving most rearward in the guide window 35a and comes into contact with the second regulating surface 302. As a result, the backward movement of the first moving body 11 in the guide window 35a is restricted. Further, the backward movement of the second moving body 12 in the first axis path 33d and the second diameter portion 352 through the first moving body 11 is also restricted. As described above, the first moving body 11 moves to the rearmost position in the guide window 35a, so that the second communication passage 41 communicates with the first communication passages 22a to 22f at the second portion 412. This maximizes the communication angle in this compressor.

Therefore, when the drive shaft 3 is at the rotation angle shown in FIG. 12, the first moving body 11 communicates the first communication passages 22a to 22c with the second communication passage 41. That is, the first moving body 11 has the first communication passages 22a to 22f in which the piston 7 communicates with the compression chambers 45a to 45f in the initial stage of the outward path, and the compression chambers 45a to 45f in which the piston 7 communicates with the compression chambers 45a to 45f in the middle stage of the outward path. The first communication passages 22a to 22f that communicate with each other, the first communication passages 22a to 22f in which the piston 7 communicates with the compression chambers 45a to 45f in the latter stage of the outward path, and the second communication passage 41 are communicated with each other. Further, also in this case, by making the first communication passages 22d to 22f and the second communication passage 41 non-communication, the first communication passages 22a to communicate with the compression chambers 45a to 45f in the compression stroke or the discharge stroke. The 22f and the second communication passage 41 are not communicated with each other.

Explaining the first communication passage 22a communicating with the compression chamber 45a and the compression chamber 45a as an example, the variable differential pressure becomes maximum, and as shown by the black arrow in FIG. 15, the first moving body 11 is most inside the guide window 35a. By moving backward, in the second communication passage 41, the first edge portion 61a of the tip edge 61 faces the first communication passage 22a. Then, as the first moving body 11 rotates together with the drive shaft 3, the first continuous passage 22a moves relative to the trailing side in the rotation direction with respect to the first edge portion 61a. In this way, the first communication passage 22a communicates with the second communication passage 41 until it faces the rear end edge 63. Here, when the first edge portion 61a faces the first continuous passage 22a, the trailing end edge 63 rotates as compared with the case where the second edge portion 61b and the third edge portion 61c face the first continuous passage 22a. It is located on the trailing side of the direction. As a result, when the first edge portion 61a faces the first communication passage 22a, the communication angle becomes maximum.

Thus, when the communication angle is maximum, the compression chambers 45a to 45f have the suction passage 39, the connecting passage 120, the second communication passage 41, and the first communication while the piston 7 is in the early stage to the late stage of the outward path. Refrigerant gas is sucked from the suction chamber 28 through the passages 22a to 22f. Therefore, the flow rate of the refrigerant gas sucked from the suction chamber 28 into the compression chambers 45a to 45f is the largest. As a result, in this compressor, the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 becomes the maximum flow rate.

Here, the first edge portion 61a is located on the trailing side in the rotation direction with respect to the second edge portion 61b and the third edge portion 61c. Therefore, taking the first passage 22a as an example, at the rotation angle of the drive shaft 3 at which the second passage 41 starts to communicate with the first passage 22a at the minimum flow rate or the intermediate flow rate, it is still at the maximum flow rate. The first continuous passage 22a does not face the first edge portion 61a, and the second continuous passage 41 is not in communication with the first continuous passage 22a. That is, at the maximum flow rate, the drive shaft 3 rotates further in the R1 direction than the rotation angle of the drive shaft 3 at which the second passage 41 starts communicating with the first passage 22a at the minimum flow rate or the intermediate flow rate. There is a need. As a result, at the maximum flow rate, the timing at which the compression chambers 45a to 45f shift from the re-expansion stroke to the suction stroke is delayed as compared with the minimum flow rate and the intermediate flow rate. That is, at the maximum flow rate, the compression chambers 45a to 45f shift from the re-expansion stroke to the suction stroke when the piston 7 advances further on the outward path as compared with the minimum flow rate and the intermediate flow rate. In other words, at the maximum flow rate, when the piston 7 approaches the intermediate stage of the outward path, the compression chambers 45a to 45f shift from the re-expansion stroke to the suction stroke, so that the drive shaft 3 re-expands per rotation. The duration of the stroke becomes longer and the start of the inhalation stroke is delayed. At the maximum flow rate, the start of the suction stroke is delayed in this way, but as described above, since the refrigerant gas is sucked from the suction chamber 28 even while the piston 7 is in the latter stage of the outward path, the suction chamber 28 The flow rate of the refrigerant gas sucked into the compression chambers 45a to 45f is the largest.

In this compressor, the pressure of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 is higher at the maximum flow rate than at the minimum flow rate and the intermediate flow rate. Therefore, at the maximum flow rate, the pressure of the residual gas remaining in the compression chambers 45a to 45f without being discharged to the discharge chamber 29 in the discharge stroke is higher than that at the minimum flow rate and the intermediate flow rate.

In this respect, in this compressor, the timing at which the first communication passages 22a to 22f and the second communication passage 41 communicate with each other is delayed at the maximum flow rate and at the intermediate flow rate, so that the compression chamber 45a The timing at which ~ 45f shifts from the re-expansion stroke to the inhalation stroke is delayed. Therefore, in this compressor, the residual gas can be sufficiently depressurized in the re-expansion stroke at the maximum flow rate. Therefore, when the first communication passages 22a to 22f and the second communication passage 41 communicate with each other, that is, at the start of the suction stroke, the residual gas in the compression chambers 45a to 45f is the second communication passage 41, and eventually the suction chamber 28. It is possible to suppress backflow to. As a result, even if the first communication passages 22a to 22f and the second communication passage 41 communicate with each other, the pressure in the compression chambers 45a to 45f is unlikely to drop sharply. In this way, when the piston 7 moves from the top dead center to the bottom dead center, the pressure in the compression chambers 45a to 45f during the re-expansion stroke, that is, the pressure of the residual gas can be suitably used. As a result, in this compressor, since the piston 7 easily moves from the top dead center to the bottom dead center at the maximum flow rate, it is possible to suppress an increase in the rotational driving force of the drive shaft 3. Further, since the residual gas remaining in the compression chambers 45a to 45f is suppressed from flowing back into the second passage 41, this compressor can suppress the suction pulsation at the maximum flow rate. ..

On the other hand, at the minimum flow rate and the intermediate flow rate, the pressure of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 is lower than that at the maximum flow rate, and the pressure remaining in the compression chambers 45a to 45f is correspondingly low. The gas pressure is also low. In this respect, in this compressor, the timing at which the compression chambers 45a to 45f shift from the re-expansion stroke to the suction stroke is earlier than that at the maximum flow rate at the minimum flow rate and the intermediate flow rate.

Therefore, in this compressor, it is possible to prevent the inside of the compression chambers 45a to 45f from becoming lower than the suction pressure, that is, the pressure of the suction chamber 28 due to the re-expansion stroke at the minimum flow rate and the intermediate flow rate. As a result, since the piston 7 easily moves from the top dead center to the bottom dead center even at the minimum flow rate and the intermediate flow rate, it is possible to suppress an increase in the rotational driving force of the drive shaft 3. There is. Further, by preventing the pressure inside the compression chambers 45a to 45f from becoming lower than the suction pressure, the compressor can suppress the suction pulsation at the minimum flow rate and the intermediate flow rate.

Therefore, according to the compressor of the first embodiment, it is possible to suppress an increase in the rotational driving force of the drive shaft 3 during operation and also to suppress suction pulsation.

Further, in this compressor, a part of the high-pressure refrigerant gas compressed in the compression stroke through the first communication passages 22a to 22f communicating with the compression chambers 45a to 45f in the compression stroke or the discharge stroke is partly in the second shaft hole 23. It circulates inward. In this respect, in this compressor, the moving body 10 has the first moving body 11 and the second moving body 12, and the cap 35 is formed with a guide window 35a for arranging the first moving body 11. There is. As a result, in this compressor, the main body portion 35b of the cap 35 faces the first communication passages 22a to 22f communicating with the compression chambers 45a to 45f in the compression stroke or the discharge stroke in the second shaft hole 23. In this way, the main body portion 35b makes the first communication passages 22a to 22f communicating with the compression chambers 45a to 45f in the compression stroke or the discharge stroke non-communication with the second communication passage 41. Here, since the cap 35 is made of steel, in this compressor, the cap 35, that is, the drive shaft 3, can suitably receive the compression load from the compression chambers 45a to 45f in the compression stroke and the discharge stroke. ..

Therefore, it becomes difficult for the compressive load to act on the first moving body 11 and eventually the moving body 10, so that the moving body 10 can easily move in the drive axis O direction. As a result, in this compressor, it is easy to change the flow rate of the refrigerant gas discharged from each of the compression chambers 45a to 45f to the discharge chamber 29 per rotation of the drive shaft 3. Further, in this compressor, it is not necessary to make the second moving body 12 excessively large in order to increase the pressure receiving area with respect to the control pressure.

Further, in this compressor, at the tip edge 61 of the second passage 41, the first edge portion 61a is connected to the second edge portion 61b through the curved portion 611. As a result, the first edge portion 61a and the second edge portion 61b are continuous while gradually changing in the rotational direction. Therefore, while increasing the degree of freedom in designing the second passage 41 including the tip edge 61, the communication timing between the first passages 22a to 22f and the second passage 41 at the maximum flow rate and the minimum flow rate It is possible to suitably set the communication timing between the first communication passages 22a to 22f and the second communication passage 41 at the time of the intermediate flow rate.

Further, in this compressor, in the transition period when the flow rate changes from the intermediate flow rate to the maximum flow rate, the communication timing between the first communication passage 22a to 22f and the second communication passage 41 is gradually delayed by the curved portion 611. It has become. Since the curved portion 611 is formed with a curvature along the first continuous passages 22a to 22f, the curved portion 611 preferably faces the first continuous passages 22a to 22f. As a result, the refrigerant gas leaks from the second communication passage 41 to the first communication passages 22a to 22f through the curved portion 611, that is, in the curved portion 611, the first communication passages 22a to 22f and the second communication passage 41 It is possible to suitably prevent the communication timing from being advanced.

Further, in this compressor, punching control is performed in which the flow rate of the refrigerant gas flowing from the control pressure chamber 27 to the suction chamber 28 via the bleed air passage 13b is changed by the control valve 13. As a result, in this compressor, the amount of the refrigerant gas in the discharge chamber 29 used for changing the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 can be reduced, so that the efficiency of the compressor can be reduced. It is possible to make it higher.

(Example 2)
As shown in FIG. 16, in the compressor of the second embodiment, in the tip edge 61 of the second passage 41, the first edge portion 61a, the second edge portion 61b, and the third edge portion 61c gradually change in the rotation direction. It is continuous while doing. As a result, the tip edge 61 has a shape that gradually extends from the leading side to the trailing side in the rotational direction from the rear end to the front end. Other configurations in this compressor are the same as those in the compressor of the first embodiment, and the same configurations are designated by the same reference numerals and detailed description of the configurations will be omitted.

In this compressor, the communication timing between the first communication passages 22a to 22f and the second communication passage 41 is gradually delayed while changing from the minimum flow rate to the maximum flow rate through the intermediate flow rate. In this way, it is possible for this compressor to perform the same operation as that of the compressor of the first embodiment.

(Example 3)
As shown in FIG. 17, in the compressor of the third embodiment, in the tip edge 61 of the second passage 41, the first edge portion 61a and the second edge portion 61b have a step 612 and are continuous. .. As a result, in this compressor, the tip edge 61 changes from the second edge portion 61b to the first edge portion 61a at a time at the portion of the step 612. Other configurations of this compressor are the same as those of the compressor of the first embodiment.

In this compressor, when the flow rate changes from the intermediate flow rate to the maximum flow rate, the communication timing between the first communication passages 22a to 22f and the second communication passage 41 suddenly changes due to the step 612. That is, in this compressor, when the flow rate changes from the intermediate flow rate to the maximum flow rate, the communication timing between the first communication passages 22a to 22f and the second communication passage 41 is changed at once. Other operations in this compressor are the same as those in the compressor of Example 1.

(Example 4)
As shown in FIGS. 18 and 19, in the compressor of the fourth embodiment, the second connecting passage 41 is composed of a hole portion 41a and a recessed portion 41b. The recess 41b is recessed in the surface 111. The recess 41b faces the hole 41a and communicates with the hole 41a. As a result, in this compressor, the tip edge 61 of the second passage 41 is formed by the hole 41a and the recess 41b. Specifically, in the tip edge 61, the second edge portion 61b and the third edge portion 61c are formed by the recess 41b. As a result, the second edge portion 61b and the third edge portion 61c are located on the front side in the rotation direction of the first moving body 11 with respect to the third edge portion 61c. Further, in this compressor, the first edge portion 61a and the second edge portion 61b, that is, the first edge portion 61a and the recess 41b have a step 612 and are continuous. Other configurations of this compressor are the same as those of the compressor of the first embodiment.

In this compressor, the second edge portion 61b of the tip edge 61 faces the first continuous passages 22a to 22f at the intermediate flow rate. Then, as the first moving body 11 rotates together with the drive shaft 3, the first continuous passages 22a to 22f move relative to the rearward side in the rotation direction with respect to the second edge portion 61b and face the recess 41b. .. As a result, while the first connecting passages 22a to 22f face the recess 41b, the refrigerant gas flows from the hole 41a through the recess 41b to the first connecting passages 22a to 22f. The same applies to the minimum flow rate. As a result, in this compressor, the timing at which the first communication passages 22a to 22f and the second communication passage 41 communicate with each other is earlier than at the maximum flow rate at the minimum flow rate and the intermediate flow rate. In other words, even in this compressor, the communication timing between the first communication passages 22a to 22f and the second communication passage 41 is delayed at the maximum flow rate. Other operations in this compressor are the same as those in the compressor of Example 1.

(Example 5)
As shown in FIG. 20, in the compressor of the third embodiment, in the tip edge 61 of the second passage 41, the third edge portion 61c is behind the second edge portion 61b in the rotation direction of the first moving body 11. Located on the side. More specifically, the third edge portion 61c is located on the trailing side in the rotation direction with respect to the second edge portion 61b and on the leading side in the rotation direction with respect to the first edge portion 61a. That is, in the tip edge 61, the second edge portion 61b is located on the leading side in the rotation direction most. Further, the first edge portion 61a and the second edge portion 61b have a step 612 and are continuous. The third edge portion 61c and the second edge portion 61b have a step 613 and are continuous. As a result, in this compressor, the tip edge 61 changes from the second edge 61b to the first edge 61a at once at the step 612, and at the step 613, the tip edge 61 changes to the third edge at the step 613. It changes from 61c to the second edge 61b at a time. Other configurations of this compressor are the same as those of the compressor of the first embodiment.

In this compressor, since the third edge portion 61c is located on the trailing side in the rotation direction with respect to the second edge portion 61b, the first communication passages 22a to 22f are located at the minimum flow rate as compared with the intermediate flow rate. The timing of communication with the second communication passage 41 is delayed. Therefore, in this compressor, the timing at which the compression chambers 45a to 45f shift from the re-expansion stroke to the suction stroke at the minimum flow rate is delayed as compared with the compressor of the first embodiment. As a result, in this compressor, the period of the suction stroke at the minimum flow rate becomes shorter, so that the flow rate of the refrigerant gas sucked into the compression chambers 45a to 45f, and eventually the flow rate of the refrigerant gas is discharged from the compression chambers 45a to 45f to the discharge chamber 29. The flow rate of the refrigerant gas is reduced. Here, since the third edge portion 61c is located on the preceding side in the rotation direction with respect to the first edge portion 61a, the communication timing between the first communication passages 22a to 22f and the second communication passage 41 at the minimum flow rate is reached. Is earlier than the communication timing between the first communication passages 22a to 22f and the second communication passage 41 at the maximum flow rate. Other operations in this compressor are the same as those in the compressor of Example 1.

Here, in this compressor, the communication timing between the first communication passages 22a to 22f and the second communication passage 41 at the minimum flow rate, and the communication timing between the first communication passages 22a to 22f and the second communication passage 41 at the maximum flow rate. The position in the rotation direction on the third edge portion 61c may be designed so that the communication timing is the same. Further, the communication timing between the first communication passage 22a to 22f and the second communication passage 41 at the minimum flow rate is later than the communication timing between the first communication passage 22a to 22f and the second communication passage 41 at the maximum flow rate. As described above, the position in the rotation direction at the third edge portion 61c may be designed.

Although the present invention has been described above with reference to Examples 1 to 5, the present invention is not limited to the above-mentioned Examples 1 to 5, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.

For example, the compressors of Examples 1 to 5 may be configured as a double-headed piston type compressor.

Further, in the compressors of Examples 1 to 5, a protrusion or the like is formed on the tip edge 61 of the second passage 41 so as to protrude toward the trailing side in the rotation direction of the first moving body 11, and the protrusion or the like is formed. The first edge portion 61a may be configured by the above method. Further, a notch or the like extending toward the leading side in the rotation direction of the first moving body 11 is formed on the tip edge 61 of the second continuous passage 41, and the notch or the like constitutes the second edge portion 61b. Is also good.

Further, in the compressors of Examples 1 to 5, the moving body 10 is formed by the first moving body 11 and the second moving body 12. However, the present invention is not limited to this, and the moving body 10 may be formed in a cylindrical shape having substantially the same diameter as the second shaft hole 23, and the drive shaft 3 may be inserted through the moving body 10.

Further, the compressors of Examples 1 to 5 may be configured such that a part of the refrigerant gas once sucked into the compression chambers 45a to 45f is discharged from the compression chambers 45a to 45f by the second connecting passage 41. Then, by changing the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f by changing the communication angle, the refrigerant discharged from the compression chambers 45a to 45f to the discharge chamber 29 per rotation of the drive shaft 3 The flow rate of the gas may be changed.

Further, in the compressors of the first to fifth embodiments, the communication angle changes according to the position of the first moving body 11 in the guide window 35a, that is, the position of the moving body 10 in the drive axis O direction. The flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 is changed. However, not limited to this, the compression chambers 45a to 45f change due to the change in the communication area between the first communication passages 22a to 22f and the second communication passage 41 according to the position of the moving body 10 in the drive axis O direction. The flow rate of the refrigerant gas discharged from the discharge chamber 29 may be changed.

Further, with respect to the compressors of Examples 1 to 5, the second moving body 12 does not slide with the second diameter portion 352, and a gap is formed between the second moving body 12 and the second diameter portion 352. You may have.

Further, for the compressors of Examples 1 to 5, instead of the shoes 8a and 8b, the rocking plate is supported on the rear surface side of the fixed swash plate 5 via a thrust bearing, and the rocking plate and the piston 7 are provided. A wobble-type conversion mechanism connected by a connecting rod may be adopted.

Further, in the compressors of Examples 1 to 5, external control may be performed to control the control pressure by switching ON and OFF of the current from the outside to the control valve 13, and the control may be performed regardless of the current from the outside. Internal control to control the pressure may be performed. Here, if the valve opening is configured to be increased by turning off the current to the control valve 13, the valve opening is increased when the compressor is stopped, and the control pressure of the control pressure chamber 27 can be lowered. .. Therefore, since the compressor can be started in a state where the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 is the minimum, the start-up shock can be reduced.

Further, in the compressors of Examples 1 to 5, input control may be performed in which the flow rate of the refrigerant gas introduced from the discharge chamber 29 to the control pressure chamber 27 via the supply air passage 13a is changed by the control valve 13. In this case, the control pressure chamber 27 can be rapidly increased in pressure, and the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 can be rapidly increased. Here, in the case of performing external control, if the control valve 13 is configured to reduce the valve opening degree by turning off the current to the control valve 13, the valve opening degree is set when the compressor is stopped. Can be reduced, and the control pressure of the control pressure chamber 27 can be lowered. Therefore, since the compressor can be started in a state where the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 is the minimum, the start-up shock can be reduced.

Further, in the compressors of Examples 1 to 5, instead of the control valve 13, a three-way valve whose opening degree can be adjusted by both the air supply passage 13a and the bleed air passage 13b may be adopted.

Further, with respect to the compressors of Examples 1 to 5, the control valve 13 reduces the control pressure of the control pressure chamber 27, so that the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 increases. It may be.

The present invention can be used for vehicle air conditioners and the like.

1 ... Housing 3 ... Drive shaft 5 ... Fixed swash plate 7 ... Piston 9 ... Valve forming plate (discharge valve)
10 ... Moving body 13 ... Control valve 21 ... Cylinder block 21a to 21f ... Cylinder bore 22a to 22f ... First continuous passage 23 ... Second shaft hole (shaft hole)
29 ... Discharge chamber 31 ... Slope chamber 35a ... Guide window 41 ... Second passage 45a-45f ... Compression chamber 61 ... Tip edge 61a ... First edge 61b ... Second edge 63 ... Rear end edge 173 ... First axis Hole (shaft hole)
612 ... Step

Claims (4)

A housing having a cylinder block in which a plurality of cylinder bores are formed, a discharge chamber, a swash plate chamber, and a shaft hole.
A drive shaft rotatably supported in the shaft hole and
A fixed swash plate that can be rotated in the swash plate chamber by rotation of the drive shaft and has a constant inclination angle with respect to a plane perpendicular to the drive shaft.
A piston that forms a compression chamber in the cylinder bore and is connected to the fixed swash plate,
A discharge valve that discharges the refrigerant in the compression chamber to the discharge chamber,
A moving body provided on the drive shaft, located in the shaft hole, rotated integrally with the drive shaft, and movable with respect to the drive shaft in the direction of the drive shaft center based on the control pressure.
A control valve for controlling the control pressure is provided.
The cylinder block is formed with a first communication passage that communicates with the compression chamber.
The moving body extends in the circumferential direction of the moving body and intermittently communicates with the first communication passage as the drive shaft rotates, so that the refrigerant is sucked into the compression chamber through the first communication passage. The second passage is formed,
A piston type compressor in which the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber changes according to the position of the moving body in the drive axis direction.
The second passage has a tip edge located on the leading side in the rotational direction of the moving body and a trailing edge edge located on the trailing side in the rotational direction with respect to the tip edge.
The tip edge is discharged from the compression chamber to the discharge chamber and a first edge portion facing the first continuous passage when the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber is maximum. It has a second edge facing the first passage when the flow rate of the refrigerant is less than the maximum.
The piston type compressor is characterized in that the first edge portion is located on the trailing side in the rotational direction with respect to the second edge portion. The drive shaft is formed with a guide window for arranging the moving body so as to be movable in the direction of the drive axis.
The moving body has a first moving body arranged in the guide window and a second moving body arranged in the drive shaft while the second continuous passage is formed.
The first moving body communicates the first communication passage with the second communication passage.
The piston type compressor according to claim 1, wherein the first communication passage and the second communication passage are not communicated with each other by the drive shaft. The piston type compressor according to claim 1 or 2, wherein the first edge portion and the second edge portion are continuous while gradually changing in the rotation direction. The piston type compressor according to claim 1 or 2, wherein the first edge portion and the second edge portion have a step and are continuous.

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