KR20190114813A - Piston compressor - Google Patents

Abstract

Provided is a piston compressor capable of rapidly decreasing a flow rate of a refrigerant discharged from a compression chamber to a discharge chamber. The compressor of the present invention includes a rotating body (15). The rotating body (15) is provided on a drive shaft (3) and is rotatable integrally with the drive shaft and movable based on a control pressure (Pc) in a direction of a drive shaft axis (O) of the drive shaft (3). Also, the rotating body (15) has a second communication passage (15d) that communicates with respective first communication passages (29a to 29f) intermittently by rotation of the drive shaft (3). In accordance with a position in the direction of the drive shaft axis (O) of the rotating body (15), a communication angle around the drive shaft axis (O) through which the first communication passages (29a to 29f) and the second communication passage (15d) communicate with each other per one rotation of the drive shaft. The compressor further includes an elastic support member (43) that elastically supports the rotating body (15) to a control pressure chamber (37) side. Between the rotating body (15) and the drive shaft (3), formed is a compression chamber (33) that elastically supports the rotating body (15) to the control pressure chamber (37) side when an internal pressure is higher than the control pressure (Pc).

Description

Piston Compressor {PISTON COMPRESSOR}

The present invention relates to a piston compressor.

Patent documents 1-3 disclose a conventional piston compressor. These compressors are provided with a housing, a drive shaft, a fixed swash plate, a plurality of pistons, a discharge valve, and a control valve.

The housing has a cylinder block in which a plurality of cylinder bores and a first communication path communicating with the cylinder bore are formed. Moreover, the discharge chamber, the swash plate chamber, the control pressure chamber, and the axial hole are formed in the housing. The swash plate chamber may also serve as the suction chamber, or an in-axis passage communicating with the suction chamber formed in the housing may be formed in the drive shaft.

The drive shaft is rotatably supported in the shaft hole. The fixed swash plate is rotatable 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 the fixed swash plate. Between the compression chamber and the discharge chamber, a reed valve type discharge valve for discharging the refrigerant in the compression chamber to the discharge chamber is formed.

In these compressors, a rotating body integral with or separate from the drive shaft is formed in the shaft hole. The rotating body rotates integrally with the drive shaft and is movable in the direction of the drive shaft center of the drive shaft by the pressure difference between the control pressure and the suction pressure controlled by the control valve. The rotating body is provided with the 2nd communication path which communicates with a 1st communication path intermittently with rotation of a drive shaft. The second communication path is formed such that the communication angle around the drive shaft center with the first communication path changes depending on the position in the drive shaft center direction of the rotating body.

These rotation bodies communicate with a 1st communication path and a 2nd communication path by the position of the rotation axis direction of a rotation body. For this reason, the refrigerant in the swash plate chamber or the suction chamber is sucked into the compression chamber via the second communication path and the first communication path. At this time, since the communication angle around the drive shaft center of a 2nd communication path and a 1st communication path changes, the flow volume of the refrigerant | coolant suctioned in a compression chamber changes, and the flow volume of the refrigerant discharged from a compression chamber to a discharge chamber changes. In this way, these compressors attempt to realize a simplification of the structure as compared with a compressor whose capacity is changed by changing the inclination angle of the swash plate.

Japanese Patent Laid-Open No. 5-306680 Japanese Patent Laid-Open No. 5-312145 Japanese Laid-Open Patent Publication No. 7-119631

However, in the conventional compressor, the compression load acts on the outer circumferential surface of the rotating body from the first communication path communicating with the compression chamber during the compression stroke. For this reason, the rotating body is pressurized in the direction orthogonal to the driving shaft center direction in the shaft hole, and the rotating body is hard to move in the driving shaft center direction. For this reason, the responsiveness of the rotating body is poor with respect to the change of the control pressure by the control valve, and it is difficult to quickly reduce the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-described conventional situation, and has been made to solve the problem of providing a piston compressor capable of rapidly reducing the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber.

The piston compressor of the present invention has a cylinder block in which a plurality of cylinder bores are formed, a discharge chamber, a swash plate chamber, a control pressure chamber, a housing in which shaft holes are formed,

A drive shaft rotatably supported in the shaft hole,

A fixed swash plate which is rotatable in the swash plate chamber by the rotation of the drive shaft and has a constant inclination angle with respect to a plane perpendicular to the drive shaft;

A piston formed in the cylinder bore and connected to the fixed swash plate;

A discharge valve for discharging the refrigerant sucked in the compression chamber to the discharge chamber;

A control valve capable of controlling the control pressure of the control pressure chamber;

A first communication path formed in the cylinder block and communicating with the cylinder bore;

A first shaft formed on the drive shaft, integrally rotating with the drive shaft, movable in the direction of the drive shaft center of the drive shaft based on the control pressure, and intermittently communicating with the first communication path with rotation of the drive shaft; It is provided with the rotating body in which two communication paths were formed,

By the position of the said rotating body in the said drive shaft center direction, the communication angle around the said drive shaft core which the said 1st communication path and the said 2nd communication path communicates per 1 rotation of the said rotating body changes, and discharges from the said compression chamber. A piston compressor in which the flow rate of the refrigerant to be changed is

Further provided with an elastic support member for elastically supporting the rotating body toward the control pressure chamber side,

The pressure storage chamber is formed between the rotating body and the drive shaft to elastically support the rotating body toward the control pressure chamber side when an internal pressure is higher than the control pressure.

In the compressor of the present invention, the elastic support member elastically supports the rotating body in the direction of the drive shaft in the direction in which the flow rate of the refrigerant decreases. In addition, the pressure storage chamber formed between the drive shaft and the rotating body elastically supports the rotating body in the direction of the driving shaft in a direction in which the flow rate of the coolant decreases when the accumulated pressure therein is higher than the control pressure.

For this reason, in this compressor, even if the rotating body is pressurized in the direction orthogonal to the direction of the drive shaft in the shaft hole, the rotating body is assisted by the elastic force of the pressure difference between the elastic support member and the pressure storage chamber and the control pressure chamber. It is possible to move quickly in the direction of the drive shaft in the direction of decreasing the flow rate of the refrigerant. In this way, the response of the rotating body in the direction in which the flow rate decreases with respect to the change of the control pressure by the control valve is improved, and the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber can be reduced quickly.

Therefore, in the compressor of the present invention, the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber can be reduced quickly.

The drive shaft is integral with the small diameter portion and the small diameter portion, and may have a large diameter portion larger in diameter than the small diameter portion. The rotating body may have an inner flange through which the small diameter portion is inserted, and a tubular portion extending from the radially outer side of the inner flange in the driving axis direction and accommodating a portion of the large diameter portion. The pressure storage chamber may be formed of an inner flange, a tube portion, a small diameter portion, and a large diameter portion. And when the rotating body most moves to the small diameter part side, it is preferable that the edge part of the cylinder part opposite to a flange is located in the radially outer side of a large diameter part. In this case, the accumulator chamber is easily formed in the compressor, and the compactness of the compressor can be realized.

It is preferable that the control pressure chamber and the pressure storage chamber communicate with each other through the narrow passage. In this case, it is not necessary to form a sealing member between the control pressure chamber and the pressure storage chamber, and the part number can be reduced.

When the control pressure chamber and the pressure storage chamber are communicated through the narrow passage, the narrow passage may be formed by the small diameter portion and the inner flange. In this case, the narrow passage is easily formed in the compressor, and the compactness of the compressor can be realized.

In the accumulator chamber, a left seat inserted into the small diameter portion and a second elastic support member for elastically supporting the left seat to the control pressure chamber side can be formed. The narrow passage may include a first passage formed of an inner flange and a small diameter portion, and a seat and a small diameter portion, and may have a second diameter smaller than the first passage. In this case, by selecting the seat, the flow path area of the second passage can be made small so that the accumulated pressure in the pressure storage chamber can act on the rotating body for a long time.

The rotating body may have a first communication path in which the piston communicates with the compression chamber located at the top dead center of the piston, and a pressure passage in communication with the pressure storage chamber. In this case, since the high pressure refrigerant remaining in the compression chamber can be supplied into the pressure storage chamber, the effective use of the residual high pressure refrigerant can be performed.

In the compressor of the present invention, the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber can be rapidly reduced.

1 is a cross-sectional view of the piston compressor of Example 1, showing a state where the discharge flow rate is maximum.
2 is a cross-sectional view of the piston compressor of the first embodiment, showing a state where the discharge flow rate is minimum.
FIG. 3 is a developed view of a rotating body relating to the piston compressor of the first embodiment and showing the trajectory and the like of the first communication path in the state of FIG. 1.
4 is an exploded view of a rotating body relating to the piston compressor of the first embodiment and showing the trajectory and the like of the first communication path in the state of FIG. 2.
FIG. 5 is a sectional view of principal parts of a piston compressor of Embodiment 1 in a state where the discharge flow rate is maximum. FIG.
FIG. 6 is a sectional view of an essential part of a piston compressor of Embodiment 1 in a state where discharge flow rate is minimum. FIG.
7 is a sectional view of principal parts of a piston compressor of Example 2 in a state where the discharge flow rate is maximum.
8 is a sectional view of principal parts of a piston compressor of Example 2 in a state where the discharge flow rate is minimum.

EMBODIMENT OF THE INVENTION Hereinafter, Example 1, 2 which actualized this invention is described, referring drawings.

 (Example 1)

As shown in FIGS. 1 and 2, the piston compressor of the first embodiment has a housing 1, a drive shaft 3, a fixed swash plate 5, and six pistons 7 (FIGS. 3 and 4). Reference), a discharge valve 11, a control valve 13, and a rotating body 15.

The housing 1 has a front housing 17, a cylinder block 19, and a rear housing 21. The front housing 17 side is the front of the compressor, the rear housing 21 side is the rear of the compressor, and the upper and lower parts of the compressor are defined as shown in FIGS. 1 and 2.

The front housing 17 and the cylinder block 19 are fastened to each other, and the swash plate chamber 23 is formed between them. In the rear housing 21, the suction chamber 21a is formed in the center, and the annular discharge chamber 21b is formed in the outer peripheral side of the suction chamber 21a. The swash plate chamber 23 communicates with the suction chamber 21a by a passage not shown. The rear housing 21 is provided with a suction port 21c for opening the suction chamber 21a to the outside and a discharge port 21d for opening the discharge chamber 21b to the outside.

The cylinder block 19 and the rear housing 21 are fastened to each other with the valve unit 25 between them. Six cylinder bores 19a to 19f (see FIGS. 3 and 4) are formed in the cylinder block 19 to penetrate back and forth. As shown in FIG. 1 and FIG. 2, the cylinder block 19 extends through the valve unit 25 and into the rear housing 21. The front housing 17 and the cylinder block 19 are formed with shaft holes 27 extending in the direction of the drive shaft center O of the drive shaft 3. The shaft hole 27 is changed into the small hole 27a located in the front housing 17 and the small hole 27a in the cylinder block 19, and consists of the large hole 27b of larger diameter than the small hole 27a. The large hole 27b communicates with the suction chamber 21a in the rear housing 21. The cylinder block 19 has a supporting wall 19g between the swash plate chamber 23 and the large hole 27b.

The cylinder blocks 19 are formed from the cylinder bores 19a to 19f toward the drive shaft center O, and the first communication paths 29a to 29f communicating with the large holes 27b are formed. The first communication paths 29a to 29f are inclined forward from the position closest to the valve unit 25 as the drive shaft center O approaches.

The drive shaft 3 is rotatably supported in the shaft hole 27. The drive shaft 3 is located in the front hole and is supported by the front housing 17 and is integrally formed with the large diameter portion 3a into which the fixed swash plate 5 is pressed and the large diameter portion 3a, and is located in the large hole 27b. It consists of the small diameter part 3b of a smaller diameter than the large diameter part 3a, and extends to the rear end integrally with the small diameter part 3b, and consists of the large diameter part 3a and the large diameter part 3c of the same diameter. In short, the small diameter portion 3b is located between the large diameter portion 3a and the large diameter portion 3c.

This drive shaft 3 prepares the 1st axis | shaft which forms the large diameter part 3a, and the 2nd axis | shaft which forms the small diameter part 3b and the large diameter part 3c, and forms a press fit hole in a 1st axis | shaft, It manufactures by pressing a part of small diameter part 3b into a press-in hole. The drive shaft 3 has a sliding layer (not shown) on the outer circumferential surface except for the portion where the fixed swash plate 5 is press-fitted, and the large diameter portion 3a is directly supported by the front housing 17 and the cylinder block 19. It is. A shaft rod device 31 is formed between the front housing 17 and the drive shaft 3. The axial rod device 31 seals the inside and the outside of the housing 1.

The rotating body 15 is formed in the large hole 27b of the shaft hole 27. As shown in FIG. 5 and FIG. 6, the rotating body 15 has a drive shaft core from an inner flange 15a through which the small diameter portion 3b of the drive shaft 3 is inserted and a radially outer side of the inner flange 15a. It extends in the (O) direction and has the cylinder part 15f which accommodates a part of large diameter part 3c. As for the cylinder part 15f, the front end side of the drive shaft center O direction is divided by the inner flange 15a, accommodates the large diameter part 3c of the drive shaft 3, and drives the outer peripheral surface of the large diameter part 3c by the drive shaft center. The storage chamber 15b which slides in the (O) direction is formed. The pressure storage chamber 33 is formed by the rear surface of the inner flange 15a, the inner circumferential surface of the cylinder portion 15f, the outer circumferential surface of the small diameter portion 3b, and the front surface of the large diameter portion 3c. In the pressure storage chamber 33, the 1st spring 43 which makes the back surface of the inner side flange 15a and the front surface of the large diameter part 3c the left surface is formed. The first spring 43 corresponds to the elastic support member of the present invention.

Moreover, the narrow passage 35 is formed by the small diameter part 3b and the inner flange 15a. The opening area of the narrow passage 35 is sufficiently smaller than the opening area in which the control passage 13c described later is opened in the control pressure chamber 37. A sliding layer (not shown) is also formed on the outer circumferential surface of the rotating body 15.

The control pressure chamber 37 is formed by the rear surface of the support wall 19g, the inner circumferential surface of the large hole 27b, the front surface of the rotating body 15, the outer circumferential surface behind the large diameter portion 3a, and the outer circumferential surface of the small diameter portion 3b. ) Is formed. In the control pressure chamber 37, the end part 3d which the large diameter part 3a and the small diameter part 3b of the drive shaft 3 make is located. This end part 3d regulates a position when the rotating body 15 moves forward in the direction of the drive shaft center O. As shown in FIG.

In the large diameter part 3c of the drive shaft 3, the outer spline 3e extended in the drive shaft center O direction, and the cylindrical surface 3f located behind the outer spline 3e are formed. On the inner circumferential surface forming the housing chamber 15b of the rotating body 15, an inner spline 15c extending in the direction of the drive shaft center O and engaging with the outer spline 3e is formed. The rotating body 15 is rotatable with the drive shaft 3 in the large hole 27b by the outer spline 3e and the inner spline 15c, and is movable to the drive shaft center O direction. Even if the rotating body 15 moves in the direction of the drive shaft center O, the cylindrical surface 3f is in sliding contact with the inner circumferential surface of the storage chamber 15b, and the accumulated pressure Pa in the pressure storage chamber 33 is cylindrical surface 3f. It is hard to leak on the side.

As shown in FIG. 3 and FIG. 4, the recessed part 15d is recessed in the outer peripheral surface of the rotating body 15. The recessed part 15d is opened to the rear end of the rotating body 15 and communicates with the suction chamber 21a by the large hole 27b of the shaft hole 27. Moreover, the width | variety of the circumference | surroundings of the drive shaft center O is narrow in the recessed part 15d in front of the rotation body 15, and the width is long in the rear. The recessed portion 15d corresponds to the second communication path.

Moreover, as shown to FIG. 5 and FIG. 6, the rotating body 15 is provided with the pressure passage 15e. The outer end of the pressure passage 15e is opened to the outer circumferential surface of the rotating body 15, and the inner end of the pressure passage 15e is opened to the pressure storage chamber 33. As shown in FIGS. 3 and 4, the pressure guiding passage 15e is a first communication path with rotation of the driving shaft 3 regardless of the position in the direction of the driving shaft center O of the rotating body 15. 29a to 29f).

5 and 6, the circlip 41 is fitted behind the large diameter portion 3c of the drive shaft 3. The circlip 41 restricts the position when the rotating body 15 moves backward in the direction of the drive shaft center O. As shown in FIG.

As shown in FIG. 1 and FIG. 2, the fixed swash plate 5 is pushed into and fixed to the large diameter portion 3a of the drive shaft 3. A thrust bearing 45 is formed between the front housing 17 and the fixed swash plate 5. The inclination angle which the fixed swash plate 5 makes with respect to the surface orthogonal to the drive shaft center O direction is constant.

The piston 7 is formed in the cylinder bores 19a to 19f. The piston 7 forms the compression chamber 47 in the cylinder bores 19a to 19f. A recess 7a is formed in the front part of the piston 7, and a hemispherical shoe 49 is formed between the front and rear surfaces of the recess 7a and the fixed swash plate 5, respectively. The piston 7 is connected to the fixed swash plate 5 by the shoe 49.

As for the valve unit 25, the retainer 25a, the discharge reed valve 25b, and the valve plate 25c are laminated | stacked in this order. The retainer 25a is located on the rear housing 21 side. When the discharge reed valve 25b is opened, the valve plate 25c is provided with a discharge port 25f for communicating the discharge chamber 21b with the compression chamber 47. The valve unit 25 and the discharge port 25f constitute the discharge valve 11.

The control valve 13 is formed in the rear housing 21. The control valve 13 and the suction chamber 21a are connected by the low pressure passage 13a, the control valve 13 and the discharge chamber 21b are connected by the high pressure passage 13b, and the control valve 13 and The control pressure chamber 37 is connected by the control passage 13c. The low pressure passage 13a and the high pressure passage 13b are formed in the rear housing 21, and the control passage 13c is formed in the rear housing 21 and the cylinder block 19. By detecting the suction pressure Ps in the suction chamber 21a, the control valve 13 adjusts the valve opening degree, and controls the pressure in the control pressure chamber 37 by the discharge pressure Pd in the discharge chamber 21b. Pc) can be controlled. In addition, the control pressure chamber 37 can reduce the control pressure in the control pressure chamber 37 by the bleeding passage which is not shown in figure. The control valve 13 supplies to the control passage 13c the refrigerant | coolant of the control pressure Pc which becomes the discharge pressure Pd at the maximum.

This compressor is used in the vehicle air conditioning system. When the drive shaft 3 is driven by an engine or a motor, the fixed swash plate 5 rotates by the drive shaft 3 in the swash plate chamber 23. Therefore, the piston 7 moves from the bottom dead center of the piston 7 to the top dead center of the piston 7, and also moves from the top dead center to the bottom dead center. In addition, below, the top dead center of the piston 7 and the bottom dead center of the piston 7 are described as top dead center and bottom dead center, respectively.

1 and 5, when the control valve 13 supplies the high pressure control pressure Pc to the control pressure chamber 37 by the control passage 13c, the rotor 15 is It is located in the rear end which abuts against the circlip 41 against the elastic force of the 1st spring 43. As shown in FIG. In this state, as shown in FIG. 3, when the piston 7 moves from a top dead center to a bottom dead center, the compression chamber 47 has the volume expanded, for example. Since the first communication paths 29b and 29c communicating with the compression chamber 47 are communicated with the recessed portions 15d of the rotating body 15, the compression holes 47 have a large hole ( Through the 27b), the refrigerant of the suction pressure Ps is sucked from the suction chamber 21a.

In the meantime, as seen from the rotating body 15, the 1st communication path 29a-29f moves according to rotation of the drive shaft 3 and the rotating body 15. As shown in FIG. For this reason, the first communication paths 29a to 29f and the concave portion 15d per rotation of the rotating body 15 are intermittently driven along the rotation of the driving shaft 3 and the rotating body 15 ( O) It communicates with the communication angle (theta) 1 around it.

And when the piston 7 moves from a bottom dead center to a top dead center, the compression chamber 47 will reduce a volume. For this reason, when the pressure in the compression chamber 47 becomes higher than the discharge chamber 21b, the discharge reed valve 25b will open and the discharge chamber 21b will communicate with the compression chamber 47, and from the compression chamber 47 The refrigerant of the discharge pressure Pd is discharged to the discharge chamber 21b. For this reason, in this state, the compressor has the maximum flow rate of the refrigerant discharged from the compression chamber 47 per rotation of the drive shaft 3 to the discharge chamber 21b. In addition, the refrigerant passing through the evaporator is supplied from the suction port 21c to the suction chamber 21a. The refrigerant in the discharge chamber 21b is discharged to the condenser via the discharge port 21d.

In this state, as shown in FIG. 2 and FIG. 6, the control valve 13 does not supply the high pressure control pressure Pc to the control pressure chamber 37 by the control passage 13c, and thus the control pressure chamber 37. When the internal control pressure Pc becomes low gradually, the rotating body 15 will bend to the elastic force of the 1st spring 43, and will be located in the front end contacting the edge part 3d. In this way, when the rotating body 15 moves to the small diameter part 3b side most, the edge part on the opposite side to the inner flange 15a of the cylinder part 15f is located in the radial direction outer side of the large diameter part 3c.

In this state, as shown in FIG. 4, the compression chamber 47 moves not only while the piston 7 moves from the top dead center to the bottom dead center and the volume is enlarged, and the piston 7 is fixed from the bottom dead center. Even if it moves to and the volume starts to shrink, the 1st communication paths 29b-29e are in communication with the recessed part 15d of the rotating body 15. As shown in FIG. For this reason, the compression chamber 47 sucks the refrigerant | coolant of suction pressure Ps from the suction chamber 21a through the large hole 27b of the axial hole 27, but compresses the refrigerant | coolant with reduction of a volume. It is refluxed upstream of the chamber 47.

In the meantime, the 1st communication path 29a-29f and the recessed part 15d per rotation of the rotating body 15 are accompanied by the rotation of the drive shaft 3 and the rotating body 15, and the rotating body 15 By intermittent position of the drive shaft center O, it is intermittently connected by the communication angle (theta) 2 around the drive shaft center O. As shown in FIG. In addition, the communication angle θ2 is larger than the communication angle θ1.

And when the piston 7 moves from a fixed position to top dead center, the compression chamber 47 will reduce a volume. For this reason, when the pressure in the compression chamber 47 becomes higher than the discharge chamber 21b, the refrigerant | coolant of discharge pressure Pd is discharged from the compression chamber 47 to the discharge chamber 21b. At this time, since only a small amount of refrigerant is sucked into the compression chamber 47, only a small amount of refrigerant is discharged into the discharge chamber 21b in the compression chamber 47. For this reason, in this state, the compressor has the minimum flow rate of the refrigerant discharged from the compression chamber 47 to the discharge chamber 21b.

In the meantime, also in this compressor, a compression load acts on the outer peripheral surface of the rotating body 15 from the 1st communication paths 29a-29f which communicate with the compression chamber 47 in a compression stroke, and the rotating body 15 makes a shaft hole. It is pressed in the direction orthogonal to the drive shaft center O direction in 27.

However, in this compressor, as shown to FIG. 5 and FIG. 6, the 1st spring 43 elastically rotates the rotating body 15 to the left direction along the drive shaft center O, in other words, the direction in which the flow volume of a refrigerant | coolant decreases. I support it.

In addition, the compression chamber 47 in which the piston 7 is located at the top dead center has a minimum volume. As shown in FIG. 3 and FIG. 5, for example, the 1st communication path 29a which communicates with this compression chamber 47 communicates with the pressure passage 15e, and is the high pressure remaining in the compression chamber 47, for example. The coolant is supplied into the accumulator chamber 33. As shown to FIG. 4 and FIG. 6, even if the rotating body 15 moved to the left direction along the drive shaft center O, the 1st communication path 29a which communicates with this compression chamber 47 is a pressure passage ( In communication with 15e), the high pressure refrigerant remaining in the compression chamber 47 is supplied into the pressure storage chamber 33. For this reason, in the accumulator chamber 33, the internal accumulation pressure Pa is higher than the control pressure Pc of the control pressure chamber 37.

For this reason, when the control valve 13 makes the control pressure Pc in the control pressure chamber 37 low, the refrigerant | coolant of the pressure difference of V-Pc will flow from the accumulator chamber 33 through the narrow passage 35 to the control pressure chamber 37 ) Flows slowly. Therefore, the rotor 15 is elastically supported in the left direction along the drive shaft center O, that is, in the direction in which the flow rate of the refrigerant decreases.

For this reason, in this compressor, even if the rotating body 15 is pressed in the direction orthogonal to the drive shaft center O direction in the shaft hole 27, the rotating body 15 is assisted by the assist based on said elastic force. , It is possible to move quickly in the left direction along the drive shaft center O, that is, in the direction in which the flow rate of the coolant decreases. In this way, with respect to the change of the control pressure Pc by the control valve 13, the responsiveness of the rotating body 15 in the direction of decreasing flow rate improves, and the discharge chamber 21b is discharged from the compression chamber 47. The flow rate of the refrigerant discharged into the furnace can be reduced quickly.

In this compressor, since the capacity is not changed by changing the inclination angle of the fixed swash plate 5, the structure can be simplified.

Therefore, in this compressor, the flow volume of the refrigerant discharged from the compression chamber 47 to the discharge chamber 21b can be rapidly reduced while realizing the structure and the like.

Moreover, in this compressor, the pressure storage chamber 33 is formed around the small diameter part 3b of the drive shaft 3, and the narrow passage part 35b is formed by the small diameter part 3b and the inner flange 15a. It is easy to form the pressure storage chamber 33 and the narrow passage 35 in the compressor, and the compactness and cost reduction of the compressor can be realized. In this compressor, the flow rate of the refrigerant decreases in the rotating body 15 due to the difference between the accumulated pressure Pa of the pressure storage chamber 33 and the control pressure Pc of the control pressure chamber 37, that is, the rotating body. Since the 15 is elastically supported toward the control pressure chamber 37 side, the first spring 43 can be downsized, and in this sense, downsizing and inexpensiveness can be realized.

In this compressor, since the pressure passage 15e of the rotating body 15 supplies the high pressure refrigerant remaining in the compression chamber 47 into the pressure storage chamber 33, effective utilization of the residual high pressure refrigerant can be performed. Can be. Moreover, since the refrigerant | coolant of the accumulating pressure Pa in the accumulator chamber 33 flows into the control pressure chamber 37 via the narrow passage 35, it is easy to maintain the control pressure chamber 37 at control pressure Pc stably.

(Example 2)

As shown in FIG. 7 and FIG. 8, the compressor of the second embodiment does not form the same pressure passage 15e as that of the first embodiment in the rotating body 15. On the other hand, the seat 51 and the second spring 53 are formed in the pressure storage chamber 33.

The seat 51 is inserted through the small diameter portion 3b of the drive shaft 3. The inner diameter of the seat 51 is smaller than the inner diameter of the inner flange 15a. The second spring 53 elastically supports the seat 51 in a direction in which the pressure storage chamber 33 is enlarged. The second spring 53 corresponds to the second elastic support member. The first passage 55a is formed by the inner flange 15a and the small diameter portion 3b, and the second passage 55b is formed by the seat 51 and the small diameter portion 3b. As shown in FIG. 7, when the seat 51 is separated from the inner flange 15a, the third passage 55c is formed by the inner flange 15a and the seat 51. These first to third passages 55a to 55c are narrow passages 55. The other configuration is the same as that of the first embodiment.

In this compressor, when the control valve 13 supplies the high pressure control pressure Pc to the control pressure chamber 37 by the control passage 13c, the rotor 15 contacts the circlip 41 at the rear end. Located in In this state, the compressor has the maximum flow rate of the refrigerant discharged from the compression chamber 47 per rotation of the drive shaft 3 to the discharge chamber 21b.

At this time, the high pressure refrigerant in the control pressure chamber 37 is supplied to the pressure storage chamber 33 via the first and second passages 55a and 55b. In addition, when the seat 51 is separated from the inner flange 15a in response to the elastic force of the second spring 53, the high pressure refrigerant in the control pressure chamber 37 passes through the third passage 55c and accumulates the pressure storage chamber 33. Supplied to. For this reason, the accumulator chamber 33 quickly maintains an internal accumulation pressure Pa at the same pressure as the control pressure Pc of the control pressure chamber 37.

In this state, as shown in FIG. 8, the control valve 13 does not supply the high pressure control pressure Pc to the control pressure chamber 37 by the control passage 13c, and thus the control pressure in the control pressure chamber 37. When Pc becomes low gradually, the refrigerant | coolant of the pressure difference of V-Pc flows gradually from the accumulator chamber 33 to the control pressure chamber 37 via the 1st, 2nd channel 55a, 55b. In this way, the rotor 15 is located at the front end. In this state, the compressor has a minimum flow rate of the refrigerant discharged from the compression chamber 47 to the discharge chamber 21b.

In this case, compared with the compressor of the first embodiment, the parts of the seat 51 and the second spring 53 increase, but by selecting the seat 51 the flow path area of the second passage 55b is made small, The accumulation pressure Pa in the pressure storage chamber 33 can act on the rotating body 15 for a long time. Other operational effects are the same as in Example 1.

As mentioned above, although this invention was demonstrated based on Example 1, 2, this invention is not limited to the said Example 1, 2, It can be said that it can change suitably and apply it in the range which does not deviate from the meaning. There is no need.

For example, in the compressor of the said Example 1, 2, although the suction chamber 21a was formed separately from the swash plate chamber 23, the swash plate chamber may also serve as the suction chamber.

An O ring may be formed between the drive shaft 3 and the rotating body 15 to prevent the control pressure chamber 37 from communicating with the pressure storage chamber 33.

The suction refrigerant may be supplied to the compression chamber 47 from the second communication path only while the piston 7 moves from the top dead center to the bottom dead center.

The direction of the rotating body 15 may be reversed back and forth. In this case, the control pressure chamber is formed in the rear housing 21.

The pressure storage chamber is not limited to the one formed between the rotating body and the drive shaft like the compressors of the first and second embodiments. For example, when the rotating body is arrange | positioned in the front-back direction opposite to Example 1, 2, and the control pressure chamber is formed in the rear housing, a pressure storage chamber is integrally formed in the rear side of a rotating body, and it is between the pressure storage chamber and the control pressure chamber. A narrow passage may be formed.

In the first embodiment, the valve opening degree of the capacity control valve 13 is adjusted to control the amount of the refrigerant introduced into the control pressure chamber 37 from the discharge chamber 21b through the high pressure passage 13b. Although the so-called "entrance control" which controls the control pressure Pc was implemented, it is not limited to this, The valve opening degree of the capacity | capacitance control valve 13 is adjusted, and the bleeding passage is opened from the control pressure chamber 37. By controlling the discharge amount of the refrigerant discharged into the suction chamber 21a through this, a so-called "outlet control" that controls the pressure in the control pressure chamber 37 may be implemented.

You may apply this invention to a wobble compressor.

The present invention can be used for an air conditioner of a vehicle.

19a to 19f... Cylinder bore
21b... Discharge chamber
23... A judge's office
37... Control chamber
27... Axes
One… Housing (17… front housing, 19… cylinder block, 21… rear housing)
3... driving axle
5... Fixed swash plate
47... Compression chamber
7... piston
11... Discharge valve
Pc… Control pressure
13... Control valve
29a to 29f... 1st communication path
O… Driving shaft
15d... 2nd communication path (concave)
15... Rotating body
θ1, θ2... Communication angle
43.. Elastic support member (first spring)
33.. Accumulator
3b... Small neck
3a, 3c... The great neck
15a... Inner flange
15f... Tube
35, 55... Narrow passage
51... Leftover
53... Second elastic support member (second spring)
55a... First passage
55b... 2nd passage
15e... Overpass

Claims (6)

A housing having a cylinder block in which a plurality of cylinder bores are formed, a discharge chamber, a swash plate chamber, a control pressure chamber, and a shaft hole;
A drive shaft rotatably supported in the shaft hole,
A fixed swash plate which is rotatable in the swash plate chamber by the rotation of the drive shaft and has a constant inclination angle with respect to a plane perpendicular to the drive shaft;
A piston formed in the cylinder bore and connected to the fixed swash plate;
A discharge valve for discharging the refrigerant sucked in the compression chamber to the discharge chamber;
A control valve capable of controlling the control pressure of the control pressure chamber;
A first communication path formed in the cylinder block and communicating with the cylinder bore;
A first shaft formed on the drive shaft, integrally rotating with the drive shaft, movable in the direction of the drive shaft center of the drive shaft based on the control pressure, and intermittently communicating with the first communication path with rotation of the drive shaft; It is provided with the rotating body in which two communication paths were formed,
By the position of the said rotating body in the said drive shaft center direction, the communication angle around the said drive shaft core which the said 1st communication path and the said 2nd communication path communicates per 1 rotation of the said rotating body changes, and discharges from the said compression chamber. A piston compressor in which the flow rate of the refrigerant to be changed is
Further provided with an elastic support member for elastically supporting the rotating body toward the control pressure chamber side,
And a pressure storage chamber for elastically supporting the rotation body to the control pressure chamber side when an internal pressure is higher than the control pressure between the rotation body and the drive shaft. The method of claim 1,
The drive shaft is integral with the small diameter portion and the small diameter portion, and has a large diameter portion larger in diameter than the small diameter portion,
The rotating body has an inner flange through which the small diameter portion is inserted, and a tubular portion extending from the radially outer side of the inner flange in the drive shaft center direction to accommodate a portion of the large diameter portion,
The pressure storage chamber is formed of the inner flange, the tubular portion, the small diameter portion, and the large diameter portion,
When the said rotor is moved to the said small diameter part side, the piston type compressor characterized by the edge part on the opposite side to the said inner side flange of the said cylinder part being located in the radially outer side of the said large diameter part. The method according to claim 1 or 2,
And the control pressure chamber and the pressure storage chamber communicate with each other through a narrow passage. The method of claim 2,
The control pressure chamber and the pressure storage chamber are communicated through the narrow passage,
A piston compressor, wherein the narrow passage is formed by the small diameter portion and the inner flange. The method of claim 4, wherein
In the accumulator chamber, a left ear inserted into the small diameter portion and a second elastic support member for elastically supporting the left arm toward the control pressure chamber side are formed.
The narrow passage is a piston compressor having a first passage formed of the inner flange and the small diameter portion, and the left portion and the small diameter portion, and having a second passage smaller than the first passage. The method according to claim 1 or 2,
The said rotary body has a piston type compressor which has the said 1st communication path which communicates with the said compression chamber located in the top dead center of the said piston, and the pressure passage which communicates with the said pressure storage chamber.

Images