JP2016191361A - Variable displacement type swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a variable displacement type swash plate compressor capable of quickly changing a discharge capacity, and capable of attaining excellent suction efficiency.SOLUTION: A variable displacement type swash plate compressor includes a partition body 45, a movable body 47, a control pressure chamber 49 and a control mechanism 51. A suction path 1k for taking in suction refrigerant from outside is opened to a swash plate chamber 1c. In a second cylinder block 1R, suction passages 1h communicating with each of second cylinder bores 1b are formed. In the movable body 47, an introduction passage 47e intermittently communicating between the swash plate chamber 1c and each suction passage 1h with rotation of the movable body 47 is formed.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a variable displacement swash plate compressor.

  Patent Document 1 discloses a conventional variable displacement swash plate compressor (hereinafter simply referred to as a compressor). The compressor includes a housing, a drive shaft, a swash plate, a link mechanism, and a plurality of pistons. The housing has a cylinder block, a front housing, and a rear housing. A plurality of cylinder bores are formed in the cylinder block, and a swash plate chamber is formed between the cylinder block and the front housing. The drive shaft is rotatably supported by the cylinder block and the front housing. A swash plate is disposed in the swash plate chamber, and the swash plate is rotated together with the drive shaft. A link mechanism having a lug plate is provided between the drive shaft and the swash plate. The link mechanism allows a change in the inclination angle of the swash plate with respect to the direction orthogonal to the rotational axis of the drive shaft. Each piston is housed in each cylinder bore and reciprocates with a stroke corresponding to the inclination angle by rotation of the swash plate to form a compression chamber in each cylinder bore. A front housing is joined to the front of the cylinder block, and a rear housing is joined to the rear of the cylinder block. The rear housing forms a suction chamber and a discharge chamber on the compression chamber side. Between the suction chamber and each compression chamber, a suction port and a suction valve that closes the suction port with an elastic force are provided. The rear housing is formed with a suction path for taking in the refrigerant into the suction chamber from the outside and a discharge path for discharging the refrigerant from the discharge chamber to the outside.

  The compressor also includes a control mechanism that controls the pressure in the swash plate chamber. The control mechanism includes a supply passage that communicates the swash plate chamber and the discharge chamber, a bleed passage that communicates the swash plate chamber and the suction chamber, and a capacity control valve that can change the opening degree of at least one of the supply passage and the bleed passage. And can have

  This compressor is used in an air conditioner such as a vehicle. When the drive shaft is rotationally driven, the compressor sucks the refrigerant in the suction chamber into each compression chamber, compresses the refrigerant in each compression chamber, and discharges the refrigerant in each compression chamber. And a discharge stroke to be discharged. At this time, if the control mechanism increases the pressure in the swash plate chamber, the back pressure acting on each piston in the swash plate chamber increases, and the inclination angle of the swash plate decreases. Conversely, if the control mechanism lowers the pressure in the swash plate chamber, the back pressure acting on each piston in the swash plate chamber decreases, and the inclination angle of the swash plate increases. Thus, this compressor realizes cooling of the passenger compartment or the like by the air conditioner with the capability according to the inclination angle.

JP 2004-225557 A

  However, in the above-described conventional compressor, the control mechanism controls the pressure in the swash plate chamber having a large volume, so that it is difficult to quickly change the pressure in the swash plate chamber, and it is difficult to change the inclination angle quickly. For this reason, this compressor cannot change discharge capacity rapidly, and it is difficult to realize coexistence with reduction of power consumption and a desired air-conditioning effect.

  For this reason, the partition body provided to rotate integrally with the drive shaft in the swash plate chamber, and the partition body can rotate integrally with the drive shaft in the swash plate chamber and move in the direction of the rotation axis with respect to the partition body. It is conceivable to provide a moving body that changes. Then, it is conceivable that the control pressure chamber is partitioned by the partition body and the moving body, and the moving body is moved by controlling the pressure in the control pressure chamber by the control mechanism. In this case, since it is sufficient for the control mechanism to control the pressure in the control pressure chamber having a smaller volume than the swash plate chamber, the pressure in the control pressure chamber can be easily changed quickly, and the inclination angle can be changed quickly. .

  However, in such a compressor, when the refrigerant is sucked into each compression chamber, each suction valve must open each suction port against an elastic force. Therefore, in that case, it is difficult to realize sufficient suction efficiency due to the power loss.

  The present invention has been made in view of the above-described conventional situation, and provides a variable displacement swash plate compressor capable of quickly changing the discharge capacity and realizing a higher suction efficiency. This is a problem to be solved.

The capacity variable swash plate compressor of the present invention includes a housing having a cylinder block in which a swash plate chamber, a discharge chamber and a plurality of cylinder bores are formed,
A drive shaft rotatably supported by the cylinder block;
A swash plate disposed in the swash plate chamber and rotated together with the drive shaft;
A link mechanism provided between the drive shaft and the swash plate, and allowing a change in the inclination angle of the swash plate with respect to a direction orthogonal to the rotational axis of the drive shaft;
A piston that is housed in each cylinder bore and reciprocates at a stroke according to the tilt angle by rotation of the swash plate to form a compression chamber in each cylinder bore;
A partition provided in the swash plate chamber so as to be integrally rotatable with the drive shaft;
A movable body that is integrally rotatable with the drive shaft in the swash plate chamber and that moves in the direction of the rotational axis relative to the partition body to change the tilt angle;
A control pressure chamber that is partitioned by the partition body and the moving body and moves the moving body by an internal pressure;
A control mechanism for controlling the pressure in the control pressure chamber,
A suction path for taking in refrigerant from outside opens into the swash plate chamber,
The cylinder block is formed with a suction passage communicating with each cylinder bore,
The moving body is formed with an introduction passage that intermittently communicates the swash plate chamber and each of the suction passages as the moving body rotates.

  In the variable displacement swash plate compressor of the present invention, the control mechanism only needs to control the pressure in the control pressure chamber having a smaller volume than the swash plate chamber, so that the pressure in the control pressure chamber can be easily changed quickly and the inclination angle can be quickly adjusted. Can be changed.

  Further, in this variable displacement swash plate compressor, the introduction passage of the moving body intermittently communicates the swash plate chamber and each suction passage as the moving body rotates. For this reason, the refrigerant taken into the swash plate chamber is sucked into each compression chamber in the suction stroke at that timing. For this reason, power loss can be reduced.

  Therefore, in the capacity variable swash plate compressor of the present invention, the discharge capacity can be changed quickly. For this reason, in this capacity variable type swash plate compressor, it is easy to realize both reduction in power consumption and a desired air conditioning effect. In addition, this variable capacity swash plate compressor can achieve better suction efficiency.

  In this variable displacement swash plate compressor, the moving body for changing the tilt angle also serves as the rotary valve. For this reason, it is not necessary to provide a separate rotary valve, and the structure can be simplified.

  Further, in this variable capacity swash plate compressor, the external suction refrigerant is first taken into the large-capacity swash plate chamber, so that suction pulsation can be easily suppressed.

  The moving body includes a high-pressure side opening that communicates with the compression chamber after completion of the discharge stroke with each rotation of the moving body via each suction passage, and a compression chamber that is in the suction stroke or in the compression stroke with the rotation of the moving body. It is preferable that a low-pressure side opening communicating with each other via each suction passage and a connection passage connecting the high-pressure side opening and the low-pressure side opening are formed.

  In this case, since the moving body can move the residual gas remaining in the compression chamber to the compression chamber during the suction stroke or the compression stroke, power loss due to re-expansion of the residual gas in the compression chamber can be reduced. Further, since it is not necessary to provide a residual gas bypass passage separately, simplification of the structure can be realized.

  Each cylinder bore may consist of a first cylinder bore located on one side of the rotational axis and a second cylinder bore located on the other side of the rotational axis. Each piston may have a first piston head located on one side of the rotational axis and a second piston head located on the other side of the rotational axis. Each compression chamber may consist of a first compression chamber formed by the first piston head in the first cylinder bore and a second compression chamber formed by the second piston head in the second cylinder bore. A first head member that forms a first discharge chamber on each first compression chamber side and a second head member that forms a second discharge chamber on each second compression chamber side can be joined to the cylinder block. Between the cylinder block and the first head member, there may be provided a first discharge valve that communicates each first compression chamber with the first discharge chamber by the pressure in each first compression chamber. Between the cylinder block and the second head member, there may be provided a second discharge valve for communicating each second compression chamber with the second discharge chamber by the pressure in each second compression chamber. The link mechanism may be arranged such that the top dead center position of the second piston head moves more greatly than the top dead center position of the first piston head in accordance with the change of the tilt angle. A first suction chamber may be formed in the first head member. It is preferable that a first suction valve is provided between the cylinder block and the first head member to communicate the first suction chamber and each first compression chamber against elastic force.

  In this case, the variable displacement swash plate compressor of the present invention is embodied as a variable displacement double-head swash plate compressor having a first suction valve on the first head member side and a rotary valve on the second head member side. Is done. In this capacity-variable double-headed swash plate compressor, the suction chamber does not necessarily have to be formed in the second head member. For this reason, it is necessary to provide a suction passage in the cylinder block for communicating the swash plate chamber with the suction chamber. Can be eliminated. For this reason, this capacity-variable double-headed swash plate compressor can avoid a suction pressure loss due to the suction passage when it is desired to reduce the size, and exhibits an excellent volumetric efficiency.

  With the variable displacement swash plate compressor according to the present invention, the discharge capacity can be changed quickly, and more excellent suction efficiency can be realized.

FIG. 1 is a longitudinal sectional view of a variable capacity double-headed swash plate compressor in a state where the inclination angle is maximum according to the first embodiment. FIG. 2 is a longitudinal sectional view of the variable capacity double-head swash plate compressor according to the first embodiment in a state where the inclination angle is minimum. FIG. 3 is a cross-sectional view of the variable capacity double-head swash plate compressor according to the first embodiment. FIG. 4 is a timing chart showing the relationship between the rotation angle of the rotary valve and each suction passage in the variable capacity double-head swash plate compressor according to the first embodiment. FIG. 5 is a graph showing a relationship between time and pressure in each compression chamber in the variable capacity double-headed swash plate compressor according to the first embodiment. FIG. 6 is an enlarged vertical cross-sectional view of a main part in the state where the inclination angle is maximum according to the first embodiment. FIG. 7 is an enlarged vertical cross-sectional view of a main part in the state where the inclination angle is minimum according to the first embodiment. FIG. 8 is a longitudinal sectional view of the variable capacity double-head swash plate compressor according to the second embodiment in a state where the inclination angle is maximum. FIG. 9 is an enlarged vertical cross-sectional view of a main part in the state where the inclination angle is maximum according to the second embodiment. FIG. 10 is an enlarged vertical cross-sectional view of a main part in the state where the inclination angle is minimum according to the second embodiment. FIG. 11 is a longitudinal sectional view of a variable capacity double-head swash plate compressor in the state where the inclination angle is maximum according to the third embodiment. FIG. 12 is a timing chart illustrating the relationship between the rotation angle of the rotary valve and each suction passage in the variable capacity double-head swash plate compressor according to the third embodiment. FIG. 13 is a graph showing a relationship between time and pressure in each compression chamber in the variable capacity double-head swash plate compressor according to the third embodiment.

  Embodiments 1 to 3 embodying the present invention will be described below with reference to the drawings.

Example 1
The variable capacity swash plate compressor (hereinafter simply referred to as a compressor) of the first embodiment is a double-headed compressor including first and second cylinder blocks 1F and 1R as shown in FIGS. . The compressor includes first and second cylinder blocks 1F and 1R, a drive shaft 3, a swash plate 5, a link mechanism 7, a plurality of pistons 9, a front housing 11, and a rear housing 13. The first and second cylinder blocks 1F and 1R, the front housing 11 and the rear housing 13 correspond to the housing of the present invention. Hereinafter, the front housing 11 side of the compressor is referred to as the front, and the rear housing 13 side of the compressor is referred to as the rear.

  The first cylinder block 1F and the second cylinder block 1R are joined together via a gasket (not shown), and a swash plate chamber 1c is formed by the first cylinder block 1F and the second cylinder block 1R. In the first cylinder block 1F, five first cylinder bores 1a parallel to each other are formed at equal angular intervals around the rotation axis O of the drive shaft 3. The same number of second cylinder bores 1b are formed in the second cylinder block 1R. Each first cylinder bore 1 a and each second cylinder bore 1 b are formed at the same position around the rotation axis O of the drive shaft 3.

  A front housing 11 is joined to the front end of the first cylinder block 1F via a first suction valve plate 6, a first valve plate 7, a first discharge valve plate 10 and a retainer plate 2a. The front housing 11 corresponds to the first head member of the present invention. The rear housing 13 is joined to the rear end of the second cylinder block 1R via the second valve plate 15, the second discharge valve plate 17, and the retainer plate 2b. The rear housing 13 corresponds to the second head member of the present invention. A suction valve plate such as the first suction valve plate 6 is not provided between the second cylinder block 1R and the second valve plate 15.

  A shaft hole 11a is formed in the front housing 11, and a shaft hole 1d and a large-diameter hole 1n coaxial with the shaft hole 11a are formed in the first cylinder block 1F. A shaft seal device 19 is provided in the shaft hole 11a, and a radial bearing 21 is provided in the shaft hole 1d. A first support member 3 p is press-fitted into the front portion of the drive shaft 3. A first flange 3c is formed on the first support member 3p. The thrust bearing 23 is provided between the first flange 3c and the first cylinder block 1F in the large-diameter hole 1n.

  The second cylinder block 1R is formed with a large-diameter hole 1e and a shaft hole 1f coaxial with the shaft holes 11a and 1d. A second support member 3q is press-fitted into the rear portion of the drive shaft 3. A second flange 3d is formed on the second support member 3q. A thrust bearing 25 and a radial bearing 27 are provided in the large-diameter hole 1e and the shaft hole 1f. The thrust bearing 27 is provided between the second flange 3d and the second cylinder block 1R.

  The drive shaft 3 is inserted into the shaft holes 11a, 1d, and 1f and the large-diameter holes 1n and 1e through the shaft seal device 19, the radial bearing 21, the thrust bearing 23, the thrust bearing 25, and the radial bearing 27, and rotates by these. It is supported as possible. The front of the drive shaft 3 is exposed from the front housing 11.

  The second cylinder block 1R is formed with a suction passage 1k for taking in the refrigerant into the swash plate chamber 1c. The suction path 1k is connected to an external evaporator (not shown) by piping. A swash plate 5 is disposed in the swash plate chamber 1c. In the swash plate chamber 1c, a lug arm 29 is provided on the first support member 3p so as to be rotatable around the first pin 31a. The rear part of the lug arm 29 is a weight part. A ring plate 5a is provided at the center of the lug arm 29 so as to be rotatable around the second pin 31b. The swash plate 5 is fixed to the ring plate 5a. The first and second pins 31a and 31b are orthogonal to the rotation axis O and extend parallel to each other. The lug arm 29, the ring plate 5a, and the first and second pins 31a and 31b constitute the link mechanism 7. The link mechanism 7 allows a change in the inclination angle of the swash plate 5 with respect to the direction orthogonal to the rotational axis O of the drive shaft 3. In particular, in this compressor, the link mechanism 7 causes the top dead center position of each second piston head 9b to move more greatly than the top dead center position of each first piston head 9a, which will be described later, as the inclination angle is changed. Is arranged. More specifically, the link mechanism 7 is configured such that the position in the direction of the rotational axis O at the top dead center in each first piston head 9a does not change regardless of the change in the tilt angle.

  Each piston 9 includes a first piston head 9a located on the front side, a second piston head 9b located on the rear side, and a neck portion 9c that integrally connects them. The first piston head 9a is housed in the first cylinder bore 1a, and the second piston head 9b is housed in the second cylinder bore 1b. Two shoes 33 are provided between the neck portion 9 c of each piston 9 and the swash plate 5. Therefore, each piston 9 reciprocates in each of the first and second cylinder bores 1a and 1b with a stroke corresponding to the inclination angle by the rotation of the swash plate 5, and the first and second cylinder bores 1a and 1b move in the first and Two compression chambers 35a and 35b are formed.

  In the front housing 11, a first suction chamber 11b is formed in an annular shape, and a second discharge chamber 11c is formed in an annular shape outside the first suction chamber 11b. A second discharge chamber 13 c is formed in the rear housing 13 in an annular shape. The rear housing 13 is formed with a pressure adjustment chamber 13d. The pressure adjustment chamber 13 d is located at the center portion of the rear housing 13. A partition wall around the pressure adjusting chamber 13d partitions the pressure adjusting chamber 13d and the second discharge chamber 13c, and the pressure adjusting chamber 13d is surrounded by the second discharge chamber 13c. The rear housing 13 is provided with a capacity control valve 37.

  The second cylinder block 1R, the second valve plate 15, the second discharge valve plate 17, the retainer plate 2b, and the rear housing 13 are formed with a low-pressure passage 39 that communicates the swash plate chamber 1c and the capacity control valve 37. The rear housing 13 is formed with a high-pressure passage 41 that communicates the capacity control valve 37 and the discharge chamber 13c, and an air supply passage 43 that communicates the capacity control valve 37 and the pressure adjustment chamber 13d.

  The first cylinder block 1F, the first suction valve plate 6, the first valve plate 7, the first discharge valve plate 10 and the retainer plate 2a extend in parallel with the rotation axis O, and the swash plate chamber 1c and the first suction chamber 11b. Are formed five passages 1g for suction. Each suction passage 1g is formed between the first cylinder bores 1a.

  The retainer plate 2a, the first discharge valve plate 10, and the first valve plate 7 are formed with a suction port 7a that communicates the first suction chamber 11b with each first compression chamber 35a. The first suction valve plate 6 is formed with a suction valve 6a that closes each suction port 7a by elastic force. Further, the first valve plate 7 and the first suction valve plate 6 are formed with discharge ports 7b that communicate the first discharge chamber 11c with the first compression chambers 35a. The first discharge valve plate 10 is formed with a first discharge valve 10a that closes each discharge port 7b by elastic force. The retainer plate 2a regulates the opening degree of each first discharge valve 10a.

  As shown in FIG. 3, a suction passage 1h for communicating each second cylinder bore 1b with the large-diameter hole 1e in the radial direction is formed behind the second cylinder block 1R. As shown in FIGS. 1 and 2, each suction passage 1h is inclined rearward as it is away from the rotation axis O, and communicates with the second cylinder bore 1b at the top dead center of the second piston head 9b.

  The second valve plate 15 is formed with a second discharge port 15b that communicates the second discharge chamber 13c and each second compression chamber 35b. The second discharge valve plate 17 is formed with a second discharge valve 17b that closes each second discharge port 15b with an elastic force. The retainer plate 2b regulates the opening degree of each second discharge valve 17b.

  The first discharge chamber 11c and the second discharge chamber 13c are connected to each other by a discharge passage 1j formed in the first and second cylinder blocks 1F and 1R, and the discharge passage 1j is piped to an external condenser (not shown) by a discharge passage 1m. Connected by. A compressor, a condenser, an expansion valve, and an evaporator constitute a vehicle air conditioner.

  Further, the compressor includes a partition body 45, a moving body 47, a control pressure chamber 49, and a control mechanism 51, as shown in FIGS. The partition body 45 has a disk shape and is fixed to the drive shaft 3 behind the swash plate 5. The moving body 47 has a connecting arm 47a extending toward the swash plate 5, and the connecting arm 47a is connected to the ring plate 5a by a third pin 47b. Similarly to the first and second pins 31a and 31b, the third pin 47b is orthogonal to the rotation axis O and extends in parallel therewith. Therefore, the moving body 47 can rotate integrally with the drive shaft 3 in the swash plate chamber 1c, and moves in the direction of the rotation axis O with respect to the partition body 45. A control pressure chamber 49 is partitioned by the partition body 45 and the moving body 47. The movable body 47 has an O-ring 47 c between the drive shaft 3. The partition body 45 has an O-ring 47 d between the movable body 47. The control pressure chamber 49 moves the moving body 47 in the direction of the rotation axis O by the internal pressure. The moving body 47 pulls the swash plate 5 by moving backward in the direction of the rotation axis O, and expands the inclination angle.

  The moving body 47 is housed in the large-diameter hole 1e in a state assembled to the compressor. A clearance is secured between the moving body 47 and the large-diameter hole 1e so that the moving body 47 can rotate. In the moving body 47, an introduction passage 47e is recessed in the outer peripheral surface thereof. The introduction passage 47e extends from the end on the swash plate chamber 1c side in the direction of the rotation axis O with a predetermined length. Thereby, even if the moving body 47 moves in the direction of the rotation axis O by changing the inclination angle, the introduction passage 47e communicates with the swash plate chamber 1c. Further, as shown in FIG. 3, the introduction passage 47e extends around the rotation axis O at a predetermined angle. Furthermore, as shown in FIG. 6, the introduction passage 47 e intermittently communicates with each suction passage 1 h as the moving body 47 rotates in a state where the inclination angle of the swash plate 5 is maximum. On the other hand, as shown in FIG. 7, the introduction passage 47e has a smaller communication area with each suction passage 1h when the inclination angle of the swash plate 5 is gradually reduced. As shown in FIG. 2, if the inclination angle of the swash plate 5 is minimized, the introduction passage 47e does not communicate with each suction passage 1h even if the moving body 47 rotates. It is also possible to make the introduction passage 47e slightly communicate with each suction passage 1h in a state where the inclination angle of the swash plate 5 is minimum.

  As shown in FIGS. 1 and 2, the drive shaft 3 is formed with a shaft hole 3 a extending coaxially with the rotational axis O from the rear end toward the front. The drive shaft 3 is formed with a radial hole 3b that communicates with the axial hole 3a at the front end of the axial hole 3a and extends in the radial direction. The diameter hole 3b communicates with the control pressure chamber 49 even when the moving body 47 is most advanced. The shaft hole 3a and the diameter hole 3b constitute a control passage.

  In this compressor, a return spring 61 is provided between the first flange 3c and the ring plate 5a, and an inclination angle reducing spring 63 is provided between the partition body 45 and the ring plate 5a. As shown in FIGS. 6 and 7, two O-rings 3e are provided between the shaft hole 1f and the second support member 3q.

  This compressor is used in a vehicle air conditioner. In the compressor, the drive shaft 3 is rotationally driven by the engine. Here, in this compressor, the suction passage 1k opens into the swash plate chamber 1c. For this reason, the refrigerant having passed through the evaporator is first taken into the swash plate chamber 1c through the suction passage 1k. Each piston 9 reciprocates according to the inclination angle of the swash plate 5.

  In the meantime, in this compressor, if the capacity control valve 37 increases the pressure in the pressure adjusting chamber 13d, the pressure is guided to the control pressure chamber 49 through the shaft hole 3a and the diameter hole 3b of the drive shaft 3, and the movable body 47 moves backward in the direction of the rotation axis O. For this reason, the swash plate 5 is pulled by the moving body 47, and the inclination angle increases as shown in FIG. In this state, as shown in FIG. 6, the introduction passage 47e and each suction passage 1h communicate with each other with a large opening.

  For this reason, as shown in FIG. 1, each first piston head 9a reciprocates with a large stroke in the first cylinder bore 1a, and each first compression chamber 35a undergoes a pressure change. For this reason, in the suction stroke, each first suction valve 6a opens the suction port 7a against the elastic force, and the first compression chamber 35a communicates with the first suction chamber 11b. For this reason, the refrigerant in the first suction chamber 11b is sucked into each first compression chamber 35a. In the compression stroke, the refrigerant is compressed in each first compression chamber 35a. In the discharge stroke, each first discharge valve 10a opens the discharge port 7b against the elastic force, and the first compression chamber 35a communicates with the first discharge chamber 11c. For this reason, the refrigerant in each first compression chamber 35a is discharged into the first discharge chamber 11c.

  Further, each second piston head 9b reciprocates with a large stroke in the second cylinder bore 1b, and each second compression chamber 35b changes in pressure. Here, as shown in FIG. 3, when the drive shaft 3 rotates clockwise at a constant speed, the introduction passage 47e and the intake passages 1h of the second cylinder block 1R communicate intermittently. For example, as shown in FIG. 4, when each suction passage 1h is distinguished by the suction passages 1h1 to 1h5 around the rotation axis O, when the drive shaft 3 is in the state (A), the introduction passage 47e causes the swash plate chamber 1c. Communicates with the suction passages 1h4 to 1h1. Therefore, the suction stroke is performed in the second compression chamber 35b communicating with the suction passages 1h4 to 1h1, and the compression stroke is performed in the second compression chamber 35b communicating with the suction passage 1h3, and the second compression communicated with the suction passage 1h2. In the chamber 35b, a discharge stroke is performed.

In the state (B) in which the drive shaft 3 is rotated 72 ° from the state (A), the swash plate chamber 1c communicates with the suction passages 1h5 to 1h2 by the introduction passage 47e. In the state (C) in which the drive shaft 3 is further rotated by 72 ° from the state (B), the swash plate chamber 1c communicates with the suction passages 1h1 to 1h3 by the introduction passage 47e. In the state (D) in which the drive shaft 3 is further rotated by 72 ° from the state (C), the swash plate chamber 1c communicates with the suction passages 1h2 to 1h4 by the introduction passage 47e. In the state (E) in which the drive shaft 3 is further rotated 72 ° from the state (D), the swash plate chamber 1c communicates with the suction passages 1h3 to 1h5 by the introduction passage 47e.

For this reason, the pressure change shown in FIG. 5 (1) occurs in the compression chamber 35b communicating with the suction passage 1h1. Similarly, pressure changes shown in FIGS. 5 (2) to (5) occur in the compression chamber 35b communicating with the suction passages 1h3 to 5h. Thus, as shown in FIG. 1, the refrigerant in each second compression chamber 35b is discharged into the second discharge chamber 13c via the second discharge port 15b and each second discharge valve 17b in the discharge stroke. The refrigerant in the first and second discharge chambers 11c and 13c is discharged to the condenser.

  As shown in FIG. 2, when the capacity control valve 37 lowers the pressure in the pressure adjusting chamber 13d, the pressure is guided to the control pressure chamber 49 through the shaft hole 3a and the diameter hole 3b of the drive shaft 3, and the movable body 47 moves forward in the direction of the rotation axis O. For this reason, the swash plate 5 is pushed by the moving body 47, and an inclination angle becomes small. In this state, as shown in FIG. 7, the introduction passage 47e and each suction passage 1h communicate with each other with a small opening or no communication.

  In this case, as shown in FIG. 2, each first piston head 9a reciprocates the first cylinder bore 1a with a small stroke or hardly reciprocates. Each second piston head 9b also reciprocates with a small stroke or hardly reciprocates with the second cylinder bore 1b.

  Thus, in this compressor, as shown in FIGS. 6 and 7, it is sufficient that the control mechanism 51 controls the pressure in the control pressure chamber 49 having a smaller volume than the swash plate chamber 1c, so that the pressure in the control pressure chamber 49c is sufficient. Can be changed quickly, and the inclination angle can be changed quickly.

  Further, in this compressor, the introduction passage 47e of the moving body 47 intermittently communicates the swash plate chamber 1c and each suction passage 1h as the moving body 47 rotates. Therefore, the refrigerant taken into the swash plate chamber 1c is sucked into the second compression chambers 35b in the suction stroke at the timing in the second cylinder bore 1b. For this reason, in this compressor, power loss can be reduced in the second compression chamber 35b by eliminating the suction valve that closes the suction port by elastic force.

  Therefore, in this compressor, the discharge capacity can be changed quickly. For this reason, in this compressor, it is easy to realize a reduction in power consumption and a desired air conditioning effect. In addition, this compressor can achieve better suction efficiency.

  Moreover, in this compressor, the moving body 47 for changing the inclination angle also serves as a rotary valve. For this reason, it is not necessary to provide a separate rotary valve, and the structure can be simplified.

  Further, in this compressor, since the external suction refrigerant is first taken into the swash plate chamber 1c having a large volume, suction pulsation can be easily suppressed.

  Further, in this compressor, it is not necessary to form a suction chamber in the rear housing 13, and it is not necessary to provide a suction passage for connecting the swash plate chamber 1c and the suction chamber in the second cylinder block 1R. For this reason, this compressor can avoid the suction pressure loss by the suction passage when it is desired to reduce the size, and exhibits an excellent volumetric efficiency.

(Example 2)
In the compressor of the second embodiment, as shown in FIG. 8, each suction passage 1p has a rotational axis at a position moved to the bottom dead center side of the second piston head 9b from each suction passage 1h of the first embodiment. It extends at right angles to O.

  A second suction chamber 13b is formed in the rear housing 13 in an annular shape. The second suction chamber 13b is connected to the evaporator by a second suction path 1n. A second discharge chamber 11c is formed in an annular shape outside the second suction chamber 13b.

  A second intake valve plate 14 is provided between the second cylinder block 1R and the second valve plate 15. As shown in FIGS. 9 and 10, the retainer plate 2b, the second discharge valve plate 17, and the second valve plate 15 are formed with a suction port 15a that communicates the second suction chamber 13b with each second compression chamber 35b. ing. The second suction valve plate 14 is formed with a suction valve 14a that closes each suction port 15a by elastic force. The second cylinder block 1R is formed with a retainer recess 14b that regulates the opening degree of each intake valve 14a.

  The rear housing 13 is formed with a low pressure passage 39 a that communicates the second suction chamber 13 b and the capacity control valve 37. Other configurations are the same as those of the compressor of the first embodiment.

In this compressor, as shown in FIG. 9, if the inclination angle is in a maximum state or a state close to the maximum, each intake valve 15a opens the intake port 15a against the elastic force in the intake stroke. The second compression chamber 35b is communicated with the second suction chamber 13b. Therefore, the refrigerant in the second suction chamber 13b is sucked into each second compression chamber 35b. The introduction passage 47e communicates with each suction passage 1p and performs a suction stroke in each second compression chamber 35b. Then, a compression stroke and a discharge stroke are performed in the second compression chamber 35b. Also in each first compression chamber 35a, the suction stroke, the compression stroke, and the discharge stroke are performed as in the first embodiment.

  On the other hand, if the inclination angle is reduced, the moving body 47 moves forward in the direction of the rotation axis O as shown in FIG. 10, and the introduction passage 47e does not communicate with each suction passage 1p. However, the suction refrigerant is sucked into each second compression chamber 35b through the suction port 15a and the second suction valve 14a by the reciprocation of the piston 9. Other functions and effects are the same as those of the compressor of the first embodiment.

Example 3
In the compressor of the third embodiment, as shown in FIG. 11, a suction passage 1q that is narrower than the suction passages 1p of the second embodiment is formed.

  Further, a bore-side groove 1s communicating with each second compression chamber 35b is formed at the rear end of the second cylinder block 1R. The first and second piston heads 9a and 9b of each piston 9 are longer than the pistons of the first and second embodiments. Each second piston head 9b is provided with a piston passage 9d that communicates with the bore-side groove 1s by positioning the second piston head 9b at the top dead center with the maximum inclination angle. Each piston passage 9d communicates with each suction passage 1q when the second piston head 9b is located at the top dead center with the maximum inclination angle.

  A rotating passage 53 is recessed in the outer peripheral surface of the moving body 47. As shown in FIG. 12, the rotary passage 53 includes a high-pressure side opening 53a that communicates with the second compression chamber 35b after the end of the discharge stroke via each suction passage 1p, and a second compression chamber that is in the suction stroke or the compression stroke. 35b and a low pressure side opening 53b communicating with each suction passage 1p, and a connection passage 53c connecting the high pressure side opening 53a and the low pressure side opening 53b. Each bore-side groove 1s, each piston passage 9d, the rotation passage 53 and each suction passage 1q constitutes a residual gas bypass passage. Each suction passage 1q also has a function of communicating the swash plate chamber 1c and each second compression chamber 35b through the introduction passage 47e of the moving body 47. Other configurations are the same as those of the compressor of the second embodiment.

Also in this compressor, similarly to the compressor of the second embodiment, the suction refrigerant is sucked into the second compression chamber 35b from the second suction chamber 13b if the inclination angle is in the maximum state or near the maximum.

  Further, in this compressor, when the tilt angle is in the maximum state or near the maximum, as shown in FIG. 12, when the drive shaft 3 is in the state (A), the swash plate chamber 1c is drawn into the suction passage 1q5 by the introduction passage 47e. Communicate with. For this reason, the suction stroke is performed in the second compression chamber 35b communicating with the suction passage 1q5, the compression stroke is performed in the second compression chamber 35b communicating with the suction passages 1q4 to 1q2, and the second compression communicating with the suction passage 1q1. The discharge stroke is finished in the chamber 35b.

  Further, as the moving body 47 rotates, residual gas remaining in the second compression chamber 35b communicating with the suction passage 1q1 after completion of the discharge stroke passes through the bore side groove 1s and each piston passage 9d, and the high pressure side opening 53a of the rotation passage 53. And is collected in the connection passage 53c. The residual gas in the connection passage 53c moves from the low-pressure side opening 53b to the second compression chamber 35b in the compression stroke through the suction passages 1q4 as the moving body 47 rotates.

  In the state (B) in which the drive shaft 3 is rotated 72 ° from the state (A), the swash plate chamber 1c communicates with the suction passage 1q1 by the introduction passage 47e. Further, the residual gas moves from the suction passage 1q5 to the second compression chamber 35b in the compression stroke through the suction passage 1q2, the high-pressure side opening 53a, the connection passage 53c, and the low-pressure side opening 53b.

  In the state (C) in which the drive shaft 3 is rotated 72 ° from the state (B), the swash plate chamber 1c communicates with the suction passage 1q2 by the introduction passage 47e. The residual gas moves from the suction passage 1q1 to the second compression chamber 35b in the compression stroke through the suction passage 1q3, the high-pressure side opening 53a, the connection passage 53c, and the low-pressure side opening 53b.

  The same applies to the state (D) in which the drive shaft 3 is rotated 72 ° from the state (C) and the state (E) in which the drive shaft 3 is rotated 72 ° from the state (D).

For this reason, the pressure change shown in FIG. 13 (1) occurs in the compression chamber 35b communicating with the suction passage 1q1. Further, residual gas in the compression chamber 35b communicating with the suction passage 1q1 is supplied to the compression chamber 35b communicating with the suction passage 1q4 via the bore side groove 1s, each piston passage 9d, and the rotation passage 53. Similarly, in the compression chamber 35b communicating with the suction passages 1q2 to 1q5, pressure changes shown in FIGS. 13 (2) to (5) occur.

  Thus, in this compressor, the moving body 47 can move the residual gas remaining in the second compression chamber 35b to the second compression chamber 35b during the suction stroke or the compression stroke. Power loss due to re-expansion of residual gas can be reduced. Further, since it is not necessary to provide a residual gas bypass passage separately, simplification of the structure can be realized. Other functions and effects are the same as those of the compressor of the second embodiment.

  In the above, the present invention has been described with reference to the first to third embodiments. However, the present invention is not limited to the first to third embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.

  For example, in the first to third embodiments, the present invention is embodied by a variable displacement double-head swash plate compressor having two cylinder blocks. However, a variable displacement single-head swash plate compression having a single cylinder block is used. The present invention can be embodied by a machine.

  In the compressors of the first to third embodiments, the discharge chamber 13a of the rear housing 13 is formed in an annular shape. However, even if the discharge chamber is formed in a U shape, the effects of the present invention can be achieved.

  Further, in the compressors of the first to third embodiments, as a control mechanism, the low pressure passage, the high pressure passage and the air supply passage are connected to the capacity control valve, but a fixed throttle is provided in the high pressure passage, and the capacity control valve is provided in the low pressure passage. A provided control mechanism may be used. Alternatively, a control mechanism in which a capacity control valve is provided in the high-pressure passage and a fixed throttle is provided in the low-pressure passage may be used.

  In the first to third embodiments, the moving body is provided on the rear housing side, the first suction chamber is formed in the front housing, and the first suction valve is provided between the cylinder block and the front housing. May be provided on the front housing side, a second suction chamber may be formed in the rear housing, and a second suction valve may be provided between the cylinder block and the rear housing.

  The present invention is applicable to an air conditioner such as a vehicle.

1c: Swash plate chamber 11c, 13c: Discharge chamber (11c: First discharge chamber, 13c: Second discharge chamber)
1a, 1b ... cylinder bore (1a ... first cylinder bore, 1b ... second cylinder bore)
1F, 1R ... Cylinder block (1F ... 1st cylinder block, 1R ... 2nd cylinder block)
11 ... Front housing (first head member)
13 ... Rear housing (second head member)
DESCRIPTION OF SYMBOLS 3 ... Drive shaft 5 ... Swash plate O ... Rotary axis 7 ... Link mechanism 35a, 35b ... Compression chamber (35a ... 1st compression chamber, 35b ... 2nd compression chamber)
DESCRIPTION OF SYMBOLS 9 ... Piston 45 ... Partition body 47 ... Moving body 49 ... Control pressure chamber 51 ... Control mechanism 1k ... Suction passage 1h, 1p, 1q ... Suction passage 47e ... Introduction passage 53a ... High pressure side opening 53b ... Low pressure side opening 53c ... Connection passage 9a ... 1st piston head 9b ... 2nd piston head 10a ... 1st discharge valve 17b ... 2nd discharge valve 11b ... 1st suction chamber 6a ... 1st suction valve

Claims (3)

A housing having a cylinder block in which a swash plate chamber, a discharge chamber and a plurality of cylinder bores are formed;
A drive shaft rotatably supported by the cylinder block;
A swash plate disposed in the swash plate chamber and rotated together with the drive shaft;
A link mechanism provided between the drive shaft and the swash plate, and allowing a change in the inclination angle of the swash plate with respect to a direction orthogonal to the rotational axis of the drive shaft;
A piston that is housed in each cylinder bore and reciprocates at a stroke according to the tilt angle by rotation of the swash plate to form a compression chamber in each cylinder bore;
A partition provided in the swash plate chamber so as to be integrally rotatable with the drive shaft;
A movable body that is integrally rotatable with the drive shaft in the swash plate chamber and that moves in the direction of the rotational axis relative to the partition body to change the tilt angle;
A control pressure chamber that is partitioned by the partition body and the moving body and moves the moving body by an internal pressure;
A control mechanism for controlling the pressure in the control pressure chamber,
A suction path for taking in refrigerant from outside opens into the swash plate chamber,
The cylinder block is formed with a suction passage communicating with each cylinder bore,
The variable displacement swash plate compressor is characterized in that an introduction passage is formed in the moving body to intermittently communicate the swash plate chamber and the suction passages as the moving body rotates.   The movable body communicates with the compression chamber after the discharge stroke and the high-pressure side opening through the suction passages, and with the compression chamber in the suction stroke or during the compression stroke and the suction passages. 2. The variable capacity swash plate compressor according to claim 1, wherein a low pressure side opening and a connection passage connecting the high pressure side opening and the low pressure side opening are formed. Each cylinder bore is composed of a first cylinder bore located on one side of the rotational axis and a second cylinder bore located on the other side of the rotational axis,
Each piston has a first piston head located on one side of the rotation axis and a second piston head located on the other side of the rotation axis,
Each compression chamber comprises a first compression chamber formed by the first piston head in the first cylinder bore and a second compression chamber formed by the second piston head in the second cylinder bore,
A first head member that forms a first discharge chamber on each first compression chamber side and a second head member that forms a second discharge chamber on each second compression chamber side are joined to the cylinder block. ,
Between the cylinder block and the first head member, there is provided a first discharge valve for communicating the first compression chamber and the first discharge chamber by pressure in the first compression chamber,
Between the cylinder block and the second head member, there is provided a second discharge valve for communicating the second compression chamber and the second discharge chamber by pressure in the second compression chamber,
The link mechanism is arranged such that the top dead center position of the second piston head moves more greatly than the top dead center position of the first piston head in accordance with the change of the tilt angle.
A first suction chamber is formed in the first head member,
2. A first suction valve is provided between the cylinder block and the first head member so as to communicate the first suction chamber and the first compression chamber against an elastic force. 2. The variable capacity swash plate compressor according to 2.

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