JP6879252B2 - Variable capacity swash plate compressor - Google Patents

Description

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

Patent Document 1 discloses a conventional variable capacity swash plate compressor (hereinafter, simply referred to as a compressor). The compressor includes a housing, a swash plate, a plurality of pistons, a capacitance control valve and an opening degree adjusting valve. The housing is formed with a suction chamber, a plurality of cylinder bores, a crank chamber, and a discharge chamber. The swash plate is provided in the crank chamber, and the inclination angle is changed by the crank chamber pressure in the crank chamber. Each piston is housed in a cylinder bore while engaging with a swash plate to form a compression chamber with the housing. The capacity control valve and the opening degree adjusting valve are provided in the housing. The capacitance control valve can change the crank chamber pressure.

More specifically, the housing is formed with an intake passage, an air supply passage and an air extraction passage. The suction passage connects the external circuit and the suction chamber. The air supply passage connects the discharge chamber and the crank chamber via a capacity control valve. The bleed air passage connects the crank chamber and the suction chamber. The opening degree adjusting valve can change the opening degree of the suction passage.

The opening degree adjusting valve has a tubular valve case and a valve body housed in the valve case. The valve case is formed with a first valve chamber, a second valve chamber, a suction window, a suction port, and an air extraction window. The first valve chamber constitutes a part of the suction passage. The second valve chamber communicates with the first valve chamber and forms a part of the bleed air passage. The suction window opens on the peripheral surface of the valve case and communicates the first valve chamber with the suction chamber side of the suction passage. The suction port is open to the end face of the valve case and communicates the first valve chamber with the external circuit side of the suction passage. The air extraction window opens on the peripheral surface of the valve case at a position different from that of the suction window, and communicates the second valve chamber and the air extraction passage.

The valve body has a first valve body, a second valve body, and an urging spring. The first valve body is slidable inside the first valve chamber. The first valve body has a valve wall that changes the area overlapping the suction window by sliding the first valve body inside the first valve chamber. The second valve body is slidable inside the second valve chamber. The urging spring is urged so that the first valve body and the second valve body are separated from each other.

Further, in the first valve chamber and the second valve chamber, a damper chamber is divided by a first valve body and a second valve body. A bypass path is formed on the peripheral surface of the valve case. The damper chamber communicates with the suction chamber side of the suction passage by a bypass path.

In this compressor, when the suction pressure of the refrigerant taken into the suction chamber is lower than the set suction pressure, the area where the valve wall and the suction window overlap becomes large. As a result, the opening of the suction window of the first valve body is reduced. In this way, the opening degree adjusting valve reduces the opening degree of the suction passage. On the other hand, when the suction pressure is higher than the set suction pressure and the capacity is large, the area where the valve wall and the suction window overlap becomes smaller. As a result, the opening of the suction window of the first valve body is increased. In this way, the opening degree adjusting valve increases the opening degree of the suction passage. Further, when the crank chamber pressure is smaller than the set crank chamber pressure, the first valve body reduces the opening degree of the suction window. In this way, the opening degree adjusting valve reduces the opening degree of the suction passage.

As a result, in this compressor, while preventing the pressure loss of the suction pressure at the time of a large capacity, the quietness at the time of a small capacity is also ensured. Further, in this compressor, the pressure fluctuation of the suction pressure at the time of starting can be reduced.

In this compressor, the damper effect based on the pressure in the damper chamber prevents the first valve body from unnecessarily sliding inside the first valve chamber when the capacity is small. As a result, the inhalation pulsation at a small volume due to the pressure fluctuation of the inhalation pressure is also reduced. Further, in this compressor, the pressure in the damper chamber is prevented from becoming excessive at the time of a large capacity by communicating with the suction chamber side of the suction passage by a bypass path.

International Publication No. 2017/145798

However, in the above-mentioned conventional compressor, since the bypass path is formed on the peripheral surface of the valve case, if the bypass path is blocked by the housing when the opening degree adjusting valve is attached, the pressure in the damper chamber is suitably adjusted. It becomes difficult. As a result, the pressure in the damper chamber becomes excessive when the capacity is large, and the damper effect is excessively exerted, so that the sliding of the first valve body is hindered. As a result, it becomes difficult to suitably take in the refrigerant from the external circuit into the suction chamber when the capacity is large.

Therefore, the mounting direction of the opening adjustment valve with respect to the housing is restricted so that the bypass path is not blocked by the housing, or a groove or the like is formed in the housing to provide a gap between the housing and the valve case. Can be considered. However, in this case, the manufacturing becomes complicated and the manufacturing cost increases.

The present invention has been made in view of the above-mentioned conventional circumstances, and an object of the present invention is to provide a variable capacity swash plate compressor that can solve all of the following problems.
(1) While preventing pressure loss of suction pressure at the time of large capacity, quietness at the time of small capacity can be ensured.
(2) It is possible to reduce the pressure fluctuation of the suction pressure at the time of starting.
(3) It is possible to suppress an increase in manufacturing cost while suitably exerting the damper effect of the damper chamber.

The variable capacity swash plate compressor of the present invention includes a housing in which a suction chamber, a cylinder bore, a crank chamber and a discharge chamber are formed, and a housing in which a suction chamber, a cylinder bore, a crank chamber and a discharge chamber are formed.
A swash plate provided in the crank chamber and whose inclination angle is changed by the crank chamber pressure in the crank chamber.
A piston that is housed in the cylinder bore while engaging with the swash plate and forms a compression chamber with the housing.
It is equipped with a capacitance control valve that can change the crank chamber pressure.
The housing includes a suction passage connecting the external circuit and the suction chamber, an air supply passage connecting the discharge chamber and the crank chamber via the capacitance control valve, and the crank chamber and the suction chamber. A bleed passage connecting the
In the variable capacity swash plate type compressor further provided with an opening degree adjusting valve for changing the opening degree of the suction passage.
The opening degree adjusting valve has a tubular valve case and a valve body housed in the valve case.
The valve case has a first valve chamber that forms a part of the suction passage, a second valve chamber that communicates with the first valve chamber and forms a part of the bleed air passage, and an opening on the peripheral surface. A suction window that communicates the first valve chamber and the suction chamber side of the suction passage, and a suction port that opens at the end face and communicates between the first valve chamber and the external circuit side of the suction passage. An air extraction window that opens to the peripheral surface or the end surface and communicates the second valve chamber and the air extraction passage is formed.
The valve body includes a first valve body slidable inside the first valve chamber, a second valve body slidable inside the second valve chamber, and the first valve body and the second valve body. It has the first valve body and the urging spring that urges the second valve body so as to be separated from the valve body.
The first valve body has a valve wall that changes the region overlapping with the suction window by sliding the first valve body inside the first valve chamber.
In the first valve chamber and the second valve chamber, a damper chamber is partitioned by the first valve body and the second valve body.
The valve wall is characterized in that a bypass path that extends in the circumferential direction and faces the suction window to communicate the damper chamber and the suction window is formed.

In the compressor of the present invention, when the suction pressure of the refrigerant taken into the suction chamber is lower than the preset suction pressure, the valve wall and the suction window of the first valve body overlap with each other inside the first valve chamber. Slide so that the area is large. As a result, the opening of the suction window of the first valve body is reduced. In this way, the opening degree adjusting valve reduces the opening degree of the suction passage at the time of starting, so that the pressure fluctuation of the suction pressure at the time of starting can be reduced.

On the other hand, when the suction pressure is higher than the set suction pressure and the capacity is large, the first valve body slides inside the first valve chamber so that the region where the valve wall and the suction window overlap becomes smaller. As a result, the opening of the suction window of the first valve body is increased. In this way, when the capacity is large, including the maximum capacity, the opening degree adjusting valve increases the opening degree of the suction passage, so that the pressure loss of the suction pressure can be prevented.

Further, when the crank chamber pressure is smaller than the preset crank chamber pressure, the second valve body slides toward the first valve body side inside the second valve chamber. Therefore, the urging spring separates the first valve body from the second valve body so that the area where the valve wall and the suction window overlap with each other becomes larger inside the first valve chamber. Sliding on. In this way, when the capacity is small, including the minimum capacity, the opening degree adjusting valve reduces the opening degree of the suction passage. As a result, the pressure fluctuation of the suction pressure at the time of small capacity can be reduced. Here, if the second valve body is configured to reduce the opening degree of the bleeding window by sliding toward the first valve body side, the opening degree adjusting valve reduces the opening degree of the bleeding passage. As a result, it becomes difficult to compress the high-pressure refrigerant in the crank chamber again, so that the volumetric efficiency increases at the minimum capacity or the small capacity. In this case, since it is not necessary to use a separate bleed valve in this compressor, the number of parts can be reduced and the degree of freedom in design is unlikely to decrease.

Then, in this compressor, the bypass path faces the suction window, so that the damper chamber and the suction chamber side of the suction passage communicate with each other. As a result, the pressure in the damper chamber is suitably adjusted, and the damper effect is suitably exhibited. Therefore, it is possible to prevent the first valve body from unnecessarily sliding inside the first valve chamber when the capacity is small, including at the time of starting and the minimum capacity. Therefore, the opening degree adjusting valve can preferably maintain a state in which the opening degree of the suction passage is reduced. As a result, in this compressor, the suction pulsation at a small volume due to the pressure fluctuation of the suction pressure can be reduced. On the other hand, when the capacity is large, the opening degree adjusting valve can preferably increase the opening degree of the suction passage by the first valve body sliding appropriately inside the first valve chamber. Therefore, the refrigerant can be suitably taken into the suction chamber from the external circuit.

Here, since the bypass path is formed in the first valve body, the bypass path is not blocked by the housing when the opening degree adjusting valve is attached to the housing. Therefore, in order to preferably exert the damper effect, in this compressor, the mounting direction of the opening adjustment valve with respect to the housing is regulated, or a groove or the like is formed in the housing to provide a gap between the housing and the valve case. There is no need to do it. Therefore, the production can be facilitated.

Further, since the bypass path is formed in the circumferential direction of the first valve wall, even when the first valve body rotates around the rotation axis extending in the direction intersecting the circumferential direction during operation, the bypass path and the bypass path are formed. It is unlikely that the phase shift from the suction window will occur. Therefore, in this compressor, even when the first valve body rotates, the bypass path can be faced with the suction window with high certainty.

Therefore, in the variable capacity swash plate compressor of the present invention, it is possible to prevent the pressure loss of the suction pressure at the time of large capacity and to secure the quietness at the time of small capacity. Further, in this variable capacity type swash plate compressor, it is possible to reduce the pressure fluctuation of the suction pressure at the time of starting. Then, in this variable capacity type swash plate type compressor, it is possible to suppress an increase in manufacturing cost while suitably exerting the damper effect of the damper chamber.

It is preferable that at least a part of the bypass path faces the suction window regardless of the position of the first valve body. In this case, since the damper chamber and the suction chamber side of the suction passage always communicate with each other by the bypass path, the pressure in the damper chamber can be appropriately adjusted, and the damper effect can be suitably exhibited.

Further, it is preferable that the second valve body has pores that communicate the inside of the second valve chamber and the outside of the second valve chamber. In this case, when the pressure inside the second valve chamber is high, the pressure inside the second valve chamber can be released to the outside of the second valve chamber through the pores, so that the second valve body can move easily and the controllability is improved. improves. Further, when the pressure in the second valve chamber is low, the refrigerant can flow into the second valve chamber from the outside of the second valve chamber through the pores. This also allows the pressure in the damper chamber to be suitably adjusted in this compressor.

The valve wall can be tubular. The bypass path preferably has a peripheral groove extending in the circumferential direction of the valve wall and facing the suction window, and a communication hole penetrating the valve wall and communicating the peripheral groove and the damper chamber. In this case, the pressure in the damper chamber can be adjusted more preferably by the bypass path, so that the damper effect can be more preferably exhibited.

Further, it is preferable that the peripheral groove is formed in an annular shape. In this case, even if the first valve body rotates during operation, the peripheral groove and the bypass path always face the suction window.

In the variable capacity swash plate compressor of the present invention, it is possible to prevent pressure loss of suction pressure at the time of large capacity and to secure quietness at the time of small capacity. Further, in this variable capacity type swash plate compressor, it is possible to reduce the pressure fluctuation of the suction pressure at the time of starting. Then, in this variable capacity type swash plate type compressor, it is possible to suppress an increase in manufacturing cost while suitably exerting the damper effect of the damper chamber.

FIG. 1 is a cross-sectional view of the compressor of the first embodiment. FIG. 2 is an enlarged cross-sectional view of a main part of the compressor at the time of starting, relating to the compressor of the first embodiment. FIG. 3 is an enlarged cross-sectional view of a main part of the compressor at the maximum capacity according to the compressor of the first embodiment. FIG. 4 is an enlarged cross-sectional view of a main part of the compressor at the minimum capacity according to the compressor of the first embodiment. FIG. 5 is a schematic view showing an opening degree adjusting valve related to the compressor of the first embodiment. FIG. (A) is a schematic view showing an opening degree adjusting valve at the time of starting. FIG. (B) is a schematic view showing an opening degree adjusting valve when the first valve body starts to open the suction window. FIG. (C) is a schematic view showing an opening degree adjusting valve at the maximum capacity. FIG. (D) is a schematic view showing an opening degree adjusting valve at the minimum capacity. FIG. 6 is an enlarged cross-sectional view of a main part of the compressor at the time of starting, relating to the compressor of the second embodiment. FIG. 7 is an enlarged cross-sectional view of a main part of the compressor at the maximum capacity according to the compressor of the second embodiment. FIG. 8 is an enlarged cross-sectional view of a main part of the compressor at the minimum capacity according to the compressor of the second embodiment. FIG. 9 is a cross-sectional view of the compressor of the third embodiment. FIG. 10 is an enlarged cross-sectional view of a main part of the compressor at the time of starting, relating to the compressor of the third embodiment. FIG. 11 is an enlarged cross-sectional view of a main part of the compressor at the maximum capacity according to the compressor of the third embodiment. FIG. 12 is an enlarged cross-sectional view of a main part of the compressor at the minimum capacity according to the compressor of the third embodiment.

Hereinafter, Examples 1 to 3 embodying the present invention will be described with reference to the drawings. The compressors of Examples 1 to 3 are single-headed piston type variable capacity swash plate type compressors. These compressors are mounted on the vehicle and form a refrigerating circuit of the air conditioner.

(Example 1)
As shown in FIG. 1, the compressor housing 1 of the first embodiment has a front housing 3, a rear housing 5, a cylinder block 7, and a valve forming plate 9. In this embodiment, the side where the front housing 3 is located is the front side of the compressor, and the side where the rear housing 5 is located is the rear side of the compressor, and the front-rear direction of the compressor is defined. Further, the upper part of the paper surface of FIG. 1 is defined as the upper part of the compressor, and the lower part of the paper surface of FIG. Then, in FIGS. 2 and 2, the front-back direction and the up-down direction are defined corresponding to FIG. The posture of the compressor is appropriately changed according to the vehicle or the like on which the compressor is mounted.

The front housing 3 is formed with a boss 3a that projects forward. A first shaft hole 3b extending in the front-rear direction of the compressor is formed in the boss 3a. A shaft sealing device 11a and a first radial bearing 11b are provided in the first shaft hole 3b. Further, a first thrust bearing 11c is provided on the rear surface of the front housing 3.

A suction chamber 5a and a discharge chamber 5b are formed in the rear housing 5. Further, the rear housing 5 is provided with a capacitance control valve 13. The suction chamber 5a is located on the outer side of the rear housing 5 in the radial direction. The suction chamber 5a is connected to the evaporator 101 provided outside the compressor by a suction passage 51 described later. The suction chamber 5a integrally includes a valve accommodating chamber 47 extending in the radial direction of the rear housing 5. That is, the valve accommodating chamber 47 constitutes a part of the suction chamber 5a. The details of the valve accommodating chamber 47 will be described later.

The discharge chamber 5b is located inside the rear housing 5 in the radial direction. The discharge chamber 5b is connected to a condenser 102 provided outside the compressor by a discharge passage 53. A check valve 55 is provided in the discharge passage 53. The external circuit 100 is composed of an evaporator 101, a condenser 102, an expansion valve 103, a pipe 104, and the like. The air conditioner is composed of the compressor and the external circuit 100.

The cylinder block 7 is located between the front housing 3 and the valve forming plate 9. A crank chamber 15 is formed between the front housing 3 and the cylinder block 7. A plurality of cylinder bores 7a are formed in the cylinder block 7 at equal angular intervals in the circumferential direction. Each cylinder bore 7a communicates with the crank chamber 15 in front.

Further, the cylinder block 7 is formed with a second shaft hole 7b coaxial with the first shaft hole 3b. A second radial bearing 17a, a second thrust bearing 17b, and a pressing spring 17c are provided in the second shaft hole 7b.

A drive shaft 19 is inserted through the front housing 3 and the cylinder block 7. The drive shaft 19 is inserted into the shaft sealing device 11a in the front housing 3. Further, the drive shaft 19 is inserted into the second radial bearing 17a and the second thrust bearing 17b in the cylinder block 7. As a result, the drive shaft 19 is supported by the housing 1 and can rotate around a rotation axis parallel to the front-rear direction of the compressor.

A lug plate 21 is press-fitted into the drive shaft 19. The lug plate 21 is arranged forward in the crank chamber 15 and can rotate in the crank chamber 15 as the drive shaft 19 rotates. A first radial bearing 11b and a first thrust bearing 11c are provided between the lug plate 21 and the front housing 3.

A swash plate 23 is inserted through the drive shaft 19. The swash plate 23 is located behind the lug plate 21 in the crank chamber 15. A tilt angle reducing spring 25 is provided around the drive shaft 19 between the lug plate 21 and the swash plate 23. A circlip 27 is fixed behind the drive shaft 19, and a return spring 29 is provided around the drive shaft 19 between the circlip 27 and the swash plate 23.

In the crank chamber 15, the lug plate 21 and the swash plate 23 are connected by a link mechanism 31. The link mechanism 31 supports the swash plate 23 so that the inclination angle of the swash plate 23 with respect to the direction orthogonal to the drive axis of the drive shaft 19 can be changed.

A piston 33 is housed in each cylinder bore 7a so as to be reciprocating. The rear end surface of each piston 33 faces the valve forming plate 9 in each cylinder bore 7a. As a result, each piston 33 partitions the compression chamber 35 behind each cylinder bore 7a.

A pair of front and rear shoes 37a and 37b are provided between each piston 33 and the swash plate 23. Each piston 33 is engaged with the swash plate 23 by a pair of shoes 37a and 37b. Then, the rotation of the swash plate 23 is converted into the reciprocating movement of the piston 33 by the shoes 37a and 37b of each pair. Further, each piston 33 can be reciprocated in each cylinder bore 7a with a stroke corresponding to the inclination angle of the swash plate 23 by the pair of shoes 37a and 37b.

The valve forming plate 9 is formed by laminating a suction valve plate, a valve plate and a discharge valve plate from the front. A suction reed valve, a suction port, a discharge port, and a discharge reed valve are formed on the valve forming plate 9 corresponding to each cylinder bore 7a. A retainer 39 is fixed to the rear surface of the valve forming plate 9. The retainer 39 is arranged in the discharge chamber 5b and regulates the maximum opening degree of the discharge reed valve.

As shown in FIG. 2, this compressor has a first air supply passage 41 that connects the discharge chamber 5b and the capacity control valve 13, and a second air supply passage 43 that connects the capacity control valve 13 and the crank chamber 15. And a detection passage 45 that communicates the suction chamber 5a and the capacity control valve 13.

As shown in FIGS. 1 and 2, the first air supply passage 41 and the detection passage 45 are formed in the rear housing 5. The second air supply passage 43 is formed in the rear housing 5, the retainer 39, the valve forming plate 9, and the cylinder block 7. The capacity control valve 13 is provided in the rear housing 5. The capacity control valve 13 adjusts the communication area between the first air supply passage 41 and the second air supply passage 43 based on the suction pressure Ps in the suction chamber 5a and the control signal of the controller 49. In this way, in this compressor, the discharge chamber 5b and the crank chamber 15 are connected to each other by the first and second air supply passages 41 and 43 via the capacity control valve 13.

The valve accommodating chamber 47 is formed in a substantially columnar shape extending in the radial direction of the rear housing 5. The valve accommodating chamber 47 has an opening 47a, a first valve accommodating chamber 47b, and a second valve accommodating chamber 47c. The opening 47a opens toward the outside of the rear housing 5, that is, toward the evaporator 101. The first valve accommodating chamber 47b has a columnar shape having a diameter smaller than that of the opening 47a. The upper end of the first valve accommodating chamber 47b is connected to the opening 47a. The second valve accommodating chamber 47c has a columnar shape having a smaller diameter than the first valve accommodating chamber 47b. The upper end of the second valve accommodating chamber 47c is connected to the lower end of the first valve accommodating chamber 47b. Further, in the valve accommodating chamber 47, a step portion 47d is formed between the opening 47a and the first valve accommodating chamber 47b, and between the first valve accommodating chamber 47b and the second valve accommodating chamber 47c. A step portion 47e is formed. An opening degree adjusting valve 61 is provided in the valve accommodating chamber 47.

As shown in FIGS. 2 to 4, the opening degree adjusting valve 61 is composed of a valve case 63 and a valve body 64. The valve body 64 includes a first valve body 65, a second valve body 67, and an urging spring 69.

The valve case 63 is formed in a substantially cylindrical shape. The valve case 63 includes a tubular body 63a, a lid body 63b, and a support 63c. The tubular body 63a constitutes the peripheral surface of the valve case 63. Further, the lid body 63b constitutes the lower end surface of the valve case 63. The support 63c constitutes the upper end surface of the valve case 63.

The tubular body 63a has a cylindrical large-diameter portion 631 having a diameter slightly smaller than that of the first valve accommodating chamber 47b, and is coaxial with the large-diameter portion 631 and integrated with the large-diameter portion 631. It is composed of a small diameter portion 632 having a small diameter cylindrical shape. The inside of the large diameter portion 631 is the first valve chamber 71a, and the inside of the small diameter portion 632 is the second valve chamber 71b. The first valve chamber 71a has a columnar shape and extends in the axial direction of the valve case 63. The second valve chamber 71b is coaxial with the first valve chamber 71a and has a columnar shape having a smaller diameter than the first valve chamber 71a. The second valve chamber 71b extends in the axial direction of the valve case 63 while communicating with the first valve chamber 71a.

The opening degree adjusting valve 61 is inserted into the valve accommodating chamber 47 in the axial direction of the valve case 63, and is prevented from coming off by the circlip 73. In this state, in the opening degree adjusting valve 61, the upper portion of the support 63c comes into contact with the step portion 47d, and the lower portion of the large diameter portion 631 comes into contact with the step portion 47e. In this way, the opening degree adjusting valve 61 is arranged in the rear housing 5 in a state where the vertical direction of the compressor and the axial direction of the valve case 63 are parallel to each other.

Further, a plurality of suction windows 73a are formed in the large diameter portion 631 in the circumferential direction. That is, each suction window 73a is formed on the peripheral surface of the valve case 63. As shown in FIG. 5, each suction window 73a is formed in a substantially rectangular shape in which the opening area gradually decreases toward the support 63c.

Further, as shown in FIG. 5, each suction window 73a is integrally formed with a start-up open path 73b. That is, each start-up open path 73b is also formed in the circumferential direction of the large diameter portion 631. Each start-up open path 73b is formed so as to be continuous with the lower end of each suction window 73a. Each start-up open path 73b is formed in a substantially triangular shape in which the opening area gradually decreases as the distance from each suction window 73a increases. The shape of each start-up open path 73b can be appropriately designed, and may be separate from each suction window 73a. Further, the start-up open path 73b may be formed so as to be integrated only with the specific suction window 73a.

As shown in FIGS. 2 to 4, a plurality of bleeding windows 73c are formed in the small diameter portion 632 in the circumferential direction. That is, each air extraction window 73c is a peripheral surface of the valve case 63, and is formed at a position different from that of each suction window 73a. As shown in FIG. 5, each air extraction window 73c is formed in a circular shape having a diameter smaller than that of each suction window 73a. The number of bleeding windows 73c and the like can be appropriately designed.

A flange 75 that projects in an annular shape is formed between the large diameter portion 631 and the small diameter portion 632. The flange 75 regulates the lower position of the first valve body 65 and the upper position of the second valve body 67. When the second valve body 67 is seated on the flange 75, the first pressure receiving area S1 shown in FIG. 2 is secured on the upper surface of the second valve body 67 by the inner diameter of the flange 75, and on the lower surface of the second valve body 67. , A second pressure receiving area S2 larger than the first pressure receiving area S1 is secured.

Further, the small diameter portion 632 is formed with O-ring grooves 77a and 77b that vertically sandwich the bleeding window 73c, and the O-ring grooves 77a and 77b are provided with O-rings 79a and 79b. The O-rings 79a and 79b are in contact with the inner peripheral surface of the second valve accommodating chamber 47c.

In the small diameter portion 632, the lid 63b is fixed to the end portion on the side opposite to the large diameter portion 631 side. A communication window 73d is formed on the lid 63b. The communication window 73d communicates the second valve chamber 71b with the second communication passage 59, which will be described later, in the axial direction of the valve case 63. The lid 63b can regulate the lower position of the second valve body 67.

In the large diameter portion 631, the support 63c is fixed to the end on the side opposite to the small diameter portion 632 side. The support 63c can regulate the upper position of the first valve body 65. An O-ring groove 77c is formed in the support 63c, and an O-ring 79c is provided in the O-ring groove 77c. The O-ring 79c is in contact with the inner peripheral surface of the first valve accommodating chamber 47b.

Further, a suction port 633 is formed through the support 63c. The suction port 633 extends in the axial direction of the valve case 63. When the opening degree adjusting valve 61 is inserted into the valve accommodating chamber 47, the upper end of the suction port 633 opens toward the opening 47a of the valve accommodating chamber 47, and the lower end opens toward the first valve chamber 71a. doing.

As shown in FIGS. 2 to 4, the first valve body 65 is housed inside the first valve chamber 71a. As a result, the first valve body 65 can slide inside the first valve chamber 71a in the axial direction of the valve case 63, that is, in the vertical direction of the compressor. The first valve body 65 includes a cylindrical first valve wall 65a and a disk-shaped first lid portion 65b that is integrated with the first valve wall 65a at the upper part of the first valve wall 65a. The first valve wall 65a is an example of the "valve wall" of the present invention. The first valve wall 65a has an outer peripheral surface 651 and an inner peripheral surface 652. Further, the first lid portion 65b is provided with a punch hole 65c and a spring seat 65d. The withdrawal hole 65c communicates the suction port 633 with the first valve chamber 71a.

The first valve wall 65a intersects each suction window 73a and each start-up open path 73b in the axial direction of the valve case 63 by accommodating the first valve body 65 inside the first valve chamber 71a. They overlap in the direction, that is, in the radial direction of the valve case 63.

The second valve body 67 is housed inside the second valve chamber 71b. As a result, the second valve body 67 can slide inside the second valve chamber 71b in the axial direction of the valve case 63, that is, in the vertical direction of the compressor. The second valve body 67 includes a cylindrical second valve wall 67a and a disk-shaped second lid portion 67b that is integrated with the second valve wall 67a at the lower part of the second valve wall 67a.

The second valve wall 67a is adapted to overlap with each bleed window 73c in the radial direction of the valve case 63 by accommodating the second valve body 67 inside the second valve chamber 71b. Further, the second lid portion 67b is provided with a first pore 67c. The first pore 67c is an example of the "pore" of the present invention. The first pore 67c communicates the communication window 73d and the second valve chamber 71b in the axial direction of the valve case 63. In this way, the first pore 67c communicates the inside of the second valve chamber 71b with the outside of the second valve chamber 71b. The shape and the like of the first pore 67c can be appropriately designed.

The urging spring 69 is held between the spring seat 65d of the first valve body 65 and the second lid portion 67b of the second valve body 67, and holds the first valve body 65 and the second valve body 67. It is separated by its urging force.

In this way, the first valve body 65 is housed inside the first valve chamber 71a, and the second valve body 67 is housed inside the second valve chamber 71b, so that the first valve chamber 65 and the first valve chamber 65 and the second valve body 67 are housed. In the two valve chamber 67, the damper chamber 60 is partitioned by the first valve body 65 and the second valve body 67.

Further, a bypass path 81 is formed in the first valve wall 65a. The bypass path 81 includes a peripheral groove 81a and a communication hole 81b. As shown in FIG. 2, the peripheral groove 81a is recessed in the outer peripheral surface 651 of the first valve wall 65a. As shown in FIG. 5, the peripheral groove 81a is formed in an annular shape around the outer peripheral surface 651 in the circumferential direction. As shown in FIGS. 2 to 5, the peripheral groove 81a can face each suction window 73a and each start-up open path 73b by sliding the first valve body 65 inside the first valve chamber 71a. It has become. As shown in FIG. 2, the communication hole 81b extends in the radial direction of the first valve wall 65a while being connected to the peripheral groove 81a, and opens to the inner peripheral surface 652 of the first valve wall 65a. As a result, the communication hole 81b communicates the peripheral groove 81a with the damper chamber 60. The shape of the bypass path 81 can be appropriately designed.

Here, as shown in FIG. 5, in the opening degree adjusting valve 61, the first valve body 65 slides inside the first valve chamber 71a in the axial direction of the valve case 63, so that the first valve wall 65a is formed. , The region overlapping each suction window 73a and each start-up open path 73b is changed. As a result, the first valve body 65 changes the opening degree of each suction window 73a and each start-up open path 73b. Specifically, as shown in FIG. 5A, the first valve body 65 is in an upper position inside the first valve chamber 71a, and the first valve body 65 and the support 63c are in contact with each other. Occasionally, the first valve wall 65a closes each suction window 73a by overlapping the entire area of each suction window 73a. As a result, the first valve body 65 minimizes the opening degree of each suction window 73a. Further, since the first valve body 65 is in the upper position in the first valve chamber 71a, the peripheral groove 81a of the bypass path 81 is located above each suction window 73a, so that the bypass path 81 has each suction window. It is in a state where it does not face either the 73a or the open road 73b at the time of activation. On the other hand, in this state, since the region of the first valve wall 65a overlapping with each start-up open path 73b is the smallest, the first valve wall 65a opens each start-up open path 73b greatly. As a result, the first valve body 65 maximizes the opening degree of each start-up open path 73b.

Then, as the first valve body 65 slides inside the first valve chamber 71a toward the flange 75, the region of the first valve wall 65a that overlaps with each start-up open path 73b gradually increases. Therefore, the first valve body 65 gradually reduces the opening degree of each start-up open path 73b. At this time, although the first valve wall 65a overlaps the entire area of each suction window 73a, the bypass passage 81 and each suction window 73a communicate with each other as the bypass passage 81 and each suction window 73a gradually start to face each other. Begin to. After that, the first valve body 65 further slides inside the first valve chamber 71a toward the flange 75, so that the bypass passage 81 and each suction window 73a communicate with each other as shown in FIG. 5 (b). The area gradually increases. Then, in the first valve wall 65a, the region overlapping each suction window 73a begins to gradually become smaller. Therefore, the first valve body 65 makes the opening degree of each suction window 73a larger than the minimum. At this time, since the first valve wall 65a overlaps the entire area of each start-up open path 73b, each start-up open path 73b is closed by the first valve wall 65a. In this way, the first valve body 65 minimizes the opening degree of each start-up open path 73b.

Further, as shown in FIG. 5 (c), when the first valve body 65 is in the lower position inside the first valve chamber 71a and the first valve body 65 and the flange 75 are in contact with each other, the first valve body 65 is in contact with the first valve body 65. Since the valve wall 65a does not overlap with each suction window 73a, the first valve wall 65a opens each suction window 73a greatly. As a result, the first valve body 65 maximizes the opening degree of each suction window 73a. Further, the bypass path 81 faces each start-up open path 73b.

Further, in the opening degree adjusting valve 61, the second valve body 67 slides inside the second valve chamber 71b in the axial direction of the valve case 63, so that the second valve wall 67a overlaps with each bleed window 73c. To change. As a result, the second valve body 67 changes the opening degree of each bleeding window 73c. Specifically, as shown in FIGS. 5A to 5C, the second valve body 67 is located at a lower position inside the second valve chamber 71b, and the second valve body 67 and the lid 63b are in a lower position. Since the second valve wall 67a does not overlap with each air extraction window 73c when they are in contact with each other, the second valve wall 67a is largely opened to each air extraction window 73c. As a result, the second valve body 67 maximizes the opening degree of each bleed window 73c. Further, since the second valve body 67 slides inside the second valve chamber 71b toward the flange 75, the second valve wall 67a gradually starts to overlap with each bleed window 73c, so that the second valve wall 67a , Each bleed window 73c gradually begins to close. Therefore, the second valve body 67 gradually reduces the opening degree of each bleed window 73c. Then, as shown in FIG. 5D, when the second valve body 67 is in the upper position inside the second valve chamber 71b and the second valve body 67 and the flange 75 are in contact with each other, the second valve body 67 is in contact with the second valve chamber 71b. The second valve wall 67a closes each bleed window 73c because the valve wall 67a overlaps the entire area of each bleed window 73c. As a result, the second valve body 67 minimizes the opening degree of each bleed window 73c. Further, as the second valve body 67 slides inside the second valve chamber 71b toward the flange 75 in this way, the spring load of the urging spring 69 acting on the first valve body 65 increases. Therefore, the first valve body 65 slides inside the first valve chamber 71a toward the support 63c. When the second valve body 67 is in the upper position inside the second valve chamber 71b, the first valve body 65 is in the upper position in the first valve chamber 71a, and the opening degree of each suction window 73a is minimized. To do. In FIG. 5, in order to facilitate the explanation, the shapes of the first and second valve bodies 65, 67 and the like are shown in a simplified manner, and the illustration of the first pore 67c and the like is omitted.

As shown in FIG. 2, in this compressor, the suction passage is provided by the opening 47a of the valve accommodating chamber 47, the suction port 633 of the support 63c, the first valve chamber 71a, each suction window 73a, and the first valve accommodating chamber 47b. 51 is configured. That is, each suction window 73a communicates the first valve chamber 71a in the radial direction of the valve case 63 with the downstream side of the suction passage 51, that is, the suction chamber 5a side of the suction passage 51. Further, each start-up open path 73b also communicates the first valve chamber 71a with the suction chamber 5a side of the suction passage 51 in the radial direction of the valve case 63. On the other hand, the suction port 633 communicates the first valve chamber 71a in the axial direction of the valve case 63 with the upstream side of the suction passage 51, that is, the evaporator 101 side of the suction passage 51.

Then, in this compressor, the suction pressure Ps before being sucked into the compressor acts on the upper surface of the first valve body 65. As a result, the first valve body 65 changes the opening degree of each suction window 73a as described above, and changes the communication area between the first valve chamber 71a and the suction chamber 5a side of the suction passage 51, thereby changing the opening degree. The adjusting valve 61 changes the opening degree of the suction passage 51. Further, in the opening degree adjusting valve 61, the first valve body 65 changes the opening degree of the open passage 73b at each start-up to increase the communication area between the first valve chamber 71a and the suction chamber 5a side of the suction passage 51. Change.

Further, as shown in FIGS. 1 and 2, the rear housing 5 is formed with a first passage 57 and a second passage 59. One side of the first passage 57 is open to the crank chamber 15, and the other side is open to the second valve accommodating chamber 47c. Here, the other side of the first communication passage 57 opens into the second valve accommodating chamber 47c in the radial direction of the valve case 63 and the valve accommodating chamber 47. As a result, the first communication passage 57 communicates the crank chamber 15 with the second valve chamber 71b of the opening degree adjusting valve 61 through the second valve accommodating chamber 47c and each air extraction window 73c. In this compressor, the first communication passage 57, the second valve accommodating chamber 47c, each bleed window 73c, the second valve chamber 71b, the first valve chamber 71a, the bypass path 81, each start-up open path 73b and the first valve accommodating. The chamber 47b constitutes the bleed air passage 52. Then, the second valve body 67 changes the opening degree of each air extraction window 73c as described above, and the communication area between the first communication passage 57 and the second valve chamber 71b is changed, so that the opening degree adjusting valve 61 is changed. , The opening degree of the bleed air passage 52 is changed.

One side of the second continuous passage 59 is connected to the second air supply passage 43, and the other side is open to the second valve accommodating chamber 47c. As a result, the second communication passage 59 communicates the second air supply passage 43 with the second valve chamber 71b of the opening degree adjusting valve 61 through the second valve accommodating chamber 47c and the communication window 73d. Therefore, the control pressure Pcv in the second air supply passage 43 acts on the second lid portion 67b of the second valve body 67.

In this compressor, the drive shaft 19 is rotationally driven by the engine or motor of the vehicle, the lug plate 21 and the swash plate 23 are rotated, and each piston 33 reciprocates in the cylinder bore 7a. At this time, each piston 33 reciprocates in the cylinder bore 7a with a stroke corresponding to the inclination angle of the swash plate 23. Therefore, each piston 33 sucks the refrigerant in the suction chamber 5a into the compression chamber 35, compresses the refrigerant in the compression chamber 35, and discharges the high-pressure refrigerant from the compression chamber 35 to the discharge chamber 5b.

During this period, in this compressor, the discharge capacity can be appropriately changed by adjusting the crank chamber pressure Pc of the crank chamber 15 by the capacitance control valve 13. For example, if the capacity control valve 13 increases the communication area between the first air supply passage 41 and the second air supply passage 43, the refrigerant having the discharge pressure Pd in the discharge chamber 5b can easily flow into the crank chamber 15. The crank chamber pressure Pc becomes high. In this case, the inclination angle of the swash plate 23 becomes small, and the discharge capacity per rotation of the drive shaft 19 becomes small. Further, if the capacity control valve 13 reduces the communication area between the first air supply passage 41 and the second air supply passage 43, it becomes difficult for the refrigerant having the discharge pressure Pd to flow into the crank chamber 15. Therefore, the refrigerant in the crank chamber 15 easily flows out to the suction chamber 5a through the bleed air passage 52, and the crank chamber pressure Pc becomes low. In this case, the inclination angle of the swash plate 23 becomes large, and the discharge capacity becomes large.

Further, in this compressor, a set suction pressure and a set crank chamber pressure are preset. The magnitudes of the set suction pressure and the set crank chamber pressure can be set as appropriate.

When the compressor is stopped in the minimum capacity state and stopped for a long time, the refrigerant in the crank chamber 15 may be cooled to become a liquid refrigerant. When it is started next, the suction pressure Ps of the refrigerant taken into the suction chamber 5a is lower than the set suction pressure, and the crank chamber pressure Pc is lower than the set crank chamber pressure. At this time, the crank chamber pressure Pc is higher than the control pressure Pcv in the second air supply passage 43.

At the time of such activation, in the opening degree adjusting valve 61, as shown in FIGS. 2 and 5A, the first valve body 65 is located at the upper position in the first valve chamber 71a, so that the first valve is the first valve. The wall 65a closes each suction window 73a, so that the opening degree of each suction window 73a is minimized. As a result, the opening degree adjusting valve 61 minimizes the opening degree of the suction passage 51. Therefore, in this compressor, the pressure fluctuation of the suction pressure Ps at the time of starting can be reduced.

Further, at the time of start-up, the second valve body 67 is located at a lower position in the second valve chamber 71b, so that the second valve wall 67a opens each bleed window 73c. Therefore, the opening degree of each bleeding window 73c is maximized. As a result, the second valve body 67 maximizes the communication area between the first communication passage 57 and the second valve chamber 71b. That is, the opening degree adjusting valve 61 increases the opening degree of the bleeding passage 52. Here, in a state where the first valve wall 65a closes each suction window 73a, the first valve wall 65a opens each start-up open path 73b, so that the opening degree of each start-up open path 73b is maximum. Become. Therefore, the liquid refrigerant and the like accumulated in the crank chamber 15 at the time of starting are collected in the first passage 57, the second valve accommodating chamber 47c, each air extraction window 73c, the second valve chamber 71b, the first valve chamber 71a, and each starting. It quickly moves to the suction chamber 5a side of the suction passage 51, and eventually to the suction chamber 5a, via the open path 73b. Further, the liquid refrigerant or the like also reaches the suction chamber 5a by circulating a clearance inevitably formed between the first valve chamber 71a and the first valve body 65. As a result, in this compressor, the crank chamber pressure Pc is rapidly lowered, so that the capacity can be easily increased quickly.

Then, the discharge capacity starts to increase, and the suction pressure Ps starts to become larger than the set suction pressure, so that the first valve body 65 slides in the first valve chamber 71a toward the flange 75. Therefore, as shown in FIG. 5B, the first valve wall 65a starts to open each suction window 73a. That is, the opening degree of each suction window 73a is larger than the minimum. At this time, each start-up open path 73b is closed by the first valve wall 65a, so that the opening degree thereof is minimized. As a result, the leakage of the refrigerant from each start-up open path 73b is almost eliminated.

Further, when the capacity is large, including the maximum capacity, the suction pressure Ps becomes higher than the set suction pressure. On the other hand, the crank chamber pressure Pc becomes lower than the set crank chamber pressure. At this time, the crank chamber pressure Pc becomes higher than the control pressure Pcv in the second air supply passage 43 due to the influence of blow-by gas or the like from each compression chamber 35. Then, at the maximum capacity, the opening degree adjusting valve 61 is in the state shown in FIGS. 3 and 5 (c).

As described above, at the maximum capacity, the first valve body 65 is located at a lower position in the first valve chamber 71a, so that the first valve wall 65a greatly opens each suction window 73a. Therefore, the opening degree of each suction window 73a is maximized. As a result, the opening degree adjusting valve 61 maximizes the opening degree of the suction passage 51. In this way, in this compressor, it is possible to prevent the pressure loss of the suction pressure Ps at the time of a large capacity including the time of the maximum capacity. At the maximum capacity, the first valve wall 65a maintains a state in which the open passage 73b at each start-up is closed.

Further, at the maximum capacity, the second valve body 67 is located at a lower position in the second valve chamber 71b, and the second valve wall 67a opens each air extraction window 73c. If the compressor is operating in the maximum capacity state, the inclination angle of the swash plate 23 is the maximum. Therefore, the high-pressure refrigerant in the discharge chamber 5b opens the check valve 55 shown in FIG. 1 and the condenser 102. Is discharged to.

On the other hand, when the capacity is small, including the minimum capacity, the crank chamber pressure Pc becomes higher than the set crank chamber pressure. At this time, since the capacity control valve 13 increases the communication area between the first air supply passage 41 and the second air supply passage 43, the control pressure Pcv in the second air supply passage 43 is the crank chamber pressure Pc. Will be higher than. Then, at the minimum capacity, the opening degree adjusting valve 61 is in the state shown in FIGS. 4 and 5 (d). In this case, the second valve body 67 is located in the upper position in the second valve chamber 71b, and the first valve body 65 is located in the upper position in the first valve chamber 71a due to the spring load of the urging spring 69. Therefore, since each suction window 73a is closed by the first valve wall 65a, the opening degree adjusting valve 61 reduces the opening degree of the suction passage 51. Therefore, the pressure fluctuation of the suction pressure Ps is reduced even when the capacity is small, including when the capacity is the minimum.

Further, at this time, since the second valve body 67 is located at an upper position in the second valve chamber 71b due to the control pressure Pcv, the second valve wall 67a closes each bleed window 73c. Therefore, the opening degree of each bleeding window 73c is minimized. As a result, the communication area between the first communication passage 57 and the second valve chamber 71b is minimized. That is, the opening degree adjusting valve 61 closes the bleed passage 52. Therefore, it becomes difficult to recompress the high-pressure refrigerant in the crank chamber 15 at the minimum capacity or the small capacity, and the volumetric efficiency of this compressor is improved.

At this time, the capacity control valve 13 can quickly increase the crank chamber pressure Pc, and the discharge capacity can be quickly changed from a large capacity to a small capacity.

Further, in this compressor, it is not necessary to provide an bleed valve that can close the bleed passage 52 as needed, separately from the opening degree adjusting valve 61. Therefore, the number of parts can be reduced, and the degree of freedom in design is less likely to decrease.

Then, in this compressor, the pressure in the first valve chamber 71a and the pressure in the second valve chamber 71b, that is, the pressure in the damper chamber 60 is suitably adjusted by the bypass passage 81 and each start-up open passage 73b. Can be done. That is, as shown in FIGS. 2, 5 (a) and 5 (d), when the first valve body 65 is in the upper position inside the first valve chamber 71a, the bypass passage 81 takes in each suction. Although it does not face the window 73a, in this case, the damper chamber 60 and the suction chamber 5a side of the suction passage 51 communicate with each other by each start-up open passage 73b. In this way, the pressure in the damper chamber 60 can be adjusted.

On the other hand, as the first valve body 65 slides inside the first valve chamber 71a toward the flange 75, each start-up open path 73b is gradually closed, but the bypass path 81 faces each suction window 73a. By doing so, the damper chamber 60 and the suction chamber 5a side of the suction passage 51 communicate with each other through the bypass path 81 and each suction window 73a. In this way, the pressure in the damper chamber 60 can be adjusted in this case as well. In the transitional period in which the first valve body 65 slides inside the first valve chamber 71a toward the flange 75, the bypass path 81 faces each suction window 73a, and each start-up open path 73b is slightly small. It will be in the open state.

Further, as shown in FIGS. 3 and 5 (c), when the first valve body 65 is in the lower position inside the first valve chamber 71a, the bypass path 81 faces each start-up open path 73b. As a result, the damper chamber 60 and the suction chamber 5a side of the suction passage 51 communicate with each other through the bypass path 81 and each start-up open path 73b. In this way, the pressure in the damper chamber 60 can be adjusted in this case as well.

Here, in this compressor, since the punch hole 65c is formed in the first lid portion 65b of the first valve body 65, the damper chamber 60 communicates with the evaporator 101 side of the suction passage 51 through the punch hole 65. There is a relationship to do. However, the punch hole 65c faces the flow of the refrigerant gas from the evaporator 101 to the suction chamber 5a. The pressure of the refrigerant gas from the evaporator 101 toward the suction chamber 5a is often higher than the pressure in the damper chamber 60. Therefore, it is difficult to adjust the pressure in the damper chamber 60 through the punch hole 65c, and when the damper effect becomes excessive, it is difficult to reduce the pressure in the damper chamber 60 depending on the punch hole 65c.

Further, in this compressor, the first valve body 65 is housed in the first valve chamber 71a, and the bypass path 81 is formed only in the first valve body 65. Therefore, in this compressor, when the opening degree adjusting valve 61 is attached to the rear housing 5, the bypass path 81 is not blocked by the rear housing 5, that is, the inner wall of the valve accommodating chamber 47. Therefore, the pressure in the damper chamber 60 does not become excessively high, and the damper effect based on the pressure in the damper chamber 60 is preferably exhibited. Therefore, in this compressor, the opening degree adjusting valve 61 is prevented from unnecessarily moving in the first valve chamber 71a when the capacity is small, including when the compressor is started and when the capacity is the minimum. Can preferably maintain a state in which the opening degree of the suction passage 51 is reduced. As a result, in this compressor, it is possible to reduce the suction pulsation at the time of a small volume due to the pressure fluctuation of the suction pressure Ps. Further, when the capacity is large, the first valve body 65 moves appropriately inside the first valve chamber 71a, so that the refrigerant can be suitably taken into the suction chamber 5a from the evaporator 101.

Then, in order to preferably exert the damper effect of the damper chamber 60 in this way, in this compressor, the mounting direction of the opening degree adjusting valve 61 with respect to the valve accommodating chamber 47 is regulated, and a groove or the like is formed in the rear housing 5. Therefore, it is not necessary to provide a gap between the valve accommodating chamber 47 and the valve case 63. Therefore, it is possible to facilitate the production.

Therefore, in the compressor of the first embodiment, the pressure loss of the suction pressure Ps at the time of a large capacity can be prevented, and the quietness at the time of a small capacity can be ensured. Further, in this compressor, the pressure fluctuation of the suction pressure Ps at the time of starting can be reduced. Then, in this compressor, it is possible to suppress an increase in manufacturing cost while suitably exerting the damper effect of the damper chamber 60.

In particular, in this compressor, the pressure in the damper chamber 60 can be adjusted by the bypass path 81 and each start-up open path 73b. Therefore, in adjusting the pressure in the damper chamber 60, it is not necessary to always face the bypass path 81 and the suction windows 73a. Therefore, in this compressor, it is possible to increase the degree of freedom in designing the opening degree adjusting valve 61.

Further, the bypass path 81 is composed of a peripheral groove 81a and a communication hole 81b, and the peripheral groove 81a is formed in an annular shape around the first valve wall 65a of the first valve body 65. Here, the bypass path 81 is configured as, for example, a vertical groove extending the outer peripheral surface 651 of the first wall portion 65a in the axial direction of the valve case 63 and communicating with each suction window 73c, each start-up open path 73b, and the damper chamber 60. It is also possible to do it. However, in such a bypass path 81, the first valve body 65 rotates around a rotation axis extending in the axial direction of the valve case 63 when the compressor is operated, so that each suction window 73a and each start-up open path 73b The phase shift with and is likely to occur. In this respect, in this compressor, since the peripheral groove 81a is formed in an annular shape that goes around the first valve wall 65a of the first valve body 65 once, when the first valve body 65 rotates when the compressor operates. Even if there is, the phase shift between the peripheral groove 81a and each suction window 73a and each start-up open path 73b does not occur. Therefore, even when the first valve body 65 rotates, the bypass path 81 can always face each suction window 73a and each start-up open path 73b.

Further, in this compressor, the first pore 67c is provided in the second lid portion 67b of the second valve body 67. The first pore 67c communicates the communication window 73d with the second valve chamber 71b. Therefore, in the opening degree adjusting valve 61, the control pressure Pcv decreases, and when the second valve body 67 moves in the second valve chamber 71b toward the lid 63b, the first pore 67c becomes the first valve. The pressure inside the chamber 71a and the second valve chamber 71b can be released to the outside of the second valve chamber 71b. In this respect as well, the compressor can suitably adjust the pressure in the damper chamber 60. Therefore, the second valve body 67 becomes easy to move, and the controllability is improved. Further, since the first pore 67c is provided in the second lid portion 67b, the refrigerant in the second air supply passage 43 communicates with the second communication passage 59 when the crank chamber pressure Pc has a minimum capacity lower than the control pressure Pcv. It flows into the second valve chamber 71b through the window 73d and the first pore 67c. This also makes it possible to suitably adjust the pressure in the damper chamber 60.

Further, each suction window 73a is formed in a substantially rectangular shape in which the opening area gradually decreases toward the support 63c. Therefore, as compared with the case where each suction window 73a is, for example, a simple square or the like, in this compressor, as the first valve wall 65a starts to open each suction window 73a, the suction chamber 5a side and the first suction passage 51 It is possible to suitably increase the communication area with the valve chamber 71a.

Further, the valve case 63 has a flange 75 between the first valve chamber 71a and the second valve chamber 71b, and the first valve has an inner diameter smaller than the outer diameter of the second valve body 67. The chamber 71a and the second valve chamber 71b are communicated with each other. Then, when the second valve body 67 is located in the upper position in the second valve chamber 71b and the first valve body 65 is located in the upper position in the first valve chamber 71a, the first valve body 67 has a first surface on the inner surface. A force of communication area S1 × suction pressure Ps acts, and a force of second communication area S2 × control pressure Pcv acts on the lower surface of the second valve body 67. Since the second valve body 67 has the first communication area S1 <the second communication area S2, the second valve body 67 reacts sensitively to a decrease in the control pressure Pcv. Therefore, it is easy to open the bleeding passage 52 again.

(Example 2)
As shown in FIGS. 6 to 8, in the compressor of the second embodiment, the start-up open path 73b is not formed in the valve case 63. Then, in this compressor, not only when the first valve body 65 is in the upper position in the first valve chamber 71a as shown in FIGS. 6 and 8, but also as shown in FIG. 7, the first valve body The bypass path 81 faces each suction window 73a even when 65 is in the lower position in the first valve chamber 71a. That is, in this compressor, the bypass path 81 always faces each suction window 73a regardless of the position of the first valve body 65 inside the first valve chamber 71a. That is, in this compressor, the sizes of the suction windows 73a and the first valve body 65 are designed so that the bypass passage 81 always faces the suction windows 73a. Other configurations in this compressor are the same as those in the compressor of the first embodiment, and the same configurations are designated by the same reference numerals and detailed description of the configurations will be omitted.

Similar to the compressor of the first embodiment, in this compressor as well, the first and second valve bodies 65 and 67 have the first and second valve chambers 71a and 71b at the time of starting, the small capacity, the maximum capacity and the minimum capacity. Move inside. Therefore, as shown in FIG. 6, the liquid refrigerant or the like accumulated in the crank chamber 15 at the time of starting is inevitably formed between the first valve chamber 71a and the first valve body 65, as well as a bypass path. It can be moved from 81 to the suction chamber 5a via each suction window 73a. That is, in this compressor, the bypass path 81 and each suction window 73a also function as the start-up open path 73b in the compressor of the first embodiment.

Then, in this compressor, the pressure in the damper chamber 60 can be adjusted by having the bypass path 81 always face each suction window 73a regardless of the position of the first valve body 65. Therefore, even with this compressor, the damper effect of the damper chamber 60 can be suitably exhibited. Other operations in this compressor are the same as those in the compressor of Example 1.

(Example 3)
As shown in FIGS. 9 and 10, the compressor of the third embodiment includes an opening degree adjusting valve 62 instead of the opening degree adjusting valve 61. Further, in this compressor, the first passage 58 is formed instead of the first passage 57. On the other hand, in this compressor, the second passage 59 is not formed in the rear housing 5.

One side of the first passage 58 is open to the crank chamber 15, and the other side is open to the second valve accommodating chamber 47c. Here, the other side of the first passage 58 opens into the second valve accommodating chamber 47c in the axial direction of the valve case 63 and the valve accommodating chamber 47.

As shown in FIG. 10, in the opening degree adjusting valve 62, unlike the opening degree adjusting valve 61, the bleeding window 73c is not formed in the small diameter portion 632 of the valve case 63. Further, the small diameter portion 632 is not provided with the O-ring grooves 77a and 77b and the O-rings 79a and 79b.

In the opening degree adjusting valve 62, an air extraction window 73e is formed on the lid 63b. That is, the bleeding window 73e is formed on the lower end surface of the valve case 63. As a result, the bleeding window 73e communicates the second valve chamber 71b with the first communication passage 58 in the axial direction of the valve case 63. Further, since the air extraction window 73e is formed in the lid body 63b, the second lid portion 67b of the second valve body 67 faces the air extraction window 73e in the axial direction of the valve case 63 in the second valve chamber 71b. ing. The second lid portion 67b is provided with a second pore 67d. The second pore 67d is also an example of the "pore" of the present invention. The second pore 67d communicates the bleeding window 73e and the second valve chamber 71b in the axial direction of the valve case 63. The shape and the like of the second pore 67d can be appropriately designed.

Further, in the opening degree adjusting valve 62, the opening path 73b at startup is not formed in the valve case 63. Therefore, as in the compressor of the second embodiment, as shown in FIGS. 10 to 12, each of the bypass paths 81 is provided in this compressor regardless of the position of the first valve body 65 in the first valve chamber 71a. It always faces the suction window 73a.

In this compressor, the first passage 58, the second valve accommodating chamber 47c, the bleed window 73e, the second pore 67d, the second valve chamber 71b, the first valve chamber 71a, the bypass path 81, each suction window 73a and the first The bleed air passage 52 is configured by the one-valve accommodating chamber 47b. Other configurations in this compressor, including other configurations of the opening degree adjusting valve 62, are the same as those of the compressor of the first embodiment.

In this compressor, the set crank chamber pressure is adjusted by the urging force of the urging spring 69. Then, in this compressor, the crank chamber pressure Pc acts on the second lid portion 67b of the second valve body 67 through the first continuous passage 58, the second valve accommodating chamber 47c and the bleed air window 73e.

In this compressor, at startup, the suction pressure Ps of the refrigerant taken into the suction chamber 5a is lower than the set suction pressure, and the crank chamber pressure Pc is lower than the set crank chamber pressure. Therefore, in the opening degree adjusting valve 62, as shown in FIG. 10, the first valve body 65 is located at an upper position in the first valve chamber 71a. As a result, the first valve wall 65a closes each suction window 73a. That is, the opening degree of each suction window 73a is minimized. In this way, the opening degree adjusting valve 62 reduces the opening degree of the suction passage 51. As a result, in this compressor, the pressure fluctuation of the suction pressure Ps at the time of starting is reduced. Further, at the time of activation, since the second valve body 67 is located at a lower position in the second valve chamber 71b, the second valve body 67 closes the bleeding window 73e. The liquid refrigerant or the like that can be filled in the crank chamber 15 at the time of start-up reaches the air extraction window 73e through the first continuous passage 58, and then, in addition to the second pore 67d, the second valve chamber 71b and the second valve body. By circulating a clearance inevitably formed between 67 and between the first valve chamber 71a and the first valve body 65, etc., the liquid can flow out to the suction chamber 5a.

On the other hand, when the capacity is large, including the maximum capacity, the suction pressure Ps is higher than the set suction pressure, and the crank chamber pressure Pc is lower than the set crank chamber pressure. Then, at the maximum capacity, as shown in FIG. 11, the first valve body 65 is located at the lower position in the first valve chamber 71a, so that the opening degree of each suction window 73a is maximized. As a result, the opening degree adjusting valve 62 increases the opening degree of the suction passage 51. In this way, even with this compressor, it is possible to prevent the pressure loss of the suction pressure Ps at the time of a large capacity including the maximum capacity.

Further, when the capacity is small, including the minimum capacity, the crank chamber pressure Pc becomes higher than the set crank chamber pressure. Then, at the minimum capacity, as shown in FIG. 12, the second valve body 67 is in the upper position inside the second valve chamber 71b, and the first valve body 65 is moved to the first position by the spring load of the urging spring 69. 1 It is in the upper position inside the valve chamber 71a. Therefore, each suction window 73a is closed by the first valve wall 65a, so that the opening degree adjusting valve 62 reduces the opening degree of the suction passage 51. Therefore, the pressure fluctuation of the suction pressure Ps is reduced even when the capacity is small, including when the capacity is the minimum.

Then, in this compressor, as in the compressor of the second embodiment, the bypass path 81 always faces each suction window 73a regardless of the position of the first valve body 65, so that the inside of the first valve chamber 71a and the first valve chamber 71a 2 The pressure in the valve chamber 71b can be adjusted.

Further, in this compressor, a second pore 67d is provided in the second lid portion 67b of the second valve body 67. Therefore, even if the second valve body 67 closes the bleeding window 73e, the bleeding window 73e and the second valve chamber 71b communicate with each other by the second pore 67d. Therefore, in the opening degree adjusting valve 62, when the crank chamber pressure Pc decreases and the second valve body 67 moves in the second valve chamber 71b toward the lid 63b, that is, the second valve body 67 draws air. When moving in the second valve chamber 71b so as to close the window 73e, the second pore 67d may release the pressure in the first valve chamber 71a and the second valve chamber 71b to the outside of the second valve chamber 71b. it can. When the crank chamber pressure Pc is lower than the set crank pressure, the refrigerant in the first communication passage 58 flows into the second valve chamber 71b through the bleed window 73e and the second pore 67d. With these, the pressure in the damper chamber 60 can be suitably adjusted in this compressor. Other operations in this compressor are the same as those in the compressor of Example 1.

In the above, the present invention has been described with reference to Examples 1 to 3, but the present invention is not limited to the above Examples 1 to 3, and can be appropriately modified and applied without departing from the spirit thereof. Needless to say.

For example, in the compressor of the first embodiment, when the first valve body 65 is located at the upper position in the first valve chamber 71a, a part of the peripheral groove 81a of the bypass path 81 faces each suction window 73a. It may be configured. Further, when the first valve body 65 is located at a lower position in the first valve chamber 71a, a part of the peripheral groove 81a may be configured to face each start-up open path 73b.

Further, in the compressors of Examples 2 and 3, when the first valve body 65 is located at the upper position or the lower position inside the first valve chamber 71a, a part of the peripheral groove 81a of the bypass path 81 sucks in each suction. It may be configured to face the window 73a.

Further, in the compressor of the first embodiment, the peripheral groove 81a is formed in an annular shape around the outer peripheral surface 651 of the first valve wall 65a in the circumferential direction, but the peripheral groove 81a is not limited to this. The shape may extend 651 in the circumferential direction to about half a circumference. Further, the bypass path 81 may be composed of only the communication holes 81b. The same applies to the compressors of Examples 2 and 3.

Further, in the compressor of the first embodiment, the suction chamber 5a integrally has the valve accommodating chamber 47. However, the present invention is not limited to this, and the suction chamber 5a and the valve accommodating chamber 47 may be separated from each other, and the suction chamber 5a and the valve accommodating chamber 47 may communicate with each other by a passage. The same applies to the compressors of Examples 2 and 3.

Further, in the compressor of the first embodiment, each start-up open path 73b is formed in the valve case 63, but the present invention is not limited to this, and the start-up open path 73b may be formed in the first valve body 65. Further, the valve case 63 and the first valve body 65 may each have a start-up open path 73b.

Further, in the compressor of the first embodiment, when the first valve body 65 starts to open each suction window 73a, that is, the first valve body 65 makes the opening degree of each suction window 73a larger than the minimum. It is configured so that the opening degree of each open path 73b at startup is minimized. However, not limited to this, when the first valve body 65 starts to open each suction window 73a, the opening degree of each start-up opening path 73b is not the minimum, but the opening degree is smaller than the maximum. You may.

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

1 ... Housing 5a ... Suction chamber 5b ... Discharge chamber 7a ... Cylinder bore 13 ... Capacity control valve 15 ... Crank chamber 23 ... Swash plate 33 ... Piston 35 ... Compression chamber 41 ... First air supply passage (air supply passage)
43 ... Second air supply passage (air supply passage)
51 ... Suction passage 52 ... Extraction passage 60 ... Damper chambers 61, 62 ... Opening adjustment valve 63 ... Valve case 64 ... Valve body 65 ... First valve body 65a ... First valve wall (valve wall)
67 ... Second valve body 67c ... First pore (pore)
67d ... Second pore (pore)
69 ... Biasing spring 71a ... 1st valve chamber 71b ... 2nd valve chamber 73a ... Suction window 73c, 73e ... Extraction window 81 ... Bypass path 81a ... Circumferential groove 81b ... Communication hole 100 ... External circuit 633 ... Suction port

Claims (5)

A housing in which a suction chamber, a cylinder bore, a crank chamber and a discharge chamber are formed,
A swash plate provided in the crank chamber and whose inclination angle is changed by the crank chamber pressure in the crank chamber.
A piston that is housed in the cylinder bore while engaging with the swash plate and forms a compression chamber with the housing.
It is equipped with a capacitance control valve that can change the crank chamber pressure.
The housing includes a suction passage connecting the external circuit and the suction chamber, an air supply passage connecting the discharge chamber and the crank chamber via the capacitance control valve, and the crank chamber and the suction chamber. A bleed passage connecting the
In the variable capacity swash plate type compressor further provided with an opening degree adjusting valve for changing the opening degree of the suction passage.
The opening degree adjusting valve has a tubular valve case and a valve body housed in the valve case.
The valve case has a first valve chamber that forms a part of the suction passage, a second valve chamber that communicates with the first valve chamber and forms a part of the bleed air passage, and an opening on the peripheral surface. A suction window that communicates the first valve chamber and the suction chamber side of the suction passage, and a suction port that opens at the end face and communicates between the first valve chamber and the external circuit side of the suction passage. An air extraction window that opens to the peripheral surface or the end surface and communicates the second valve chamber and the air extraction passage is formed.
The valve body includes a first valve body slidable inside the first valve chamber, a second valve body slidable inside the second valve chamber, and the first valve body and the second valve body. It has a first valve body and an urging spring that urges the second valve body so as to be separated from the valve body.
The first valve body has a valve wall that changes the region overlapping with the suction window by sliding the first valve body inside the first valve chamber.
In the first valve chamber and the second valve chamber, a damper chamber is partitioned by the first valve body and the second valve body.
A variable-capacity swash plate compressor characterized in that a bypass path extending in the circumferential direction and facing the suction window to communicate the damper chamber and the suction window is formed on the valve wall. .. The variable capacity swash plate compressor according to claim 1, wherein at least a part of the bypass path faces the suction window regardless of the position of the first valve body. The variable capacity swash plate compressor according to claim 1 or 2, wherein pores communicating the inside of the second valve chamber and the outside of the second valve chamber are formed in the second valve body. The valve wall has a tubular shape,
The bypass path has a peripheral groove extending in the circumferential direction of the valve wall and facing the suction window, and a communication hole formed in the valve wall and communicating the peripheral groove and the damper chamber. Item 3. The variable capacity swash plate compressor according to any one of Items 1 to 3. The variable capacity swash plate compressor according to claim 4, wherein the peripheral groove is formed in an annular shape.

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