TWI704292B - Pressure booster - Google Patents

Abstract

A pressure booster (10) including a pressure boosting cylinder (12) with driving cylinders (14, 16) arranged on both sides, wherein the pressure booster is equipped with a pair of pilot valves (72, 74) having knock pins (90), against which pistons (36, 38) of the driving cylinders abut at moving ends thereof, and a pair of operating valves (48, 52) that switch a supply state of a pressure fluid to a pressurized chambers (24a, 26a) of the driving cylinders, and when the knock pin is pressed by the piston to switch one or the other of the pilot valves to a first position, the supply state of the pressure fluid to the pair of the operating valves is switched and a predetermined fluid pressure is applied to the knock pin to keep the pilot valve at the first position.

Description

Booster

The present invention relates to a pressurizing device that pressurizes and outputs pressure fluid.

[Related technical description]

In the prior art, a pressurizing device that continuously pressurizes and outputs the pressure fluid by the reciprocating action of the piston is known.

For example, Japanese Patent Application Laid-Open No. 08-21404 describes a supercharger in which a pair of pressure-increasing cylinders in which each piston is directly connected to a piston rod are arranged to face each other, and between the pair of pressure-increasing cylinders Equipped with a cylinder for energy recovery. This supercharger injects compressed air into the compression chamber and action chamber of one supercharging cylinder and the compression chamber of the other supercharging cylinder, and the air that has been injected into the compression chamber of one supercharging cylinder Boost and output. The air supply switching action for the booster cylinder and the flow path switching action for the retracting cylinder are performed by detecting the piston position of the booster cylinder with a reed switch and turning the solenoid of the switching valve ON-OFF. .

In the supercharger of Japanese Patent Laid-Open No. 08-21404, the action chamber for driving the piston and the compression chamber for compressing the fluid are provided in a pair of pressurizing cylinders, and there is a concern that the degree of freedom of design is limited. Furthermore, reed switches and solenoids are used to perform the switching operation, and therefore, electrical means including electrical wiring must be included.

In this regard, the applicant in this case filed an invention patent application for the invention of a pressure booster device that separately sets up a cylinder for driving the piston and a cylinder for compressing pressure fluid and arranges these closely interactively without relying on electrical means for switching operations. (Japan Special Application No. 2017-164945).

The pressure boosting device of the above patent application is provided with: a pair of pilot valves, the driving cylinder is arranged on both sides of the pressure boosting cylinder, and the piston of the driving cylinder is provided with a push rod abutting with its moving end; And a pair of operating valves switch the supply state of the pressure fluid from the pressure fluid supply source to the pressure chamber of the driving cylinder.

In the supercharging device of the aforementioned patent application, when the output of the supercharging device is close to the saturated state, the force of the piston of the driving cylinder to push the push rod will be weakened, and in the state where the pilot valve is not fully switched, the push rod The situation being pushed back by elastic force is not satisfactory. The present invention was developed in view of this situation, and aims to provide a pressure boosting device that can reliably switch the pilot valve even when the force of the piston of the driving cylinder to push the pilot valve is weak.

The pressure boosting device of the present invention is equipped with driving cylinders on both sides of the pressure boosting cylinder. The pressure boosting device is provided with a pair of pilot valves, which are abutted by the piston of the driving cylinder with their moving ends. The control pin; and a pair of action valves, which switch the supply state of the pressure fluid from the pressure fluid supply source to the pressure chamber of the driving cylinder; when the piston pushes the control pin, the pilot valve of one or the other is switched to the first At one position, it is switched to a state where pressure fluid is supplied to a pair of action valves, and a predetermined fluid pressure is applied to the control pin to keep the pilot valve in the first position.

According to the above-mentioned pressurizing device, the control pin abutting on the piston of the driving cylinder can be pushed to the end with a predetermined fluid pressure, and the pilot valve can be maintained at a fully switching position.

According to the pressurizing device of the present invention, because a predetermined fluid pressure acts on the control pin to keep the pilot valve in the switched position, even if the force of the piston of the driving cylinder to push the control pin is weak, the control can be controlled The pin is pushed to the end, and the pilot valve is surely switched.

The description of the following preferred embodiments in conjunction with the drawings should clarify the above-mentioned objectives, features and advantages.

10‧‧‧Boosting device

12‧‧‧Pressurized cylinder

14‧‧‧The first drive cylinder

16‧‧‧Second drive cylinder

18‧‧‧First cover member

20‧‧‧Second cover member

22‧‧‧Pressure chamber

22a‧‧‧First pressurization chamber

22b‧‧‧Second plenum

24‧‧‧First Drive Room

24a、26a‧‧‧Pressure chamber

24b, 26b‧‧‧Back pressure chamber

26‧‧‧Second Drive Room

28‧‧‧The third cover member

30‧‧‧Wall

32‧‧‧Piston rod

34‧‧‧Piston for pressurization

36‧‧‧Piston for the first drive

38‧‧‧Second drive piston

40‧‧‧Supply Port

42a‧‧‧First supply flow path

42b‧‧‧Second supply flow path

42c‧‧‧First supply check valve

42d‧‧‧Second supply check valve

44‧‧‧Output port

46a‧‧‧First output channel

46b‧‧‧Second output channel

46c‧‧‧First output check valve

46d‧‧‧Second output check valve

48‧‧‧First action valve

50‧‧‧First shell

52‧‧‧Second action valve

54‧‧‧Second shell

56F‧‧‧ Pilot port

58a to 58e‧‧‧Flow path

60‧‧‧The first fixed throttle

62‧‧‧First silencer

56A, 64A‧‧‧First port

56B, 64B‧‧‧Second port

56C, 64C‧‧‧third port

56D, 64D‧‧‧4th port

56E, 64E‧‧‧Port 5

64F‧‧‧ Pilot port

66a to 66e‧‧‧flow path

68‧‧‧Second fixed throttle

70‧‧‧Second silencer

72‧‧‧First pilot valve

74‧‧‧Second pilot valve

76A, 80A‧‧‧First port

76B, 80B‧‧‧Second port (supply port)

76C, 80C‧‧‧third port

76D, 80D‧‧‧Fourth port (connecting port)

78a‧‧‧Flow Path

78b‧‧‧First guide flow path

78c‧‧‧Branch flow path

82a‧‧‧Flow Path

82b‧‧‧Second guide flow path

82c‧‧‧Branch flow path

84‧‧‧Valve receiving hole

84a‧‧‧Large diameter hole

84b‧‧‧Small diameter hole

84c‧‧‧Pitch hole

86‧‧‧Valve seat

86a‧‧‧Annular groove

86b‧‧‧Annular recess

86c‧‧‧First through hole

86d‧‧‧Second through hole

88‧‧‧Valve seat pressure piece

90‧‧‧Control pin

90a‧‧‧Large diameter shaft

90b‧‧‧Pitch diameter shaft

90c‧‧‧Small diameter shaft

90d‧‧‧Annular groove

90e‧‧‧Segment difference

92‧‧‧Fixed ring

94a‧‧‧First seal

94b‧‧‧Second seal

96a‧‧‧Third seal

96b‧‧‧Fourth seal

98a‧‧‧First liner

98b‧‧‧Second liner

98c‧‧‧third liner

A1, A2‧‧‧direction

Figure 1 is a perspective view of the appearance of a supercharging device according to an embodiment of the present invention.

Figure 2 is a side view of the supercharging device of Figure 1.

Figure 3 is a cross-sectional view taken along the line III-III of Figure 2.

Figure 4 is a cross-sectional view taken along the line IV-IV in Figure 2.

Fig. 5 is an overall schematic diagram of the supercharging device of Fig. 1 shown in a fluid circuit diagram.

Figure 6 is a cross-sectional view of the first pilot valve of the pressurizing device of Figure 1.

Figure 7 is a diagram when the control pin of the first pilot valve corresponding to Figure 6 moves to another position.

Figure 8 is a diagram when the control pin of the first pilot valve corresponding to Figure 6 is moved to another position.

Fig. 9 is a diagram when the supercharging device corresponding to Fig. 5 is changed from the state of Fig. 5 to another state.

Hereinafter, with reference to the drawings, a detailed description will be given of the preferred embodiments of the supercharging device of the present invention. The supercharging device 10 of the embodiment of the present invention is arranged between an unshown pressure fluid supply source (compressor) and an unshown actuator operated by the pressurized pressure fluid.

As shown in Figures 1 and 3, the supercharging device 10 has a first driving cylinder 14 connected to one end side (A1 direction side) and the other end side (A2 direction side) of the supercharging cylinder 12, respectively. And a triple cylinder structure of the second drive cylinder 16. That is, in the supercharging device 10, from the A1 direction to the A2 direction, the first driving cylinder 14, the supercharging cylinder 12, and the second driving cylinder 16 are successively provided in this order.

A block-shaped first cover member 18 is provided between the first drive cylinder 14 and the pressurizing cylinder 12, and a block-shaped second cover member 20 is provided between the pressurization cylinder 12 and the second drive cylinder 16.

A booster chamber 22 is formed inside the booster cylinder 12, and a first drive chamber 24 and a second drive chamber 26 are formed inside the first drive cylinder 14 and the second drive cylinder 16, respectively. At this time, by fixing the third cover member 28 to the end of the first driving cylinder 14 in the A1 direction, and disposing the first cover member 18 at the end of the A2 direction, the first driving chamber 24 is formed. Furthermore, by arranging the second cover member 20 at the end of the second driving cylinder 16 in the A1 direction, and closing the end in the A2 direction with the wall 30, the second driving chamber 26 is formed.

As shown in FIG. 3, the piston rod 32 is arranged so as to penetrate the first cover member 18, the pressurizing cylinder 12 and the second cover member 20. One end of the piston rod 32 extends to the first drive chamber 24, and the other end of the piston rod 32 extends to the second drive chamber 26.

In the pressurizing chamber 22, a pressurizing piston 34 is connected to the center of the piston rod 32. Thereby, the pressurizing chamber 22 is divided into the first pressurizing chamber 22a on the A1 direction side and the second pressurizing chamber 22b on the A2 direction side (see FIG. 5). In the first drive chamber 24, a first drive piston 36 is connected to one end of the piston rod 32. Thereby, the first drive chamber 24 is divided into a pressure chamber 24a on the A1 direction side and a back pressure chamber 24b on the A2 direction side (refer to FIG. 5). In addition, in the second driving chamber 26, The second driving piston 38 is connected to the other end of the piston rod 32. Thereby, the second drive chamber 26 is divided into a pressure chamber 26a on the A2 direction side and a back pressure chamber 26b on the A1 direction side (refer to FIG. 5). The pressurizing piston 34, the first driving piston 36 and the second driving piston 38 are integrally connected by a piston rod 32.

As shown in FIG. 1, a supply port 40 for receiving pressure fluid from a pressure fluid supply source (not shown) is formed on the upper part of the front surface of the pressurizing cylinder 12. As shown in Figures 4 and 5, the pressurizing cylinder 12, the first cover member 18, and the second cover member 20 are provided with a supply port 40 communicating with each other to supply the supplied pressure fluid to the first The fluid supply mechanism of the pressurizing chamber 22a and the second pressurizing chamber 22b. The fluid supply mechanism has a first supply flow path 42a that communicates the supply port 40 and the first pressurizing chamber 22a, and a second supply flow path 42b that communicates the supply port 40 and the second pressurization chamber 22b.

The first supply flow path 42 a is provided with a first supply check valve 42 c that allows fluid to flow from the supply port 40 to the first pressurizing chamber 22 a and prevents the fluid from flowing from the first pressurized chamber 22 a to the supply port 40. The second supply flow path 42b is provided with a second supply check valve 42d that allows fluid to flow from the supply port 40 to the second pressurizing chamber 22b and prevents the fluid from flowing from the second pressurized chamber 22b to the supply port 40.

As shown in FIG. 1, an output port 44 for outputting fluid pressurized by a pressurizing operation described later to the outside is formed on the lower front surface of the pressurizing cylinder 12. As shown in Figures 4 and 5, the inside of the pressurizing cylinder 12, the first cover member 18, and the second cover member 20 are provided with an output port 44 that communicates with each other through the first pressurizing chamber 22a or the second A fluid output mechanism in which the pressurized fluid in the pressurizing chamber 22b is output from the output port 44. The fluid output mechanism has a first output flow path 46 a that communicates the first pressurizing chamber 22 a and the output port 44, and a second output flow path 46 b that communicates the second pressurization chamber 22 b and the output port 44.

The first output flow path 46a is provided with a first output check valve 46c that allows fluid to flow from the first pressurizing chamber 22a to the output port 44 and prevents the fluid from flowing from the output port 44 to the first pressurizing chamber 22a. The second output flow path 46b is provided with a second output check valve 46d that allows fluid to flow from the second pressurizing chamber 22b to the output port 44 and prevents the fluid from flowing from the output port 44 to the second pressurizing chamber 22b.

Next, the structure of the operating valve will be described. As shown in Figure 1, the upper part of the first driving cylinder 14 is provided with a first housing 50 having a first operating valve 48, and the upper part of the second driving cylinder 16 is provided with a first housing 50 having a second operating valve 52. Two shell 54.

As shown in Fig. 5, the first operating valve 48 has a first port 56A to a fifth port 56E as a connection and switching point of the flow path, and is configured to be able to drive the first driving piston 36 The position is switched between the second position and the second position for causing the first driving piston 36 to act in accordance with the driving of the second driving piston 38.

The first port 56A is connected to the pressurizing chamber 24a of the first driving cylinder 14 through a flow path 58a. The second port 56B is connected to the back pressure chamber 24b of the first driving cylinder 14 through a flow path 58b. The third port 56C is connected to the first supply flow path 42a through the flow path 58c. The fourth port 56D is connected to the first muffler 62 having a discharge port through the flow path 58d. The fifth port 56E is connected to the middle of the flow path 58a by the flow path 58e. A first fixed throttle valve 60 is inserted in the flow path 58d.

When the first action valve 48 is in the first position, the first port 56A is connected to the third port 56C, and the second port 56B is connected to the fourth port 56D. Thereby, the pressure flow system from the supply port 40 is supplied to the pressurizing chamber 24a through the flow path 58c and the flow path 58a, and the fluid in the back pressure chamber 24b passes through the flow path 58b and the flow path 58d and passes through the first fixed throttle valve. 60 and the first muffler 62 are discharged.

When the first action valve 48 is in the second position, the first port 56A is connected to the fourth port 56D, and the second port 56B is connected to the fifth port 56E. With this, the flow of the pressurized chamber 24a A part of the body is recovered to the back pressure chamber 24b through the flow path 58a, the flow path 58e, and the flow path 58b, and the rest is discharged through the first fixed throttle valve 60 and the first muffler 62 through the flow path 58d.

The first action valve 48 also has a pilot port 56F for introducing pilot pressure from a second pilot valve 74 described later. The first action valve 48 is at the first position when the pressure fluid (pilot pressure) is supplied to the guide port 56F, and is at the second position when the pressure fluid (pilot pressure) is not supplied to the guide port 56F.

The second action valve 52 has a first port 64A to a fifth port 64E as a connection and switching point of the flow path, and is configured to be capable of driving the second driving piston 38 at the first position and for making the second The driving piston 38 switches between the second positions in which it operates in accordance with the driving of the first driving piston 36.

The first port 64A is connected to the pressurizing chamber 26a of the second driving cylinder 16 through the flow path 66a. The second port 64B is connected to the back pressure chamber 26b of the second driving cylinder 16 through the flow path 66b. The third port 64C is connected to the second supply flow path 42b through the flow path 66c. The fourth port 64D is connected to the second muffler 70 having a discharge port through the flow path 66d. The fifth port 64E is connected to the middle of the flow path 66a by the flow path 66e. A second fixed throttle 68 is inserted in the flow path 66d.

When the second action valve 52 is in the first position, the first port 64A is connected to the third port 64C, and the second port 64B is connected to the fourth port 64D. Thereby, the pressure flow system from the supply port 40 is supplied to the pressurizing chamber 26a through the flow path 66c and the flow path 66a, and the fluid in the back pressure chamber 26b passes through the flow path 66b and the flow path 66d and passes through the second fixed throttle valve. 68 and the second muffler 70 are discharged.

When the second action valve 52 is in the second position, the first port 64A is connected to the fourth port 64D, and the second port 64B is connected to the fifth port 64E. Thereby, a part of the fluid in the pressurizing chamber 26a is recovered to the back pressure chamber 26b through the flow path 66a, the flow path 66e, and the flow path 66b, and the rest passes through the flow path 66d and passes through the second fixed throttle 68 and the second The muffler 70 is discharged.

The second operating valve 52 also has a pilot port 64F for introducing a pilot pressure from a first pilot valve 72 described later. The second action valve 52 is at the first position when the pressure fluid (pilot pressure) is supplied to the guide port 64F, and is at the second position when the pressure fluid (pilot pressure) is not supplied to the guide port 64F.

Next, the structure of the pilot valve will be explained. A first pilot valve 72 is provided inside the first cover member 18, and a second pilot valve 74 is provided inside the second cover member 20.

The first pilot valve 72 has a first port 76A to a fourth port 76D, and is configured to be at a first position for generating a pilot pressure for the second action valve 52 and a first position for eliminating the pilot pressure Switch between the two positions.

The first port 76A is connected to the guide port 64F of the second action valve 52 through the first guide flow path 78b. The second port (supply port) 76B is connected to the first supply flow path 42a through the flow path 78a. The third port 76C constitutes a discharge port. The fourth port (linking port) 76D is connected to the first port 80A of the second pilot valve 74 described later through the branch flow path 82c and the second guide flow path 82b described later. In addition, the branch flow path 78c reaching the fourth port 80D of the second pilot valve 74 described later is branched from the first guide flow path 78b.

When the first pilot valve 72 is in the first position, the first port 76A is connected to the second port 76B. Thereby, the pressure flow system from the supply port 40 is supplied to the guide port 64F of the second action valve 52 through the flow path 78a and the first guide flow path 78b, and passes through a branch branched from the first guide flow path 78b. The flow path 78c is branched and supplied to the fourth port 80D of the second pilot valve 74 described later.

When the first pilot valve 72 is in the second position, the first port 76A is connected to the third port 76C. Thereby, the pressure flow system supplied to the pilot port 64F of the second action valve 52 is discharged through the first pilot flow path 78b, and the pressure flow system supplied to the fourth port 80D of the second pilot valve 74 passes through The flow path 78c and the first guide flow path 78b are branched and discharged.

The second pilot valve 74 has a first port 80A to a fourth port 80D, and is configured to be at a first position for generating a pilot pressure for the first action valve 48 and a first position for eliminating the pilot pressure Switch between the two positions.

The first port 80A is connected to the guide port 56F of the first action valve 48 through the second guide flow path 82b. The second port (supply port) 80B is connected to the second supply flow path 42b through the flow path 82a. The third port 80C constitutes the exhaust port. The fourth port 80D (linking port) is connected to the first port 76A of the first pilot valve 72 through the branch flow path 78c and the first guide flow path 78b. In addition, the branch flow path 82c reaching the fourth port 76D of the first pilot valve 72 is branched from the second guide flow path 82b.

When the second pilot valve 74 is in the first position, the first port 80A is connected to the second port 80B. Thereby, the pressure flow system from the supply port 40 is supplied to the guide port 56F of the first action valve 48 through the flow path 82a and the second guide flow path 82b, and passes through the branch branched from the second guide flow path 82b. The flow path 82c is branched and supplied to the fourth port 76D of the first pilot valve 72.

When the second pilot valve 74 is in the second position, the first port 80A is connected to the third port 80C. Thereby, the pressure flow system supplied to the pilot port 56F of the first action valve 48 is discharged through the second pilot flow path 82b, and the pressure flow system supplied to the fourth port 76D of the first pilot valve 72 passes through The flow path 82c and the second guide flow path 82b are branched and discharged.

Here, referring to FIGS. 6 to 8, the specific structure of the first pilot valve 72 will be described. In addition, since the specific structure of the second pilot valve 74 is the same as that of the first pilot valve 72, its description is omitted.

The first pilot valve 72 includes a valve seat 86 received in the valve receiving hole 84 provided in the first cover member 18, a valve seat pressing member 88 and a control pin 90. The valve accommodating hole 84 is closed on the side of the pressurizing cylinder 12 and opened on the side of the first driving cylinder 14. The closed-side end of the valve housing hole 84 is a large-diameter hole 84a, and the fourth port 76D communicates with this large-diameter hole 84a.

The valve accommodating hole 84 has a small diameter hole portion 84b connected to the large diameter hole portion 84a and a medium diameter hole portion 84c connected to the opening side of the small diameter hole portion 84b. The first port 76A, the second port 76B, and the third port 76C communicate with the small-diameter hole portion 84 b of the valve receiving hole 84. Among these three ports, the second port 76B is located closest to the fourth port 76D, and the third port 76C is located farthest from the fourth port 76D.

The thin-walled cylindrical valve seat 86 and the thick-walled cylindrical valve seat holder 88 are fitted in the small-diameter hole portion 84 b of the valve housing hole 84. The valve seat pressing member 88 has one axial end facing the back pressure chamber 24 b of the first driving cylinder 14, and the other axial end surface abuts the valve seat 86. A fixing ring 92 that abuts against the valve seat holder 88 is fixed to the middle diameter hole portion 84 c of the valve housing hole 84. Thereby, the valve seat 86 and the valve seat pressing member 88 are axially positioned and fixed in the valve receiving hole 84. In addition, the valve seat 86 is locked in a step portion provided in the middle of the small-diameter hole portion 84b.

An annular groove 86a facing the first port 76A is provided on the outer periphery of the axial center portion of the valve seat 86, and the outer periphery of the axial end portion of the valve seat 86 on the side of the valve seat pressing member 88 is provided with a third The annular recess 86b facing the port 76C. The annular groove 86a of the valve seat 86 is connected to the inner peripheral side of the valve seat 86 through a first through hole 86c that penetrates the valve seat 86 in the radial direction, and the annular recess 86b of the valve seat 86 penetrates the valve seat 86 in the radial direction. The second through hole 86 d communicates with the inner peripheral side of the valve seat 86.

On the outer peripheral surface of the valve seat 86, a first seal 94a and a second seal 94b that abut against the small-diameter hole portion 84b of the valve housing hole 84 are respectively mounted via the groove. The first sealing member 94a is located between the valve seat 86 and the valve receiving hole 84 to prevent the first port 76A from communicating with the second port 76B, and the second sealing member 94b is located between the valve seat 86 and the valve receiving hole 84 The gap prevents the first port 76A from communicating with the third port 76C.

On the outer peripheral surface of the valve seat pressing member 88, the third seal 96a is installed in the groove to abut against the small-diameter hole 84b of the valve housing hole 84. On the inner peripheral surface of the valve seat pressing member 88, the groove A fourth seal 96b slidably connected to the control pin 90 is installed. With the third seal 96a and the fourth The sealing member 96b, the third port 76C and the back pressure chamber 24b of the first driving cylinder 14 are sealed.

The control pin 90 has a large-diameter shaft portion 90a, a middle-diameter shaft portion 90b, and a small-diameter shaft portion 90c. The large-diameter shaft portion 90 a is inserted into the small-diameter hole portion 84 b of the valve housing hole 84. The intermediate diameter shaft portion 90b is inserted into the inner side of the valve seat 86 with a part protruding from the valve seat 86, and the portion protruding from the valve seat 86 is radially separated from the small diameter hole portion of the valve housing hole 84 with a predetermined gap. 84b is relative. The small-diameter shaft portion 90c is inserted into the inner side of the valve seat pressing member 88.

In the large-diameter shaft portion 90a of the control pin 90, a first gasket 98a slidably connected to the small-diameter hole portion 84b of the valve receiving hole 84 is installed via the groove. The first gasket 98a is used to seal the second port 76B and the fourth port 76D. The middle diameter shaft portion 90b of the control pin 90 is provided with a second gasket 98b and a third gasket 98c which can be slidably connected to the inner peripheral surface of the valve seat 86 via a groove. On the outer periphery of the inner diameter shaft portion 90b of the control pin 90, an annular groove 90d is provided between the installation location of the second gasket 98b and the installation location of the third gasket 98c.

The control pin 90 is slidable at the position where the end of the large-diameter shaft portion 90a abuts against the bottom surface (closed end surface) of the valve housing hole 84, and the stepped surface 90e between the intermediate-diameter shaft portion 90b and the small-diameter shaft portion 90c abuts Between the positions of the end faces of the valve seat pressing member 88. When the control pin 90 abuts on the end surface of the valve seat holder 88, the small diameter shaft portion 90c of the control pin 90 protrudes from the back pressure chamber 24b of the first drive cylinder 14 (hereinafter referred to as "the protruding length of the control pin" ) Reached the maximum. The first driving piston 36 can abut against the end of the small-diameter shaft portion 90 c of the control pin 90 to press the control pin 90 toward the bottom surface of the valve housing hole 84.

Regardless of the protruding length of the control pin 90, the annular groove 90d of the control pin 90 communicates with the annular groove 86a via the first through hole 86c of the valve seat 86. In other words, the annular groove 90d of the control pin 90 is constantly connected to the first port 76A, regardless of the position of the control pin 90. again In addition, the second port 76B constantly communicates with the gap formed between the middle diameter shaft portion 90 b of the control pin 90 and the small diameter hole portion 84 b of the valve receiving hole 84.

When the protruding length of the control pin 90 is large, the second gasket 98b is in contact with the inner surface of the valve seat 86, and the third gasket 98c is separated from the inner surface of the valve seat 86 (see FIG. 6). Therefore, the first port 76A communicates with the first port through the gap between the control pin 90 of the annular groove 90d including the control pin 90 and the inner surface of the valve seat 86, the second through hole 86d of the valve seat 86, and the annular recess 86b. Sanbu 76C.

When the first driving piston 36 abuts on the control pin 90 so that the protruding length of the control pin 90 is slightly reduced from the above, either the second gasket 98b and the third gasket 98c abut against the inner surface of the valve seat 86 (Refer to Figure 7). Therefore, the first port 76A is not connected to any of the second port 76B and the third port 76C.

When the protruding length of the control pin 90 is small, the second gasket 98b is separated from the inner surface of the valve seat 86, and the third gasket 98c abuts against the inner surface of the valve seat 86 (see FIG. 8). Therefore, the first port 76A can pass through the gap between the control pin 90 of the annular groove 90d containing the control pin 90 and the inner surface of the valve seat 86, and the small diameter between the inner diameter shaft portion 90b of the control pin 90 and the valve receiving hole 84 The gap formed between the holes 84b communicates with the second port 76B.

When the pressure fluid is supplied to the fourth port 76D, the control pin 90 is pushed in the direction in which the protruding length increases. The reason is that the fluid pressure applied area (pressure area) of the fourth port 76D applied in the direction that increases the protruding length of the control pin 90 is larger than the second port 76D applied in the direction that reduces the protruding length of the control pin 90 The fluid pressure action area (pressure area) of the port 76B.

On the other hand, when the pressure fluid is not supplied to the fourth port 76D, the control pin 90 is pushed in the direction in which the protruding length decreases. The reason is that the protruding length of the control pin 90 due to the orientation The fluid pressure of the fourth port 76D applied in the increasing direction disappears, and the fluid pressure of the second port 76B applied in the direction that reduces the protruding length of the control pin 90 is maintained.

The supercharging device 10 according to the first embodiment of the present invention is basically configured as described above, and its operation and effects will be described next. As shown in FIG. 5, the first operating valve 48 is switched to the second position and the second operating valve 52 is switched to the first position, and the pressurizing piston 34 is located near the center of the pressurizing chamber 22 As the initial position. In addition, in the following description, in order to distinguish the control pin of the first pilot valve 72 from the control pin of the second pilot valve 74, the former is referred to as "control pin 90-1" and the latter is referred to as "control pin 90-2". ". Furthermore, in order to distinguish the valve accommodating hole of the first pilot valve 72 from the valve accommodating hole of the second pilot valve 74, the former is called "valve accommodating hole 84-1" and the latter is called "valve accommodating hole 84-2" ".

In this initial position, by supplying the pressure fluid from the pressure fluid supply source to the supply port 40, the pressure fluid flows into the first supply flow path 42a and the second supply flow path 42b. Then, it is introduced into the first pressurizing chamber 22a and the second pressurizing chamber 22b of the pressurizing cylinder 12 through the first supply check valve 42c and the second supply check valve 42d.

A part of the pressure fluid supplied from the supply port 40 is supplied to the pressurizing chamber 26a of the second driving cylinder 16 through the flow path 66c, the second operating valve 52 at the first position, and the flow path 66a. The second driving piston 38 is driven in the A1 direction by the pressure fluid supplied to this pressurizing chamber 26a. Thereby, the pressurizing piston 34 integrally connected with the second driving piston 38 slides, and the pressure fluid in the first pressurizing chamber 22a of the pressurizing cylinder 12 is pressurized. The pressurized pressure flow system is guided to the output port 44 through the first output flow path 46a and the first output check valve 46c to be output.

On the other hand, when the first driving piston 36 integrally connected with the second driving piston 38 slides, the volume of the pressurizing chamber 24a of the first driving cylinder 14 decreases. Because of the first action The valve 48 is in the second position, so a part of the pressure fluid in the pressurizing chamber 24a is recovered to the back pressure chamber 24b through the flow path 58a, the flow path 58e, and the flow path 58b, and the rest is discharged through the flow path 58d.

As described above, in the stroke of the pressurizing piston 34 moving a predetermined distance from the initial position toward the A1 direction, the first pilot valve 72 is located at the first position, and the pressure flow system from the supply port 40 passes through the first pilot valve 72. It is supplied to the fourth port 80D of the second pilot valve 74. On the other hand, the second pilot valve 74 is located at the second position, and pressure fluid is not supplied to the fourth port 76D of the first pilot valve 72. Therefore, the first pilot valve 72 is pushed in the direction in which the protruding length of the control pin 90-1 decreases, and the first pilot valve 72 is stably maintained in the first position. Furthermore, the second pilot valve 74 is pushed in the direction in which the protruding length of the control pin 90-2 increases, and the second pilot valve 74 is stably maintained in the second position.

Then, as shown in FIG. 9, the second driving piston 38 is in contact with the control pin 90-2 of the second pilot valve 74 near the end of the stroke at which the pressurizing piston 34 is displaced in the A1 direction. The control pin 90-2 is pushed by the second driving piston 38 and is displaced until the first port 80A and the second port 80B of the second pilot valve 74 communicate with each other. Then, the pressure flow system from the supply port 40 is supplied to the pilot port 56F of the first action valve 48 through the second pilot flow path 82b, and is supplied to the fourth port of the first pilot valve 72 through the branch flow path 82c. 76D. Thereby, the first action valve 48 is switched to the first position, and the first pilot valve 72 is switched to the second position.

When the first pilot valve 72 is switched to the second position, the pressure flow system supplied to the pilot port 64F of the second action valve 52 passes through the first pilot flow path 78b from the third port 76C of the first pilot valve 72 Is discharged. Thereby, the second action valve 52 is switched to the second position.

Next, when the first pilot valve 72 is switched to the second position, the pressure flow system supplied to the fourth port 80D of the second pilot valve 74 passes through the branch flow path 78c and the first pilot flow path 78b from the first The third port 76C of the pilot valve 72 is discharged. Therefore, in the second pilot valve 74, the fluid pressure acts in a direction that reduces the protruding length of the control pin 90-2. According to this, with the second drive The control pin 90-2, which is displaced by the push of the piston 38 to connect the first port 80A and the second port 80B of the second pilot valve 74, is more subjected to fluid pressure and held in contact with the valve receiving hole 84- The position of the bottom surface of 2. That is, the second pilot valve 74 is stably maintained in the first position. The state in which the second pilot valve 74 is held at the first position is maintained until the first driving piston 36 is driven in the A2 direction to displace the control pin 90-1 as described later.

Next, a part of the pressure fluid supplied from the supply port 40 is supplied to the pressurizing chamber 24a of the first driving cylinder 14 through the flow path 58c, the first operating valve 48 at the first position, and the flow path 58a. The first driving piston 36 is driven in the A2 direction by the pressure fluid supplied to this pressurizing chamber 24a. Thereby, the pressurizing piston 34 integrally connected with the first driving piston 36 slides, and the pressure fluid in the second pressurizing chamber 22b of the pressurizing cylinder 12 is pressurized. The pressurized pressure flow system is directed to the output port 44 through the second output flow path 46b and the second output check valve 46d to be output.

On the other hand, when the second driving piston 38 integrally connected with the first driving piston 36 slides, the volume of the pressurizing chamber 26a of the second driving cylinder 16 decreases. Since the second operating valve 52 is at the second position, a part of the pressure fluid in the pressurizing chamber 26a is recovered to the back pressure chamber 26b through the flow path 66a, the flow path 66e, and the flow path 66b, and the remaining part is passed through the flow path 66d discharge.

Then, in the vicinity of the stroke end point at which the pressurizing piston 34 is displaced in the A2 direction, the first driving piston 36 is in contact with the control pin 90-1 of the first pilot valve 72. The control pin 90-1 is pushed by the first driving piston 36 and displaced until the first port 76A and the second port 76B of the first pilot valve 72 communicate with each other. Then, the pressure flow system from the supply port 40 is supplied to the pilot port 64F of the second action valve 52 through the first pilot flow path 78b, and is supplied to the fourth port of the second pilot valve 74 through the branch flow path 78c. 80D. Thereby, the second action valve 52 is switched to the first position, and the second pilot valve 74 is switched to the second position.

When the second pilot valve 74 is switched to the second position, the pressure flow system supplied to the pilot port 56F of the first action valve 48 passes through the second pilot flow path 82b from the third port 80C of the second pilot valve 74 Is discharged. Thereby, the first action valve 48 is switched to the second position.

Furthermore, when the second pilot valve 74 is switched to the second position, the pressure flow system supplied to the fourth port 76D of the first pilot valve 72 passes through the branch flow path 82c and the second pilot flow path 82b from the first The third port 80C of the second pilot valve 74 is discharged. Therefore, in the first pilot valve 72, the fluid pressure acts in a direction that reduces the protruding length of the control pin 90-1. Accordingly, the control pin 90-1, which is displaced by the pushing of the first driving piston 36 to connect the first port 76A and the second port 76B of the first pilot valve 72, is more subjected to fluid pressure and held at Abutting on the bottom surface of the valve housing hole 84-1. That is, the first pilot valve 72 is stably maintained in the first position. The state in which the first pilot valve 72 is held at the first position is maintained until the second driving piston 38 is driven in the A1 direction again to displace the control pin 90-2. Hereinafter, the pressurizing piston 34 repeats the same reciprocating motion, and continuously outputs the pressurized fluid from the output port 44.

According to the pressurizing device 10 of this embodiment, the control pin 90-1 that is displaced to the first port 76A and the second port 76B of the first pilot valve 72 by the pushing of the first driving piston 36 can be Further, it is pushed in by a predetermined fluid pressure to a position where it abuts against the bottom surface of the valve housing hole 84-1, and is held at that position. Similarly, the control pin 90-2, which is displaced to the communication between the first port 80A and the second port 80B of the second pilot valve 74 by the pushing of the second driving piston 38, can be further pushed by a predetermined fluid pressure. It enters to a position where it abuts against the bottom surface of the valve housing hole 84-2, and is held at that position.

Furthermore, the first operating valve 48 is switched to the first position when the pilot pressure is supplied from the second pilot valve 74 which is switched in conjunction with the first pilot valve 72 to switch positions, and the pilot valve is not supplied from the second pilot valve 74. Switch to the second position when under pressure. Similarly, the second operating valve 52 is switched to the first position when the pilot pressure is supplied from the first pilot valve 72 which is linked with the second pilot valve 74 to switch positions. When the pilot pressure is not supplied from the first pilot valve 72, it is switched to the second position. Therefore, the first operating valve 48 and the second operating valve 52 can operate stably and simultaneously switch.

Furthermore, since part of the fluid supplied to the pressurizing chamber 24a when the first driving piston 36 is driven, the back pressure is recovered when the first driving piston 36 follows the driving of the second driving piston 38. The chamber 24b can reduce the consumption of pressure fluid. Similarly, since part of the fluid supplied to the pressurizing chamber 26a when the second driving piston 38 is driven, the back pressure is recovered when the second driving piston 38 follows the driving of the first driving piston 36. The chamber 26b can reduce the consumption of pressure fluid.

The supercharging device of the present invention is not limited to the above-mentioned embodiment, and of course various configurations can be adopted within the scope not departing from the gist of the present invention.

10‧‧‧Boosting device

12‧‧‧Pressurized cylinder

14‧‧‧The first drive cylinder

16‧‧‧Second drive cylinder

22‧‧‧Pressure chamber

22a‧‧‧First pressurization chamber

22b‧‧‧Second plenum

24‧‧‧First Drive Room

26‧‧‧Second Drive Room

24a、26a‧‧‧Pressure chamber

24b, 26b‧‧‧Back pressure chamber

32‧‧‧Piston rod

34‧‧‧Piston for pressurization

36‧‧‧Piston for the first drive

38‧‧‧Second drive piston

40‧‧‧Supply Port

42a‧‧‧First supply flow path

42b‧‧‧Second supply flow path

42c‧‧‧First supply check valve

42d‧‧‧Second supply check valve

44‧‧‧Output port

46a‧‧‧First output channel

46b‧‧‧Second output channel

46c‧‧‧First output check valve

46d‧‧‧Second output check valve

48‧‧‧First action valve

52‧‧‧Second action valve

56F‧‧‧ Pilot port

58a to 58e‧‧‧Flow path

60‧‧‧The first fixed throttle

62‧‧‧First silencer

56A, 64A‧‧‧First port

56B, 64B‧‧‧Second port

56C, 64C‧‧‧third port

56D, 64D‧‧‧4th port

56E, 64E‧‧‧Port 5

64F‧‧‧ Pilot port

66a to 66e‧‧‧flow path

68‧‧‧Second fixed throttle

70‧‧‧Second silencer

72‧‧‧First pilot valve

74‧‧‧Second pilot valve

76A, 80A‧‧‧First port

76B, 80B‧‧‧Second port (supply port)

76C, 80C‧‧‧third port

76D, 80D‧‧‧Fourth port (connecting port)

78a‧‧‧Flow Path

78b‧‧‧First guide flow path

78c‧‧‧Branch flow path

82a‧‧‧Flow Path

82b‧‧‧Second guide flow path

82c‧‧‧Branch flow path

90‧‧‧Control pin

A1, A2‧‧‧direction

Claims (5)

A supercharging device is provided with first and second driving cylinders (14, 16) on both sides of a supercharging cylinder (12), and the supercharging device is provided with: first and second pilot valves (72, 74), each is equipped with the control that the first driving piston (36) of the first driving cylinder and the second driving piston (38) of the second driving cylinder are in contact with their moving ends Pin (90); and first and second action valves (48, 52), which switch the pressure fluid from the pressure fluid supply source to the pressure chamber (24a) of the first drive cylinder and the second drive cylinder The supply state of the pressurizing chamber (26a); when the first driving piston presses the control pin so that the first pilot valve corresponding to the pressed control pin is switched to the first position, switch to the aforementioned Pressure fluid is supplied to the state of the first and second action valves, and a predetermined fluid pressure acts on the control pin to keep the first pilot valve at the first position. As for the pressure boosting device described in claim 1, wherein the second action valve switches its position according to the presence or absence of the pilot pressure supplied from the first pilot valve, and the first action valve is based on The position of the pilot pressure supplied by the aforementioned second pilot valve is switched. As described in the first item of the scope of patent application, the first pilot valve has: a supply port that constantly receives the supply of the pressure fluid; and a linkage port that passes through the second guide The valve receives the supply of the aforementioned pressure fluid; the aforementioned second pilot valve has: a supply port that constantly receives the supply of the aforementioned pressure fluid; and a linkage port that receives the supply of the aforementioned pressure fluid through the aforementioned first pilot valve; The control pin of the first or second pilot valve is oriented so that the pilot valve becomes the second position when the pressure fluid is supplied to the interlocking port. When pressing, when the pressure fluid is not supplied to the interlocking port, the predetermined fluid pressure acts. The pressure boosting device described in item 3 of the scope of patent application, wherein when the first pilot valve is in the first position, the pilot pressure is supplied to the second action valve, and the pilot pressure is applied to the second pilot valve. The interlocking port supplies the pressure fluid, and when the second pilot valve is in the first position, the first action valve is supplied with the pilot pressure, and the interlocking port of the first pilot valve is supplied with the pressure fluid. The pressurizing device described in claim 1, wherein the first action valve is switched to: supply the pressure fluid to the pressurization chamber of the first drive cylinder, and switch the first drive cylinder The state in which the pressure fluid in the back pressure chamber (24b) is discharged; and the state in which part of the pressure fluid in the pressurizing chamber of the first drive cylinder is recovered to the back pressure chamber of the first drive cylinder; the second action valve It is switched to a state where the pressure fluid is supplied to the pressurization chamber of the second drive cylinder and the pressure fluid in the back pressure chamber (26b) of the second drive cylinder is discharged; and the second drive cylinder is discharged A part of the pressure fluid in the pressure chamber is recovered in the state of the back pressure chamber of the second driving cylinder.

Images