JPH11117905A - Power generating machine for hydraulic system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power generating machine for a hydraulic system with miniaturized and reduced weight construction and improved durability. SOLUTION: A hydraulic pump 3 and an air cylinder 2 are arranged in series, a piston 4 is inserted into the cylinder head part 7 of the air cylinder 2, and at the cylinder head part 7, a piston control mechanism P for supplying and exhausting compressed air to and from a chamber 6 is provided. A cylindrical hole 33 is opened in the hydraulic pump 3 side wall face of the air cylinder 2, and the portion on the hydraulic pump 3 side of the cylindrical hole 33 is used as a pressurizing chamber 34 for oil pressure. The front end part of the piston rod 5 is held in the cylindrical hole 33, a ring-like damper 31 is arranged at the opening-edge part of the cylindrical hole 33, and the portion adjacent to the piston rod 5 of the damper 31 is projected. The inclined surface of the outer periphery of a projected part 31a of the damper 31 is smoothly curved into an S-shape, and a ring-like washer 35 which is curved along the curve of the inclined surface, is allowed to abut on the inclined surface. A coil spring 36 is arranged between the washer 35 and the piston 4, and the piston 4 is energized by the coil spring 36 in the direction in which the piston departs from the hydraulic pump 3.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power generator for a hydraulic device which converts air pressure of compressed air into hydraulic pressure and supplies driving power to a hydraulic processing machine or the like.

[0002]

2. Description of the Related Art Conventionally, a pneumatic oil converter has a part for controlling reciprocation of a pneumatic part for increasing hydraulic pressure and a compression drive part for actually generating hydraulic pressure, which are arranged in parallel or in series. What is installed by arrangement is known.

[0003] As a power generator for a hydraulic device, there is a portable power processing machine disclosed in Japanese Patent Application Laid-Open No. Hei 7-285015.

This "portable hydraulic working machine" is intended to reduce the size and weight of a housing. First and second chambers are defined before and after a piston head in a cylinder. , A reservoir serving as an oil reservoir is communicated with the second chamber. When the oil pressurized by the motor and the pump in the main body including the cylinder is supplied from the reservoir to the first chamber behind the piston head, the first
When the piston moves forward due to the supply of pressurized oil to the chamber, a pair of processing jigs opposing the housing at the tip of the piston operate, and desired machining is performed.

In the portable hydraulic processing machine described in this publication, a reservoir is provided at a position adjacent to a cylinder in a pump case forming a part of a main body. A flexible airbag for preventing generation of a negative pressure under inflation is provided in the reservoir in communication with the internal atmosphere.

In Japanese Patent Laid-Open No. 7-285015, oil is supplied to one chamber of a cylinder defined by a piston, and a return spring is provided in the other chamber.
The return spring is compressed by moving the piston by the force of the compressed air. When the return spring is sufficiently compressed, the oil is discharged, and the elastic force of the return spring returns the piston to its original position. The return spring has a coil shape and is provided around the piston rod.

[0007]

However, when the reciprocating control part of the pneumatic part and the compression drive part are arranged in parallel or in series as in the prior art, the size becomes large, and when applied to a hand-held hydraulic tool. This has been an alienation factor in reducing the size and weight. In addition, in the “portable hydraulic working machine” disclosed in Japanese Patent Application Laid-Open No. 7-285015, the capacity of the reservoir increases when the driving force is increased. Therefore, there is a limit in reducing the size and weight when applied to a handheld hydraulic tool.

Further, in Japanese Patent Application Laid-Open No. 7-285015,
The part supporting the return spring for driving the piston with oil is not shown. However, when the piston is reciprocated by the compressed air and the coil spring, the piston moves fast, so it is necessary to provide a damper for supporting the piston moving by the compressed air. Is provided,
When the piston collides with the cylindrical damper and the damper expands, the durability of the damper may be reduced due to the damper being sandwiched between the winding portions of the coil spring.

The present invention has been made in view of such a problem. When supplying hydraulic pressure to a hand-held hydraulic tool, it is possible to reduce the size and weight of the hydraulic tool and to use a compressed air for a hydraulic pump. An object of the present invention is to stabilize the elastic force of a coil spring for reciprocating a piston when operating, and to improve the durability of a damper supporting the coil spring.

[0010]

According to a first aspect of the present invention, there is provided a power generator for a hydraulic device, comprising: a hydraulic pump and an air cylinder which are connected to a cylinder rod of a piston in an air cylinder. The cylinder is arranged in series along the axial direction, a cylinder head is provided at a portion of the air cylinder opposite to the hydraulic pump, the piston rod is inserted into the cylinder head, and the hydraulic pump of the cylinder head is provided. A piston control mechanism for supplying / exhausting compressed air to / from a chamber between the piston and the cylinder head portion at a position opposite to the front side, and extends in the axial direction of the cylinder rod on a side wall surface of the hydraulic pump of the air cylinder. A cylindrical hole is opened, and a portion of the cylindrical hole on the hydraulic pump side is used as a hydraulic pressure suction / discharge portion of the hydraulic pump. Wherein the front end of the cylinder rod slidably is held, the opening edge portion in said air cylinder of the cylinder bore, arranged capable of supporting an annular damper the piston as well as through the cylinder rod within,
A portion near the piston rod of the damper is protruded in the axial direction of the piston rod, and an inclined surface of the projected portion of the damper near the inner peripheral wall of the air cylinder is smoothly curved into an S-shape. A washer that is curved along the curve of the inclined surface and is formed in a ring shape is abutted, and a coil spring is disposed between the washer and the piston, and the piston is moved from the hydraulic pump by the coil spring. It is characterized in that it is urged in a direction to separate.

According to the power generator for a hydraulic device of the present invention,
The portion near the piston rod of the damper protrudes, and furthermore, the slope of the protrusion of the damper smoothly curves in an S-shape,
A washer is provided on this curved part, and the coil spring is supported on this washer. Even if the coil spring is compressed by approaching the damper side of the piston, the damper is sandwiched by the coil spring winding part. Is prevented. For this reason, the durability of the damper is improved. Further, since the washer is curved along the curve of the damper, displacement of the washer and the coil spring is prevented, and unstable elastic force of the spring is prevented.

[0012]

Next, a power generator for a hydraulic device according to a preferred embodiment of the present invention will be described with reference to the drawings.

FIG. 1 schematically shows the configuration of a power generator for a hydraulic device according to one embodiment of the present invention. The main configuration of the hydraulic power generator 1 will be briefly described. The hydraulic power generator 1 includes an air cylinder 2 and a hydraulic pump 3 arranged in series, and a piston rod 5 of a piston 4 in the air cylinder 2. Is held in a pressurizing chamber 34, which is a hydraulic path of the hydraulic pump 3, and the piston 4 reciprocates to suck and discharge oil from the hydraulic pump 3 to the hydraulic cylinder.

At a position on the opposite side of the hydraulic pump 3 of the air cylinder 2, there is provided a cylinder head portion 7 which forms a compressed air chamber 6 in cooperation with the piston 4 and the air cylinder 2. A piston control mechanism P is provided at a portion of the cylinder head 7 opposite to the piston 4.
The piston control mechanism P is disposed inside a storage room R partitioned by the storage housing 52. The cylinder head 7 includes an inner housing 8 that projects in a cylindrical shape around the piston rod 5, and a cylindrical middle housing 9 that is located outside the inner housing 8.
It is composed of

The piston control mechanism P includes an inner housing 8, a middle housing 9, and an inner housing 8.
A cylindrical space portion 10 between the inner housing 8 and the middle housing 9, a cylindrical intake / exhaust control valve 11 for intake / exhaust of compressed air into / from the chamber 6, and cylindrical concave portions 73, 74 inside the inner housing 8. And a cylindrical reciprocating control valve 12 slidably held at the other end of the piston rod 5 protruding from the bottom of the cylindrical concave portion 73.

The intake / exhaust control valve 11 is connected to the air cylinder 2
When the air is slid to the first switching position 13, the compressed air is introduced into the chamber 6 while the intake / exhaust control valve 11
Slides to the second switching position 14 retreated from the air cylinder 2 to exhaust the compressed air in the chamber 6 to the storage room R.

When the piston 4 is located at the most compressed position of the chamber 6, the reciprocation control valve 12 moves the intake / exhaust control valve 11 to the first switching position 13, and moves the piston 4 to the most expanded position of the chamber 6. Immediately before the position, the intake / exhaust control valve 11 is positioned at the second switching position 14.

The reciprocating control valve 12, the inner housing 8, the intake / exhaust control valve 11, the middle housing 9, and the air cylinder 2 are arranged concentrically around the piston rod 5.

In the power generator 1 for a hydraulic device, when the intake / exhaust control valve 11 is positioned at the first switching position 13 in a state where the compressed air is supplied to the peripheral surface of the middle housing 9, the compressed air is generated. The piston 4 is introduced into the chamber 6 of the cylinder 2 and moves toward the hydraulic pump 3 against the urging force.

Immediately before the piston 4 is positioned at the minimum position of the chamber 6, the reciprocating control valve 12 held at the rear end of the piston rod 5 causes the intake / exhaust control valve 1 to move.
1 moves to the second switching position 14 side, the state where the compressed air is supplied to the middle housing 9 is cut off, and the compressed air in the chamber 6 is exhausted.

The compressed air in the chamber 6 is exhausted, and the piston 4 returns to the cylinder head 7 by the urging force. When the piston 4 moves to the cylinder head 7 side and is located at the maximum position of the chamber 6, the reciprocation control valve 1
2 moves the intake / exhaust control valve 11 to the first switching position 13 side, and again through the middle housing 9 to the chamber 6.
Compressed air is introduced into the inside. When the supply of the compressed air to the middle housing 9 can be cut off, the reciprocating operation of the piston 4 stops.

As described above, the reciprocating control valve 12, the inner housing 8, the intake / exhaust control valve 11, and the middle housing 9 for controlling the reciprocating operation of the piston 4 are formed concentrically around the piston rod 5. The size and weight of the piston 4 are promoted, and the vibration of the intake / exhaust control valve 11 and the reciprocation control valve 12 is reduced when the piston 4 reciprocates.

Next, each part of the power generator 1 for a hydraulic device will be described in detail.

The power generator 1 for a hydraulic device includes a handle 1
A connection port 17 to which an air hose of compressed air is connected is provided at the bottom 16 of 5. A supply path 19 for guiding compressed air introduced from the connection port 17 to a supply chamber 27 formed on the outer peripheral side of the air cylinder 2 and a used air from the air cylinder 2 and the like are provided at a front portion 18 of the handle portion 15. And an exhaust path 20 for exhausting air.

A trigger 23 for sliding a main valve 22 for supplying / stopping compressed air into the middle housing 9 along the piston rod 5 is provided at a rear portion 21 of the handle portion 15. .

An arrangement space 2 in which the main valve 22 is arranged
4 has an air passage 26 leading to a valve (not shown) operated by the trigger 23 through the upper portion 25 of the handle portion 15.
The arrangement space 24 is selectively connected to a compressed air supply source and an exhaust port by the valve.

When the trigger 23 is not pulled, compressed air from a compressed air source is supplied into the arrangement space 24 via the valve, and this compressed air acts on the upper end surface of the main valve 22 to cause the main valve 22 to move. 22 is pressed forward to shut off the space between the supply chamber 27 and the middle housing 9, thereby shutting off the supply of compressed air into the middle housing 9.

When the trigger 23 is pulled, the valve is switched against the urging force of the spring, and the arrangement space 24 is connected to the exhaust port through the air passage 26. As a result, the compressed air at the upper end face of the main valve 22 in the arrangement space 24 is exhausted, and the main valve 22 is moved rearward by the pressure of the compressed air in the supply chamber 27 acting on the lower end face, so that the compressed air is removed. The power is supplied into the middle housing 9 to operate the power generator 1 for a hydraulic device.

Further, when the retraction of the trigger 23 is stopped and the trigger 23 is returned to its original position, the arrangement space 2 is opened via the air passage 26 by a valve.
4 acts on the upper end of the main valve 22, moves the main valve 22 forward, closes the space between the supply chamber 27 and the middle housing 9, and cuts off the supply of compressed air. The operation of the power generator 1 is stopped.

The exhaust path 20 communicates with the storage chamber R, and the exhaust of the chamber 6 exhausted to the storage chamber R and the compressed air exhaust that reciprocally slides the intake / exhaust control valve 11 pass through the exhaust path 20. Exhausted. The exhaust path 20 is the handle 1
5, a rectifying filter F for rectifying the exhaust of the compressed air passing through the exhaust path 20 is provided near the bottom of the exhaust path 20. The rectification filter F has a fin F1 extending in parallel to the flow direction of the airflow in the exhaust path 20, and a handle portion 15 is provided below the rectification filter F.
An exhaust port A for exhausting the compressed air is opened outside the. A trigger 2 is provided upstream of the rectifying filter F in the exhaust path 20.
The exhaust path 26 on the third side merges into one, and the exhaust from the exhaust path 26 and the exhaust from the exhaust path 20 are merged, pass through the rectifying filter F, and are exhausted from the exhaust port A. I have. As a result, the exhaust gas from the exhaust path 20 and the exhaust gas from the exhaust path 26 are both rectified, and the exhaust noise is attenuated.

A trigger 23 for sliding a main valve 22 for supplying and stopping compressed air into the middle housing 9 along the piston rod 5 is provided at a rear portion 21 of the handle portion 15. .

The arrangement space 2 in which the main valve 22 is arranged
4 has an air passage 26 leading to a valve (not shown) operated by the trigger 23 through the upper portion 25 of the handle portion 15.
The arrangement space 24 is selectively connected to a compressed air supply source and an exhaust port by the valve.

When the trigger 23 is not pulled, compressed air from a compressed air source is supplied into the arrangement space 24 through the valve, and this compressed air acts on the upper end surface of the main valve 22 to cause the main valve 22 to move. 22 is pressed forward to shut off the space between the supply chamber 27 and the middle housing 9, thereby shutting off the supply of compressed air into the middle housing 9.

When the trigger 23 is pulled, the valve is switched against the urging force of the spring, and the arrangement space 24 is connected to the exhaust port through the air passage 26. As a result, the compressed air at the upper end face of the main valve 22 in the arrangement space 24 is exhausted, and the main valve 22 is moved rearward by the pressure of the compressed air in the supply chamber 27 acting on the lower end face, so that the compressed air is removed. The power is supplied into the middle housing 9 to operate the power generator 1 for a hydraulic device.

Further, when the retraction of the trigger 23 is stopped and the trigger 23 is returned to its original position, the arrangement space 2 is opened via the air passage 26 by the valve.
4 acts on the upper end of the main valve 22, moves the main valve 22 forward, closes the space between the supply chamber 27 and the middle housing 9, and cuts off the supply of compressed air. The operation of the power generator 1 is stopped.

Air cylinder 2 in front of handle 15
, The piston 4 fixed to the piston rod 5 is slidably held. The outer circumference of the air cylinder 2 is covered by an outer housing 28 forming a supply chamber 27 for compressed air. Outer housing 28
Is formed in a cylindrical shape, and the air supply passage 19 of the handle portion 15 is formed.
Is connected to

Inside the outer housing 28, a cylindrical main valve 22 for controlling the compressed air in the supply chamber 27 is slidably disposed. The main valve 22 cuts off and communicates between the supply chamber 27 and the outer peripheral surface of the middle housing 9 when the lower end surface contacts and separates from the upper end surface of the air cylinder 2. In other words, the drive compressed air in the supply chamber 27 is supplied or stopped to the hydraulic power generator 1 to start and stop the hydraulic power generator 1. The main valve 22 performs pneumatic control on the outer peripheral surface of the middle housing 9 while slidingly contacting the outer periphery of the middle housing 9. The inner housing 8 and the middle housing 9 provided inside the middle housing 9 constitute a cylinder head 7 of the air cylinder 2.

A hydraulic pump 3 having a hydraulic cylinder is fixed to a front end, which is one end of the air cylinder 2. A circular recess 30 having the same diameter as the inside diameter of the air cylinder 2 is formed in a portion facing the inside of the air cylinder 2 of the hydraulic pump 3, and a bumper 31 is fixed to the inner periphery and the bottom of the circular recess 30. Have been. At the center of the bottom of the circular concave portion 30, a cylindrical hole 33 in which the front end portion 32 of the piston rod 5 is slidably held is formed. The cylindrical hole 33 forms a hydraulic path of the hydraulic pump 3. The front end 32 of the piston rod 5 and the cylindrical hole 33 are sealed so that the pressurizing chamber 34 in front of the front end 32 of the piston rod 5 is kept watertight.

The bumper 31 is made of, for example, a plastic elastomer such as oil-resistant butyl rubber or the like, is formed in a ring shape, and has a central portion bulging toward the piston 4. The central portion of the bumper 31 and the vicinity of the portion through which the piston rod 5 passes is protruded toward the piston 4, and the outer peripheral portion of the protruding portion 31a of the bumper 31 is smoothly curved in an S shape. . The S-shaped inclined surface extends at a right angle toward the inner peripheral wall surface of the air cylinder 4 and is fitted into the inner peripheral wall surface of the air cylinder 4 of the bumper 31.

A ring-shaped washer 35 is provided on the outer periphery of the bumper 31 on the piston 4 side. Washer 35
The central portion on the side of the piston rod 5 is curved in an S shape along the shape of the peripheral surface of the bumper 31. The inside of the washer 35 protrudes toward the piston 4 to reinforce the side surface of the protruding portion of the bumper 31 and to resiliently urge the piston 4 and the washer 35 in the separating direction.
I support. The bumper 31 buffers and stops the piston 4 driven by the compressed air in the chamber 6 at its reciprocating end.

The bumper 31 has a central portion protruding and an outer peripheral portion S
The washer 35 comes into surface contact with the inclined surface, and the coil spring 36 is supported on the washer 35. Therefore, even if the coil spring 36 is compressed, the winding of the coil spring 36 is performed. Bumper 3 at the turn
1 is prevented from being pinched, the coil spring 36 is stably held, and the washer 35 and the coil spring 36 are prevented from being displaced in the direction perpendicular to the piston rod 5. Since the displacement of the washer 35 and the coil spring 36 is prevented and stabilized,
The speed of the reciprocating slide of the piston 4 can be increased.

As shown in FIG. 8, a seal ring 37 is fitted on the peripheral surface of the piston 4. The seal ring 3 seals the air cylinder 2 and the peripheral surface of the piston 4. The piston 4 is supported by a fixed flange 38 provided on the piston rod 5. Between the surface of the piston 4 facing the bumper 31 and the surface on the opposite side of the bumper 31,
Vent 3 for inserting piston 4 into air cylinder 2
9 is open. A piston damper 40 is attached to a surface of the piston 4 opposite to the bumper 31.
The piston damper 40 seals the vent 39 when the chamber 6 is filled with air, and reduces the collision of the piston 4 with the inner housing 8. On the inner housing 8 side of the piston damper 40, a ring-shaped bead 41 (see FIG. 8) is formed to protrude. In this embodiment, the piston damper 40 as the first damper is provided on the piston 4 side, but the first damper may be provided on the cylinder head 7 side.

A chamber 6 is formed between the piston 4 and the cylinder head 7 so as to expand and contract due to intake and exhaust of compressed air. A port 42 opened to the inner housing 8 faces the chamber 6. This port 4
Reference numeral 2 denotes a lower portion of the inner housing 8, which extends from a surface facing the chamber 6 to a front outer peripheral surface of the cylindrical space 10, and is opened and closed by an intake / exhaust control valve 11. As shown in FIG. 1, when the main valve 22 is open and the intake / exhaust control valve 11 is located at the first switching position 13, the port 42 is connected to the port 43 b of the middle housing 9 and the port of the intake / exhaust control valve 11. In communication with 69, the compressed air of the supply chamber 27 is introduced into the chamber 6.

Incidentally, as shown in FIG.
When the intake / exhaust control valve 11 is located at the second switching position 14 far from the hydraulic pump 3, the compressed air in the chamber 6 is communicated with the gap 58 between the middle housing 9 and the inner housing 8 so that the compressed air in the chamber 6 is exhausted. Exhaust. That is, as shown in FIG. 5, before the chamber 6 reaches the maximum position where the chamber 6 expands most, the port 42 is exhausted, and the piston 4 is pushed toward the cylinder head 7 by the urging force of the coil spring 36. By doing so, port 42,
The compressed air in the chamber 6 is exhausted through the gap 58.

A supply chamber 27 for supplying compressed air to the chamber 6 and the air reservoir 59 is formed on the outer periphery of the air cylinder 2. As shown in FIG. 2, the supply chamber 27 includes an air cylinder 2 and an outer housing 2.
8, a cylindrical grip adapter 45, and seal rings 46, 4 fixed to front and rear ends of the grip adapter 45.
7 is formed. A compressed air supply passage 19 extending from the handle portion 15 is provided at a lower portion of the outer housing 28.
Communicates. The grip adapter 45 has an opening 48 through which the supply path 19 and the supply chamber 27 pass.

The seal ring 46 located on the front end side of the outer housing 28 is provided with a flange 49 of the hydraulic pump 3.
It is held and fixed. The seal ring 46 seals the outer peripheral surface of the air cylinder 2 and the inner peripheral surface of the outer housing 28 so as to maintain airtightness.

The seal ring 47 located at the rear end of the outer housing 28 is supported by a flange 50 projecting from the inner wall surface of the rear end of the outer housing 28. The front end of the above-mentioned main valve 22 is slidably in contact with the inside of the seal ring 47. The seal ring 47 seals so as to maintain airtightness between the inner peripheral surface of the outer housing 28 and the front end of the main valve 22.

The space 51 in which the main valve 22 is disposed has a cylindrical storage housing 5 forming a front portion of the handle portion 15.
2, a stepped portion 53 at the rear of the middle housing 9, a rear end of the outer housing 28, and a seal ring 47. The space between the stepped portion 53 of the middle housing 9 and the storage housing 52 is sealed so that airtightness can be maintained.

The main valve 22 is formed in an annular shape having a substantially “L” -shaped cross section.
It is slidably disposed in an arrangement space 51 formed between the storage housing 52 and the middle housing 9, and the thin lower end surface faces the supply chamber 27 facing the upper end surface of the air cylinder 2. . The storage housing 52
The compressed air is supplied to the arrangement space 51 where the rear end face of the thick portion 54 of the main valve 22 faces through the air passage 26, or from the arrangement space 51. The compressed air is exhausted.

When the compressed air is supplied into the arrangement space 51 via the air passage 26, the main valve 22
The compressed air acting on the rear end face of the thick portion 54 of the main valve 22 is biased forward and the lower end face is pressed against the upper end face of the air cylinder 2 to block the supply chamber 27 from the middle housing 9. When the compressed air in the arrangement space 51 is exhausted through the air passage 26, the biasing force of the compressed air acting on the rear end of the thick portion 54 is eliminated, and the supply chamber acting on the lower end of the thin portion is removed. 2
7 is deflected rearward by the action of the compressed air inside, and the lower end surface is separated from the upper end surface of the air cylinder 2 so that the supply chamber 27
And the middle housing 9.

The front end of the middle housing 9 forms a cylinder head 7 together with the inner housing 8, and is airtightly fitted inside the rear end of the air cylinder 2. As shown in FIG. 3, a seal ring 55 is provided on the outer periphery of the front end of the middle housing 9, and the seal ring 55 seals the front end of the middle housing 9 and the rear end of the air cylinder 2. . A seal ring 56 is provided on the inner periphery of the front end of the middle housing 9, and the seal ring 56 seals between the front end of the inner housing 8 and the middle housing 9. The ports 43a and 43b described above are opened in upper and lower portions of the middle housing 9 on the side of the air cylinder 2. The ports 43a and 43b may be arranged in a broken line shape over the entire outer peripheral surface of the cylindrical inner housing 8.

Between the middle housing 9 and the inner housing 8, a cylindrical space 10 in which the intake / exhaust control valve 11 is provided is formed. As shown in FIGS. 2 to 7, a rear outer peripheral wall 57 of the cylindrical space portion 10 is formed on the inner housing 9 side. A gap 58 is provided between the rear outer peripheral wall 57 and the rear of the middle housing 9. When the intake / exhaust control valve 11 is located at the second switching position 14, the gap 58 exhausts the compressed air in the chamber 6 through the port 42 and the port 69 of the intake / exhaust control valve 11. The gap 58 is formed so as to surround the intake / exhaust control valve 11.

At the rear of the cylindrical space 10, air is stored between the rear end of the intake / exhaust control valve 11 and air for moving the intake / exhaust control valve 11 forward to the first switching position 13. A reservoir 59 (see FIGS. 3 and 4) is provided. In the air reservoir 59, a gap 61 for passing air into the air reservoir 59 is provided between the inner peripheral surface of the rear end portion of the intake / exhaust control valve 11 and the cylindrical arrangement chamber 57.

A port 62 is opened from the front upper portion of the inner housing 8 to the middle portion of the inner wall, and a cylindrical concave portion 73 formed inside the inner housing 8 is formed.
It communicates with 74. As shown in FIG.
Seal rings 75, 76 provided on inner wall surfaces
Is away from the outer peripheral surface of the reciprocation control valve 12,
The compressed air entering from the port 62 passes through the gap 63 between the sliding contact surface with the reciprocation control valve 12, and further, the port 64 opened at the rear of the intake / exhaust control valve 11, the gap 61
And enters the air reservoir 59.

That is, as shown in FIG. 2, when the intake / exhaust control valve 11 is at the second switching position 14 separated from the air cylinder 2, the port 62 of the inner housing 8 is
The gap 63 between the reciprocation control valve 12 and the port 64 at the rear of the inner housing 8 communicate with each other. Accordingly, compressed air is introduced into the air reservoir 59 through the gap 61, and the intake / exhaust control valve 11 moves from the second switching position 14 to the first switching position 13.

As shown in FIG. 4, the intake / exhaust control valve 11 has a seal 65 on the inner wall on the air cylinder 2 side and a seal ring 66 on the outer wall on the air cylinder 2 side. A recess 67 is formed on the inner wall of the intake / exhaust control valve 11 behind the seal ring 65, and a recess 68 is formed on the outer wall of the intake / exhaust control valve 11 behind the seal ring 66. I have. The recesses 67 and 68 are connected by a port 69. The concave portion 68 is formed on the entire circumference of the intake / exhaust control valve 11, and the port 69 is intermittently surrounded on the entire circumference. A seal ring 70 is provided at the center of the outer wall of the intake / exhaust control valve 11, and a concave portion 71 covering the entire circumference is formed on the outer wall behind the seal ring 70. A seal ring 72 is provided on a rear end outer wall of the intake / exhaust control valve 11.

When the intake / exhaust control valve 11 is in the second switching position 14, the seal rings 65 and 66 are connected to the port 42 of the inner housing 8 and the port 4 of the middle housing 9.
3a and 43b are shut off. Seal rings 66, 7
When the intake / exhaust control valve 11 is at the first switching position 13, the port 0 communicates with the ports 42, 43 b, and 69 to seal the compressed air to be sent to the chamber 6. When the intake / exhaust control valve 11 is at the second switching position 14, the seal rings 66, 70 are provided with the ports 42, 69, the recess 68, and the gap 5.
Seal so that 8 communicates. The seal ring 72 seals when air is stored in the air reservoir 59.
A seal ring 8 a provided at the center of the outer periphery of the inner housing 8 seals a space before and after the intake / exhaust control valve 11.

As shown in FIG.
As shown in FIG. 6, cylindrical concave portions 73 and 74 having different inner diameters.
Are connected in a row. Seal rings 75 and 76 are provided on the inner wall surfaces of the cylindrical concave portions 73 and 74, respectively. The reciprocating motion control valve 12 is accommodated in the cylindrical concave portions 73 and 74, and the seal rings 75 and 76 cooperate with the outer peripheral surfaces of the small diameter portion 77 and the large diameter portion 78 of the reciprocating motion control valve 12. Then, the port 62 of the inner housing 8
Compressed air coming in from the small diameter portion 77 and the gap between the large diameter portion 78 of the reciprocating motion control valve 12 and the port 64
The air is supplied to the air reservoir 59 or the compressed air in the air reservoir 59 is exhausted to an exhaust passage.

The seal rings 75 and 76 apply frictional force to the reciprocating motion control valve 12 when the piston rod 5 retreats, and the reciprocating motion control valve 12 has a slight delay in the return operation of the piston rod 5. When it moves backward and the seal of the seal ring 80 is released, the compressed air in the air reservoir 59 is exhausted.

The reciprocating motion control valve 12 is connected to the piston rod 5
Is slidably supported at the rear end. The reciprocation control valve 12 is prevented from falling off at the rear end of the piston rod 5 by a stopper 79. A seal ring 80 is attached to a rear outer periphery of the large diameter portion 78 of the reciprocating motion control valve 12, and the seal ring 80 passes through a concave portion 81 provided on an inner wall side edge of the port 64 of the inner housing 8. Sometimes, the air in the air reservoir 59 is exhausted.

In the vertical wall of the storage housing 52, compressed air exhausted from the air reservoir 59 of the intake / exhaust control valve 11 through the cylindrical concave portion 74, and the reciprocating control valve 12
A block bumper 94 that attenuates the vibration of is attached. The block bumper 94 is made of an elastic material such as rubber so as to easily absorb vibration, and is formed in an annular shape so as to correspond to a cross-sectional shape of a rear portion of the inner housing 8.

When the intake / exhaust control valve 11 is switched to the first switching position 13
Is slid to the second switching position 14 by exhausting compressed air from the air reservoir 59 into the cylindrical recess 74. The air exhausted to the cylindrical recess 74 is exhausted from the storage chamber R. It is sent to the road 20. When the piston 4 returns from the hydraulic pump 3 to the cylinder head 7, the air in the chamber 6 is exhausted from the gap 58 into the storage chamber R and exhausted from the exhaust passage 20. As described above, since the compressed air for reciprocating the piston 4 is exhausted into the storage chamber R and is exhausted in an annular shape, the storage chamber R is formed small, while the annular direction and the axial direction of the piston rod 5 are increased. Therefore, a sufficient exhaust area can be secured, and the speed of the reciprocating operation of the piston 4 can be increased.

A hydraulic pump 3 having a hydraulic cylinder is fixed to the front of the air cylinder 2. A flange 89 protrudes from a peripheral edge of the front end of the hydraulic pump 3, and a hydraulic cylinder 90 is fixed to the flange 89 by bolts. At the end of the hydraulic pump 3 facing the air cylinder 2 side, as shown in FIG. 1, a circular recess 35 having substantially the same diameter and the same size as the inner peripheral wall of the air cylinder 2 is formed. At the center, a cylindrical hole 33 for holding the front end 32 of the piston rod 5 slidably in a watertight manner is formed. The cylindrical hole 33 is connected to the reservoir and the hydraulic cylinder 90 via a hydraulic suction port 85 and a hydraulic discharge port 86. Front end 32 of piston rod 5
Reciprocates inside the cylindrical hole 33, the oil in the reservoir is sucked into the cylindrical hole 33 through the hydraulic suction port 85, and the oil is further discharged through the hydraulic discharge port 86, and Supplied to In the vicinity of the hydraulic suction port 85 and the vicinity of the hydraulic discharge port 86, the oil in the cylindrical hole 33 is prevented from flowing out from the hydraulic suction port 85 and the oil on the hydraulic cylinder 90 side is prevented from flowing into the cylindrical hole 33. Check valves 87 and 88 are provided, respectively.

The hydraulic cylinder 90 is filled with oil in the oil chamber 91 of the hydraulic cylinder 90 by repeating the reciprocating operation of the piston 4, and the pressing portion 92 moves forward.
When the pressing portion 92 moves forward with the hydraulic tool attached to the attachment holder 93, the pressing portion 9
Work is performed on the hydraulic tool by the pressing operation of 2.
The hydraulic cylinder 9 is provided on the flange 89 and the hydraulic cylinder 90.
There is provided a discharge valve (not shown) capable of discharging oil from the oil chamber 91 inside. When the discharge valve is opened, the oil in the oil chamber 91 is discharged from the middle of the cylinder of the hydraulic pump 3, and the discharged oil is stored in a reservoir (not shown). As a hydraulic tool, for example,
A bender for bending a metal bar or a cutter for cutting is attached.

Next, the operation of the power generator for a hydraulic device according to the present invention will be described with reference to FIGS.

FIG. 2 shows that the trigger 23 is pulled, the compressed air supplied to the rear portion of the main valve 22 is exhausted, and the main valve 22 is retracted to allow communication between the supply chamber 27 and the middle housing 9. Shows the state immediately after. The piston 4 approaches the vicinity of the cylinder head 7 by the restoring force of the coil spring 36, and the volume of the chamber 6 is minimized.

When the main valve 22 is opened, first, a supply chamber 27 formed in a cylindrical shape around the air cylinder 2.
The compressed air in the air enters the cylindrical space 10 containing the intake / exhaust control valve 11 via the ports 43a and 43b at the upper part of the middle housing 9. The compressed air acts on the front end side of the intake / exhaust control valve 11 to retreat the intake / exhaust control valve 11 to the rear of the cylindrical space 10, and the compressed air from the ports 43 a, 43 b on the front upper portion of the cylindrical space 10. Compressed air enters.

The compressed air that has entered the front of the cylindrical space 10 is subjected to a port 62 opening at the top of the inner housing 8, a cylindrical recess 73 of the inner housing 8, and a gap 63 at the front end of the reciprocating control valve 12. , Cylindrical recess 7
4, the air enters the air reservoir 59 via the port 64 and the gap 61. As the compressed air accumulates in the air reservoir 59, the intake / exhaust control valve 11 moves forward so as to approach the piston 4 as shown in FIG.

FIG. 3 shows a state in which the intake / exhaust control valve 11 moves forward and stops at the first switching position 13. When the intake / exhaust control valve 11 is located at the first switching position 13, the port 43
b and the port 62 opening at the upper front part of the inner housing 8 are shut off, while the port 42 opening at the lower front part of the inner housing 8 communicates with the port 43b opening at the front part of the intake / exhaust control valve 11. I do. The compressed air entering from the port 43b continues to be supplied to the air reservoir 59 via the port 62 and the front end of the intake / exhaust control valve 11. The compressed air in the supply chamber 27
The piston 4 is supplied to the rear surface of the piston 4 in the chamber 6 via b, 69, 42, and the piston 4 is shifted to the hydraulic pump 3 side. The piston 4 compresses the coil spring 36 to increase the elastic biasing force of the coil spring 36.
By the displacement of the piston 4 toward the hydraulic pump 3, the piston rod 5 enters the deep portions of the cylindrical concave portions 73 and 74, and the reciprocating control valve 12 is pushed by a stopper 79 formed at the rear end of the piston rod 5 and moves forward. , And then the communication between the cylindrical recess 74 and the port 64 is cut off.

Immediately before the piston 4 compresses the coil spring 36 and reaches the position where the chamber 6 is most expanded, as shown in FIG. Is released. By releasing the seal between the seal ring 80 and the recess 81, the air in the air reservoir 59 is exhausted through the gap 58, the port 64, the gap between the reciprocation control valve 12 and the inner wall of the cylindrical recess 74. Further, since the piston rod 5 comes closest to the hydraulic pump 3 side, the reciprocating motion control valve 12 is fitted into the steps of the cylindrical concave portions 73 and 74 by the stopper 79 at the rear end of the piston rod 5.

When the air in the air reservoir 59 is exhausted, FIG.
As shown in (2), the intake / exhaust control valve 11 moves to the second switching position 14 side by the action of the compressed air acting on the front end side. Thereby, the chamber 6 and the ports 42, 69,
The gap 58 communicates with the exhaust path 20, the air in the chamber 6 is exhausted, and the piston 4 is
Starts to move toward the cylinder head 7 due to the repulsive urging force.

When the intake / exhaust control valve 11 is in the second switching position 14
When the chamber 6 communicates with the exhaust path 20, the piston 4 moves toward the cylinder head 7 by the resilient urging force of the coil spring 36, as shown in FIG. As the piston 4 moves, the piston rod 5 moves toward the vertical wall of the storage housing 52. The reciprocating motion control valve 12 is held for a short time in the steps of the cylindrical concave portions 73, 73 due to frictional resistance caused by sliding with the seal rings 75, 76, but the action of the compressed air acting on the front end surface side is soon. And moves toward the vertical wall of the storage housing 52 together with the piston rod 5.

As shown in FIG. 7, immediately before the piston 4 approaches the cylinder head 7 and reaches the reciprocating dead center on the cylinder head 7 side, the port 62 of the inner housing 8 is again turned into a cylindrical shape. The gap between the recess 73 and the reciprocation control valve 12 (between the seal rings 75 and 76) and the gap between the cylindrical recess 74 and the reciprocation control valve 12 (the seal ring 7).
6, 80), and communicate with the air reservoir 59 via the port 64 and the gap 61. As a result, air starts to accumulate in the air reservoir 59, and the intake / exhaust control valve 11 located at the second switching position 14 starts to move toward the first switching position 13.

When the intake / exhaust control valve 11 is in the first switching position 13
Then, the state is changed to the state of FIG. 2 again, and the steps between FIG. 7 are repeated. The main valve 22 is maintained in the supply chamber 2 while the trigger 23 is kept pulled.
As long as the piston 7 is released, the piston 4 repeatedly drives reciprocatingly, oil is sucked from the hydraulic suction port 85 of the hydraulic pump 3 shown in FIG.
The oil is filled in the oil chamber 91 and the work by the hydraulic cylinder 90 can be performed.

As described above, when the reciprocating motion control valve 12 and the intake / exhaust control valve 11 reciprocate, the block bumper 94 made of an elastic material attached to the vertical wall of the storage housing 52 causes the intake / exhaust control valve 11 to operate. Receiving compressed air exhausted from the air reservoir 59 through the cylindrical concave portion 74 and compressed air that escapes from the gap 58 between the middle housing 9 and the inner housing 8, vibration of the vertical wall of the storage housing 52 is suppressed, and reciprocation is achieved. The vibration of the dynamic control valve 12 and the vibration of the intake / exhaust control valve 11 are reduced.

[0076]

According to the power generator for a hydraulic device of the present invention, the portion near the piston rod of the damper protrudes.
Since the slope of the projecting portion of the damper smoothly curves in an S-shape, a washer is provided at the curved portion, and a coil spring is supported on the washer.
Even if the coil spring is compressed by approaching the damper side of the piston, the damper is prevented from being caught in the wound portion of the coil spring. For this reason, the durability of the damper is improved. Further, since the washer is curved along the curve of the damper, displacement of the washer and the coil spring is prevented, and unstable elastic force of the spring is prevented.

Therefore, according to the power generator for a hydraulic device of the present invention, when supplying hydraulic pressure to a hand-held hydraulic tool, it is possible to promote reduction in size and weight and to operate a hydraulic pump using compressed air. In addition, the elastic force of the coil spring for reciprocating the piston can be stabilized, and the durability of the damper supporting the coil spring can be improved.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a main configuration of a power generator for a hydraulic device according to an embodiment of the present invention.

FIG. 2 is a cross-sectional view of a state where a piston of the power generator for a hydraulic device in FIG. 1 is closest to a cylinder head.

FIG. 3 is a cross-sectional view of a state in which compressed air has entered the chamber of the power generator for a hydraulic device in FIG. 1 and the piston has started to advance;

FIG. 4 is a cross-sectional view showing a state where a piston of the power generator for a hydraulic device in FIG. 1 moves toward a maximum position of a chamber.

FIG. 5 is a cross-sectional view of a state where the piston of the power generator for the hydraulic device of FIG. 1 has reached the maximum position of the chamber and the intake / exhaust control valve is located at the second switching position.

FIG. 6 is a cross-sectional view showing a state in which a piston of the power generator for a hydraulic device in FIG. 1 is retracted toward a cylinder head by an elastic force of a coil spring, and air in a chamber is exhausted.

FIG. 7 is a cross-sectional view of a state in which a piston of the power generator for a hydraulic device in FIG. 1 approaches a cylinder head side and compressed air starts to enter an air reservoir at a rear portion of the intake / exhaust control valve.

FIG. 8 is a sectional view of a piston rod and a reciprocation control valve.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 Power generator for hydraulic device 2 Air cylinder 3 Hydraulic pump 4 Piston 5 Piston rod 6 Chamber 7 Cylinder head 8 Inner housing 9 Middle housing 10 Cylindrical space 11 Intake / exhaust control valve 12 Reciprocating motion control valve 13 First switching position 14 Second switching position 15 Handle portion 19 Supply path 20 Exhaust path 22 Main valve 27 Supply chamber 28 Outer housing 31 Bumper 31a Projection 33 Cylindrical hole 34 Pressurizing chamber 35 Washer 36 Coil spring 39 Vent 40 Piston damper 42 Port 43a, 43b Port 52 Storage housing 69 Port 85 Hydraulic suction port 86 Hydraulic discharge port 94 Piston damper P Piston control mechanism R Storage chamber

Claims (1)

[Claims] 1. A hydraulic pump and an air cylinder are arranged in series along an axial direction of a cylinder rod of a piston in an air cylinder, and a cylinder head is provided at a portion of the air cylinder opposite to the hydraulic pump. A piston control for supplying and exhausting compressed air to a chamber between the front piston and the cylinder head at a position of the cylinder head opposite to the hydraulic pump while inserting the piston rod through the cylinder head; A mechanism is provided, a cylindrical hole extending in the axial direction of the cylinder rod is opened in the side surface of the hydraulic pump of the air cylinder, and a portion of the cylindrical hole on the hydraulic pump side is connected to a hydraulic pressure suction / discharge part of the hydraulic pump. At the same time, the front end of the cylinder rod is slidably held in the cylindrical hole, and the cylindrical hole is inserted into the air cylinder. An annular damper, which can insert the cylinder rod and support the piston, is provided at the opening edge, and a portion of the damper near the piston rod protrudes in the axial direction of the piston rod. The inclined surface near the inner peripheral wall of the air cylinder is smoothly curved into an S-shape, and a washer formed in a ring shape while being curved along the curved surface of the inclined surface is brought into contact with the inclined surface. A power generator for a hydraulic system, wherein a coil spring is disposed between a washer and the piston, and the coil spring urges the piston away from the hydraulic pump.