US3610107A

US3610107A - Torque cylinder

Info

Publication number: US3610107A
Application number: US850836A
Authority: US
Inventors: Seiji Kawaguchi
Original assignee: Daiei Kogyo Sha Co Ltd
Current assignee: Daiei Kogyo Sha Co Ltd
Priority date: 1969-08-18
Filing date: 1969-08-18
Publication date: 1971-10-05
Anticipated expiration: 1988-10-05

Abstract

THE TORQUE CYLINDER IS OPERATED BY FLUID UNDER PRESSURE, AND COMPRISES A PRIMARY MEMBER WHICH IS MOVED BY FLUID PRESSURE AND IS GUIDED FOR SUBSTANTIALLY RECTILINEAR MOVEMENT IN THE CYLINDER. AN OPERATING SHAFT HAS A REVERSIBLE HELICAL DRIVING CONNECTING WITH SUCH MEMBER. TWO SECONDARY MEMBERS ARE LOCATED ON OPPOSITE SIDES OF THE PRIMARY MEMBER AND ARE MOVED BY FLUID UNDER PRESSURE. THEY ARE ARRANGED TO DRIVE THE OPERATING SHAFT AXIALLY, AND A PASSAGE IS PROVIDED FOR CONDUCTING FLUID PAST EACH OF THE SECONDARY MEMBERS. TWO VALVE-CONTROLLED EXHAUST PORTS ARE PROVIDED, EACH CONNECTED TO THE SPACE IN ONE END OF THE CYLINDER BEYOND ONE OF THE SECONDARY MEMBERS. TWO VALVE-CONTROLLED INLET PORTS ARE PROVIDED FOR ADMITTING FLUID UNDER PRESSURE SELECTIVELY AT EITHER END OF THE PRIMARY MEMBER WHILE THE EXHAUST PORT AT THE ADJACENT END OF THE CYLINDER IS CLOSED, IN ORDER TO ROTATE THE SHAFT BY MOVING THE PRIMARY MEMBER INTO ENGAGEMENT WITH ONE OF THE SECONDARY MEMBERS AND TO TRANSLATE THE SHAFT BY MOVING ALL THREE MEMBERS IN UNISION.

Description

7 SEIJI KAWAGUCHI 3,610,107

TORQUE CYLINDER L19 IZIIZU Filed Aug. 18, 1969 5 Sheets-Sheet 1 In a E Q 1 g N r n a 3 E 3 Q1 Q g g g e Q Q H 1% I s I Q a g k 5 Sheets-Sheet :3

3N UM am M 2 E d 3 N 1 wry?! c .1 I 7 A Oct. 5, 1971 SEIJI KAWAGUCHI TORQUE CYLINDER Filed Aug. 18. 1969 Q E mm W m w? E i a Q N 2 em 1971 SEIJI KAWAGUCHI 3,610,107

TORQUE CYLINDER Filed Aug. 18, 1969 5 Shouts-Shoot t an, 14 JJ 53 30 5 33 b: 1W

5, 1971 SEIJI KAWAGUCHI 3,610,107

TORQUE CYLINDER Filsd Aug. 18, 1969 5 Sheets-Sheet 5 209 206 202 2w III 5- -5. 5

u IAVIIZTAI/A'IAVI/I United States Patent Oflice 3,610,107 Patented Oct. 5, 1971 ABSTRACT OF THE DISCLOSURE The torque cylinder is operated by fluid under pressure, and comprises a primary member which is moved by fluid pressure and is guided for substantially rectilinear movement in the cylinder. An operating shaft has a reversible helical driving connection with such member. Two secondary members are located on opposite sides of the primary member and are moved by fluid under pressure. They are arranged to drive the operating shaft axially, and a passage is provided for conducting fluid past each of the secondary members. Two valve-controlled exhaust ports are provided, each connected to the space in one end of the cylinder beyond one of the secondary members. Two valve-controlled inlet ports are provided for admitting fluid under pressure selectively at either end of the primary member while the exhaust port at the adjacent end of the cylinder is closed, in order to rotate the shaft by moving the primary member into engagement with one of the secondary members and to translate the shaft by moving all three members in unison.

BACKGROUND OF THE INVENTION This invention relates to a torque cylinder, and more particularly to a fluid pressure operated torque cylinder for accurately controlled reversible rotary motion, or rotary motion and reciprocating motion.

A piston operating in a cylinder ordinarily does not undergo rotation, but only reciprocating motion. In order to produce rotary motion it is necessary to control the piston shaft by means such as a key or the like.

To rotate the piston shaft after or before forward motion, and when suitable forward motion has been done to rotate the piston shaft reversely, has required very complicated mechanism heretofore. To contain this control mechanism in a cylinder it was necessary to reduce the pressurized area of the piston. And also, to obtain the desired torque required a large cylinder.

SUMMARY OF THE INVENTION In accordance with this invention, a piston shaft is provided eccentrically on a piston in a cylinder, and the piston shaft is operated reciprocatively, so that the piston is reciprocated by fluid pressure or elasticity of a spring without rotating the piston.

In the present torque cylinder, in which the driving shaft is located eccentrically of the piston shaft, a key for the piston is not required, and also the pressurized area of the piston is very small, and the capacity of the cylinder is also small, and both rotary and reciprocating motion of the piston and driving shaft are made possible.

Further this invention provides reciprocating motion of the driving shaft, and clockwise and counterclockwise rotary motion in a predetermined position, so that this invention may be used to bend a metal plate or tube, turn work around, or operate various remote control clutches and the like.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal vertical section of a torque cylinder embodying the invention.

FIG. 2 is a front view thereof.

FIG. 3 is a longitudinal vertical section of a second embodiment of the torque cylinder, connected to a reversing valve.

FIGS. 4A, 4B, 4C and 4D are longitudinal vertical sections showing the operation of the torque cylinder.

FIG. 5 is a longitudinal vertical section of a further embodiment of this invention.

FIG. 6 is a front view of the torque cylinder of FIG. 5.

FIG. 7 is an exploded view of the essential parts in FIG. 5 and FIG. 6.

DESCRIPTION OF THE PREFERRED EMBODIMENTS The first embodiment, shown in FIG. 1, produces rotary motion and reciprocating motion by means of a fluid delivered under pressure.

101 is a cylinder, and 102 is a piston in the said cylinder. 103, 103 are O-rings fitted in grooves formed on the outer surface of the piston 102. 41 and 51 are closures which are inserted into both ends of the cylinder 101. 71 is a cylinder for a piston shaft 61 located on the centerline X, offset from the center-line X of the piston 102. 81 is an O-ring which is set in a groove in the surface of the piston shaft 61. 91 is a stem, on the right end of a driving shaft 110, which is guided in a hole drilled in the piston 102 on the center-line X. On the right side of this hole is a chamber 112 for a coiled spring 111, the right end 113 of which bears against the base of the piston shaft 61, and the left end of which bears against a base 114 secured to the right end of the driving shaft 110. An internal thread 115 is provided in the left end of the piston 102, which end is of reduced diameter and is located on the centerline X. A cavity 116 is provided next to the internal thread 115. An external thread is provided on the surface of the driving shaft 110, and this external thread is screwed into the internal thread 115. 118 is an O-ring which is inserted in a groove on the surface of the stem 91 of the driving shaft. 119 is a hole drilled on the centerline X through the closure 51 to receive a bushing 120. 121 is an O-ring set in an internal groove in the bushing 120, to maintain a seal when the driving shaft 110 slides in the bushing. 122 and 123 are needle valves. Needle valve 122 connects the chamber 2a on the right side of the piston 102 with the cylinder 71 on the right of the piston shaft 61. The needle valve 123 connects the left chamber 2b with a space 19a on the right side of the bushing 120. 124 and 125 are horizontal ducts for fluid which are connected by the needle valves 122 and 123 with the right and left chambers of piston 102. When a fluid flows into the right chamber 2a of piston 102 and into cylinder 71 through the duct 124, the driving shaft 110 moves to the left with piston 102 until the driving shaft is stopped by a collar 10a. When the piston 102 continues to move to the left the coiled spring 111 is compressed and the base 114 separates from the left wall of the chamber 112. Piston 102 in moving to the left then rotates the external thread 117 by means of the internal thread 115. When the left portion of the piston 102 strikes collar 10a, the rotation of the driving shaft is stopped, and forward motion of the piston 102 is stopped.

Center-line X on the piston 102 and center-line X are eccentric to each other, so that when driving shaft 110 is rotated by piston 102, the piston 102 can undergo only reciprocating motion. When the pressure on the fluid in the duct 124 is relieved and fluid under pressure flows into the duct 125, the coiled spring 111 expands, the driving shaft 110 is suspended, and the piston 102 begins to move to the right. This movement brings about the reverse rotation of the driving shaft 110. When the base 114 contacts the left wall of the chamber 112, driving shaft 110 moves to the right so as to return to the predetermined position without further rotation.

Next the pressure on the fluid in the duct 125 is relieved, and fluid under pressure flows into duct 124. The above motions are repeated.

The stroke of the driving shaft 110 is determined by the travel of the piston 102. The amount of clockwise and counterclockwise rotary motion and the revolutions per minute of the driving shaft are determined by the angle of the internal thread.

In this device compressed air, oil pressure, gas pressure, water pressure, or an electromagnetic drive may be used.

The second embodiment is shown in FIG. 3 and FIGS. 4A, 4B, 4C and 4D. This torque cylinder causes a shaft to rotate and then move forward upon actuation of a reversing valve, and causes the shaft to rotate in the reverse direction and then move backward upon reverse actuation of the valve.

1 is a reversing valve which comprises a cylinder 2, in which a piston 5 having ports in the form of

grooves

3 and 4 is slidably mounted. Inlets 6a and 6b and outlets 7a and 7b for fluid are provided on the upper surface of the valve 1. Outlets 8a and 8b and inlets 9a and 9b are provided on the lower surface of the valve I. Said piston 5 has an operating handle K. The reversing valve 1 is of a conventional type. 11 is a tubular cylinder, in one end of which is a closure member 12 having a hole 12a eccentrically drilled therethrough. A bushing 13 is set in the hole 12a. In order to permit the fluid to be discharged from the left end of cylinder 11, a communicating hole 14 is drilled to intersect a discharge hole 14a. A closure member 15 having an eccentric hole 15a is set into the other end of said cylinder 11. A bushing 16 is set in the hole 15a. In order to permit fluid to be discharged from the right end of cylinder 11, a hole 17 is drilled to intersect a discharge hole 17a. In bushings 13 and 16 a shaft 18 is pivotally mounted. At both ends of the shaft, within the cylinder 11, spaced

holes

19, 19 and 20, 20 are drilled. Said holes 19, 19 are connected by a communicating hole 21, and said

holes

20, 20 are connected by a hole 22. Slidably mounted on said shaft, in the cylinder 11, are secondary members consisting of small

reciprocating pistons

23 and 24. One reciprocating piston 23 has a communicating hole 25 of which one end 25a registers with the end 14b of the communicating hole 14, and the other end 25b faces the surface of the shaft 18. Another said piston 24 has a communicating hole 26 of which one end 26a registers with the end 17b of the communicating hole 17, and the other end 26b faces the surface of the shaft 18.

A thread portion 27 is formed on the middle part of the shaft 18 in the cylinder 11.

An internal thread portion 28 in a reciprocating primary member consisting of a piston 29 is geared with said thread portion 27. Said reciprocating piston 29 is movably mounted in said cylinder 11.

Grooves

30 and 31 are formed on the upper surface of the piston 29. On the upper portion of cylinder 11,

inlets

32 and 33 are provided, to connect with the outlets 8a and 8b of the reversing valve by suitable tubing. And also, said discharge holes 14a and 17a are connected with the inlets 9a and 9b by suitable tubing.

Consequently, when one turns the handle K of the reversing valve clockwise, the piston 5 is moved in the direction of the arrow (as shown in FIG. 3), so that the outlet 8a is joined to the inlet 6a, and the fluid flows into the chamber a1 through the inlet 32 and groove 30. The reciprocating piston 29 is moved in the direction of the arrow (as shown in FIG. 4A) by this fluid pressure, and the shaft 18 is rotated in the direction of the arrow (FIG. 4B) by movement of this reciprocating piston 29. The valve formed by the

holes

19 and 21 opens as soon as piston 29 engages the small piston 24, so that fluid then flows into the chamber a2, passing through holes 19 and communicating hole 21, opening 25b and communicating hole 25. The small reciprocating piston 23 is thus moved 4 in the direction of the arrow (as shown in FIG. 4C) so as to move the shaft 18 to a predetermined position.

When one turns the handle K counterclockwise, the piston 5 is moved to the right, so that the outlet 8b is joined to the inlet 6b, and the fluid flows into the chamber b1 through the inlet 33 and groove 31. The reciprocating piston 29 is moved in the direction of the arrow (as shown in FIG. 4D) by this fluid pressure, and the shaft 18 is rotated in the direction of the arrow (as shown in FIG. 4D) by movement of this reciprocating piston 29. The fluid then flows into the chamber b2, passing through holes 20 and communicating hole 22, opening 26b and communicating hole 26. The reciprocating piston 24 is thus moved in the direction of the arrow (as shown in FIG. 4D) so as to return the shaft 18 to its original position.

In this embodiment, the driving shaft is located eccentrically of the piston shaft, so that in this embodiment a key is not required for the piston. This construction minimizes the pressurized area of the piston, whose thread portions control the reciprocating motion and rotary motion of the driving shaft.

The third embodiment is shown in FIGS. 5, 6 and 7. This embodiment relates to an apparatus, which can be used to produce only clockwise and counterclockwise rotary motion or to produce clockwise and counterclockwise rotary motion and reciprocating motion.

In the conventional apparatus, the shaft is driven from the moving member by a relatively large screw so as to be rotated by the movement of the said moving member. Said moving member is operated by suitable fluid pressure, so that in the conventional method of converting the reciprocating motion of a moving member into rotary motion and transmitting it to an operating shaft, a relatively large screw is required.

In the above mentioned construction, disadvantages have been experienced. One disadvantage is that it is very diflicult to convert the reciprocating motion into rotary motion, because great friction is caused by the screw. Consequently, in order to convert the reciprocating motion into rotary motion, great force is required.

One of the objects of this embodiment is to eliminate the above disadvantages.

In this third embodiment, the reciprocating motion is converted into rotary motion by means of a moving member having a comparably wide helical slot, and a rotary member which is driven by the action of the helical slot. This construction easily converts the reciprocating motion into rotary motion.

201 is a cylindrical casing having a flange 202 at one end, and having an internally threaded portion 203 at the other end. An adapter plate 204 is fixed on the flange 202 by screws 205. An inlet and outlet 206 for fluid, an inserting hole 208 for an operating shaft 207 and an inserting hole 210 for a thrust bearing 209 are drilled in the adapter plate 204. 211 is a pressure plate which is mounted in the casing 201. One end of a bellows 212 is fixed on pressure plate 211, the other end being fixed on a liner 213 which is mounted on the adapter plate 204. 214 is a moving member which is fixed on the pressure plate 211 by the screw 215. An inserting hole 216 for the shaft 207 is provided in the central portion of the moving member 214. Two comparatively wide helical slots 217 are cut in opposite sides of moving member 214. 218 is a guiding cylinder for moving member 214, having an inserting hole 219 in which operating shaft 207 is inserted, and having inserting holes 221 for a driver 220. The said operating shaft 207 is inserted into the inserting hole 208, the inserting hole 219, and the inserting hole 216, and the joint between the operating shaft 207 and the inserting hole 208 in the adapter 204, may be sealed by a conventional O- ring 222. The shaft 207 is fixed by a set screw 223 to the guiding cylinder 218. 224 is a bracket for the thrust bearing 209 which is fixed on the said operating shaft, this bracket 224 being located in the inserting hole 210, provided that the operating shaft 207 is inserted into the

holes

208, 219 and 216. 225 is a keeper plate bearing against thrust bearing 209. 226 is a closure which is screwed into the internally threaded portion 203. Coiled spring 227 is provided between the closure 226 and the pressure plate 211. Said pressure plate 211 is returned by the coiled spring 227 after each operation. Said driver 220 is pierced through the shaft 207, and both ends of the driver 220 projecting from the operating shaft 207 are inserted into the helical slots 217 and the holes 221. On the portions of driver 220 that pass through the helical slots 217, rollers 228 are mounted.

When fluid under pressure flows into the bellows 212 from the inlet 206, pressure plate 211 is moved against the coiled spring 227. Also, moving member 214 is moved, accompanying this movement of the pressure plate 211.

The operating shaft 207 is rotated according to the movement of moving member 214, by the driver 220 and rollers 228. The driver 220, being pierced through the operating shaft 207, is guided in the helical slots 217 by rollers 228, so that when moving member 214 is moved, operating shaft 207 is obliged to rotate by rollers 228 and driver 220.

Next, when fluid is discharged to relieve the fluid pressure in the bellows 212, the pressure plate 211 is moved to the left by the coiled spring 227, and the moving memher 214 is moved in the same direction, accompanying this movement. And also, this movement brings about counterclockwise rotary motion of the operating shaft 207. So, flowing in and out of the fluid brings about clockwise and counterclockwise rotary motion of the driving shaft 207.

Now it is apparent that the clockwise and counterclockwise rotary motion of the operating shaft 207 is produced by the helical slots 217, rollers 228 and driver 220, so that when the reciprocating motion of moving member 214 is converted into rotary motion of the operating shaft 207, the friction caused is so small that the conversion may be executed very smoothly. High fluid pressure is not required to operate this apparatus.

The mechanism consisting of a driver 220 and helical slots 217 is universally usable in the present torque cylinder, and may be substituted for the screw threads 115 and 117 in the device shown in FIG. 1.

I claim:

1. A torque cylinder operated by fluid under pressure, comprising a primary member which is moved by fluid presF-ure and guided for substantially rectilinear movement in the cylinder, and an operating shaft having a reversible helical driving connection with such member, wherein the improvement comprises two secondary members which are located in the cylinder on opposite sides of the primary member, and which are moved by fluid under pressure and are arranged to drive the operating shaft axially, a passage for conducting fluid past each secondary member from the space between the secondary member and the primary member to the space beyond the secondary member in the end of the cylinder, two valvecontrolled exhaust ports, each connected to the space in one end of the cylinder beyond one of the secondary members, and two valve-controlled inlet ports for admitting fluid under pressure selectively at either end of the primary member while the exhaust port at the adjacent end of the cylinder is closed, in order to rotate the shaft by moving the primary member into engagement with one of the secondary members and to translate the shaft by moving all three members in unison.

2. A torque cylinder according to claim 1 wherein a valve controlling the passage for conducting fluid past each secondary member is operated by the operating shaft to maintain such passage closed until the primary member engages the other secondary member.

References Cited UNITED STATES PATENTS 1,719,562 7/1929 Sala et al. 92-33 2,918,799 12/1959 Geyer 92-33 X 2,930,362 3/1960 Riester et a1 92-33 X 2,948,265 8/1960 Jensen et al. 92-31 X 2,955,579 10/1960 Block 92-33 3,103,834 9/1963 Neukom 92-31 X 3,143,932 8/1964 Lanman 92-31 3,153,986 10/1964 Mitchell 92-33 3,165,982 1/1965 Taylor 92-33 3,183,792 5/1965 Allen 92-33 3,457,838 7/1969 Rowe 92-33 MARTIN P. SCHWADRON, Primary Examiner L. I. PAYNE, Assistant Examiner US Cl. X.R. 74-25