US2876742A

US2876742A - Variable speed fluid pressure actuated impact device

Info

Publication number: US2876742A
Application number: US540271A
Authority: US
Inventors: John F Sherrill
Original assignee: EVA R LEMERT
Current assignee: EVA R LEMERT
Priority date: 1955-10-13
Filing date: 1955-10-13
Publication date: 1959-03-10
Anticipated expiration: 1976-03-10

Description

March 1o, 1959 J. F. SHRRILL 2,876,742

VARIABLE SPEED` FLUID PRESSURE ACTUATED IMPACT DEVICE Mai'ch 10, 1959 J. F. sHERRlLL 2,876,742

VARIABLE SPEED FLUID PRESSURE ACTUATED IMPACT'DEVICE Filed oct.A 1s, 1955 ,s sheets-sheet 2 T1114. im; .15 jJE IN VEN TOR.

Jan/vf @fee/L March 10, 1959 J. F. SHERRILL 2,876,742

. VARIABLE SPEED FLUID PRESSURE ACTUATED IMPACT DEVICE 55.17 [T1-E21: 'E522 INVENTOR.

VARIABLE SPEED FLUID PRESSURE ACTUATED IMPACT DEVICE John F. Sherrill, Plymouth, Ind., assignor to Eva R. Lemert, Plymouth, Ind.

Application October 13, 1955, Serial No. 540,271

19 Claims. (Cl. 121-20) This invention relates to a variable speed fluid pressure actuated impact device, and more particularly to a device of this character of the type wherein the impact member is rotatable. This application is a continuation in part of my co-pending application, Serial No. 507,589, filed May l1, 1955, now abandoned.

Heretofore impact devices have generally operated at a substantially constant speed regardless of the setting of the controls thereof. Variations in the control settings of such devices, such as riveting machines, have made possible variations in the force of the blow or variations in the stroke of the peen or other impact tool, but other factors usually have not been controllable, and in particular, the range of variations of the speed of prior irnpact devices of the air pressure actuated type has been limited.

It is the primary object of this invention to provide a novel, simple, highly efcient air pressure responsive impact device having means therein for controlling the speed of impact or operation, and in particular, for varying the number of blows or oscillations of the device per unit time over a wide range of speeds.

A further object is to provide a device of this character having control means for varying the rate of operation of the device and the number of blows per unit of time With-out substantial sacrifice of the amount of power or force derived from the pressure source.

A further object is to provide a device of this character having a rotatable -control valve operable to control the ilow of fluid under pressure through ports and passages in the device to reciprocate a power responsive member in timed relation to the speed of rotation of the control element.

A further object is to provide a device of this character by means of which it is possible to cause the operation of a reciprocating impact device at speeds greatly in excess of the speeds at which said devices have heretofore been capable of operating.

A further object is to provide a device of this character which is simple in construction, easy to assemble, and which has a minimum number of operating parts, so that the same may operate efficiently in a substantially trouble-free manner for long periods of time.

Other objects will be apparent from the following specification.

In the drawings:

Fig. l is a fragmentary side view of a spinning riveting machine employing my new improvement;

Fig. 2 is an enlarged longitudinal detail sectional view taken on line 2 2 of Fig. 1;

Fig. 3 is a fragmentary longitudinal sectional view illustrating the control valve in one operating position;

Fig. 4 is a longitudinal sectional view similar to Fig. 3 but illustrating the valve in a dilerent operating position;

Fig. 5 is an axial sectional view of a part only of the valve mechanism, taken on line 5 5 of Fig. 6;

States Patent ing machine.

2,876,742 Patented Mar. 10, 1959 ice Fig. 6 is an end view of the valve part shown in Fig. 5 viewed from the bottom thereof;

Fig. 7 is a transverse sectional view of the body of the device taken on line 7 7 of Fig. 2;

Fig. 8 is an axial sectional view of the valve rotor taken on line 8 8 of Fig. 9;

Fig. 9 is an end View of the valve rotor;

Fig. l0 is a transverse sectional View of the valve rotor taken on line 1.0 10 of Fig. 8;

Fig. 1l is a transverse sectional view taken on line 1.1 11 of Fig. 2;

Fig. 12 is a transverse sectional view taken on line 12-12 of Fig. 2, illustrating the position of the parts at the start of down stroke tiring;

Fig. 13 is a transverse sectional View taken on line 12-12 of Fig. 2 and illustrating the position of the parts at the end of the down stroke firing;

Fig. 14 is a transverse sectional view taken on line 12-12 of Fig. 2 and illustrating the start of upstroke firing;

Fig. 15 is a transverse sectional View taken on line 12-12 of Fig. 2 and illustrating the position of the parts at the end of upstroke firing;

Fig. 16 is a transverse sectional view taken on line 16-16 of Fig. 3 and illustrating the position of the parts at the start of downstroke firing;

Fig. 17 is a fragmentary axial sectional View -of a modified embodiment of the invention;

Fig. 18 is a transverse sectional view taken on line 18 18 of Fig. 17, and illustrating the parts at the start of the upstroke of the pressure responsive member;

Fig. 19 is a transverse sectional view taken on line 19 19 of Fig. 17 and illustrating the parts at the start of the upstroke of the pressure responsive member;

Fig. 20 is a transverse sectional view taken on line 18-18 and illustrating the position of the parts at the start of the down stroke of the pressure responsive member;

Fig. 21 is a fragmentary longitudinal sectional view taken on line 21-21 of Fig. 20 and showing the position of the valve at the start of the down stroke;

Fig. 22 is a fragmentary longitudinal sectional View taken on line 22-22 of Fig. 20, illustrating the position of the valve at the start of the downstroke; and

Fig. 23 is an axial sectional View of the rotatable valve taken on line 23-23 of Fig. 20.

Referring to the drawings which illustrate the preferred embodiment of the invention, and particularly Figs. 1 to 16, which illustrate an embodiment of the invention having one type of control valve, the numeral 10 designates an upright or standard forming a part of a support or rivet- Assuming that a riveting device is involved in which it is desirable to shift a riveting mechanism 12 vertically between operative and inoperative positions with respect to a Work-supporting table or platform (not shown), the support 10 will carry a slidable carrier 14 which preferably will rest upon the upper end of a coil spring 16 which in turn is supported and positioned by a collar or other abutment 18 fixedly secured upon the column 10. The slidable carrier 14 will pref,.- erably have a pair of spaced axially aligned bearing members 20 slidably encircling the column. Clamp members 22 project from the carrier and are adapted to embrace and grip the riveting mechanism 12. A member 23 will preferably interconnect the clamp members 22 so as to space the same and the bearings 20 in predetermined spaced relation.

The slidable carrier or frame unit will preferably include a portion carrying a base member 24 upon which an electric motor 26 is mounted. Base 24 may also serve to carry a support or bracket 28 for an idler pulley 30.

' The peen or impact member 32 of the hammer 12 will preferably have a pulley 34 mounted thereon, around which is trained a drive belt 36 leading to a pulley 38 mounted on the shaft of the motor 26, said belt 36 being trained around the idler 30. The arrangement of the parts is such that the motor 26 will serve to' drive the pulley 34 and rotate the peen 32 of the riveting mechanism.

The carrier will also preferably include the upwardly extending portion 40, such as a sleeve, at the top thereof, from which extends laterally a platform 42 mounting a variable speed motor 44 substantially coaxial and above the riveting member 12', with its shaft 46 having a drive connection with a control part of theriveting mechanism, to be described. Any suitable controller 4S may be provided for regulating or controlling the speed of operation of motor 44 at will, as Well understood in the arts.

The impact hammer or rivet mechanism has a cylindrical body 50. As here shown, the body 50 constitutes a tube open at its opposite ends and having a central longitudinal bore 52 therethrough. At one end the body 50 has an internally screw-threaded enlarged bore portion 54, Within which is screw-threaded an end member 56 which has an axial bore therethrough mounting a bearing sleeve 58 within which the shaft 46 is journaled. The end member 56 has a bore 60 therethrough which communicates at its inner end with the bore of the body 50. The mouth portion 62 of the bore 60 is preferably enlarged and screw-threaded to accommodate connection of a conduit 64 extending to a source of air under pressure.

The body 50 has a longitudinal intake passage 66 formed therein and terminating spaced from one end thereof. As here shown, passage 66 is closed by a plug 68 at the end thereof mounting the head S6. Passage 66 communicates with a bore 70 leading to the interior of the bore 52 adjacent the neck portion 54. The opposite end of the passage 66 is open. A longitudinal exhaust passage 72, preferably displaced approximately 180 degrees from the intake passage 66, is closed at the end thereof adjacent 4the head S6, as by a plug 74. A port 76 communicates with the interior of the bore 52 at the end adjacent the neck 54 in longitudinally inwardly spaced relation to the location of the port 70. A radial exhaust port 78 is spaced circumferentially from the port 76, preferably slightly less than 90 degrees, and is spaced from the end of the body S the same distance as the port 76. A pair of

radial ports

79 and 80 are formed in the body 50 intermediate the ends thereof and adjacent theinner ends of the strokes of a pressure responsive piston member 82 which is reciprocable in the bore 52 between the inner and outer limit positions.

An end cap 84 is screw-threaded externally upon the body S0 at the end thereof opposite that which mounts the member 56. The end cap 84- and end member 88 cooperate' to dehe a chamber in the tubular body` The member 84 has an axial bore therethrough of different diameters and is shouldered at 86 to provide a seat for an end plate member 88 which is pressed against the end of the tubular body 50 and which has recesses 90 in its inner face adapted to communicate with the

bores

66 and 72 and with the chamber 52 in the interior of the tubular body S0. The disk or end plate 88 has a central bore therein lined by bearing sleeve 92 which receives the inner end portion 94 of the peen member 32. The peen member 32 has a circumferential shoulder 96 delining a stop limiting inward movement of the peen member 32 when pressed upon by a coil spring 98 encircling a portion of the peen member and seating against a shoulder 99 in the cap member 84.

A rotary valve controls fluid ow through the device from inlet passage 60 to outlet 78. As here shown, the valve has a housing or socket of the construction best illustrated in Figs. and 6 which seats in the end of the bore S2 adjacent to the end member 56. The valve housing is a cupshaped member having an end wall 100, va cylindrical wall 102, and an outturned circumferential ia'nge 104 at its open end. A port or aperture 106 is formed in the side wall 102 at such a location as to register with the inlet port 70 when the housing is properly oriented in the body with the ange 104 bearing against the shoulder of the body 50 adjacent to the projecting sleeve portion 54. In substantially diametrically opposed relation to port 106 and longitudinally spaced therefrom is a port 108 to normally register with the exhaust port 76 in the body. A port 110 is circumferentially spaced from the port 10S at the same longitudinal position as the port 108. An aperture 112 is formed in the base or end member 106 spaced from the center thereof and radially oriented similarly to the opening 110. The cup-shaped housing fits very snugly within the bore 52, as by a press lit, so that substantially no leakage of fluid under pressure will be experienced between the same and the interior wall surface of the body 50.

A valve element has a snug rotative lit within the valve socket, such as housing 190, 102, and preferably is of the construction illustrated in Figs. 8, 9 and l0. It will Vbe understood, however, that the valve element may be stationary and the housing 160, 192 may be a rotating sleeve. The valve element comprises a solid cylindrical body 114 of a length substantially equal to the depth of the cavity of the valve housing and has a detachable driving connection with shaft 46. Ffhus body 114 may have projecting therefrom at its outer end one or more lugs 116 which interfit with configured end portions of the shaft 46 to be driven by said shaft upon rotation of the shaft. The valve member 114 has a passage 11S open at its outer or upper end, as viewed in Fig. 4, which terminates in a lateral portion 120 open at the periphery of the body and adapted to register and communicate with the ports 166 and itl in one rotative position of the valve member 114. 1n substantially diametrically opposed relation to the bore 11S is provided a longitudinal boie 122 extending completely through the valve member 114 spaced from the axis of member 114 and adapted to register with the port 112 in the bottom 1% of the valve housing when properly oriented therewith. A longitudinal passage 124 extends from the bottom or inner end of the valve member 114 to a point opposite the ports 1Gb and 110 in the valve housing at which a lateral outlet 126 from the passage 124 is formed. The spacing of the

longitudinal passages

122 and 124 from the axis of member 114 will be substantially equal so that they are successively brought in register with the housing passage 112 incident to rotation of the member 114. A circumferential groove 12S of an arcuate extent greater than the spacing between the passages 10S and 110 is formed in the valve member 114 to extend substantially 90 degrees therearound, with one end portion thereof located adjacent the passage 122 and the opposite end thereof extending in a direction away from the longitudi nal

passages

122 and 124.

Assuming that the device is in the position illustrated in Figs. 2 and 4 with the piston or pressure responsive member 82 being located at the lower end of the stroke, the valve will be located in the position shown in Fig. 14. Fluid, such as air, under pressure from the conduit 64 passes through the bore 60 in the head member 56 into the portion 53 of the bore of the tube at the outer end of the valve member 114. The air passes 'through the valve element passage 113, 120, through port 166 in the valve housing and port 70 in the body 50, and thence through the longitudinal passage 66 to and through the recess 90 in the disk S8 to act against the bottom end of the piston or pressure responsive member 82. -At the same time, or slightly sooner, the longitudinal passage 124 is approaching register with the passage 112 in the bottom of the valve housing and the lateral outlet 126 is approaching register with the exhaust passage 78 in the body 50 so as to open to atmosphere the portion of the bore above the pressure responsive member 82 for the escape of pressure in advance of the upward `movement of the member 82. At the same time the circumferential groove 128 of the valve element approaches register with the

ports

76 and 108. The parts are so oriented that the port 118 will have passed out of communication with the

ports

106 and 70 before the

exhaust passages

124, 126 pass out of communication with the exhaust port 78, so that throughout the upstroke of the pressure responsive member, the upper portion of the chamber will have been open to atmosphere to exhaust air therefrom. The position of the valve part 114 at the end of the upstroke is illustrated in Fig. 15, in which it will be seen also that passage `118 is out of supply relation to the ports communicating with the passage 66, the passage 126 is just leaving communicating relation with the outlet 78, and the circumferential groove 128 communicates with the passage 72 and its leading end approaches communication with the exhaust outlet 78.

A slight additional rotation of the parts from the Fig. 15 position in a clockwise direction shifts the parts to the position shown in Fig. 12 for commencement of the downstroke of the device. At this time the parts of the mechanism are positioned substantially as illustrated in Fig. 3. This rotative position of the valve 114 has brought the leading end of the circumferential groove 128 into communication with the exhaust port 78, thereby opening communication between the bottom chamber of the device and the atmosphere through the passage 72. At the same time the passage 122 in the valve moves into register with the opening 112 in the bottom of the valve housing so that air under pressure within the chamber 53 passes directly through the valve to act upon the upper surface of the pressure responsive member 82 and drive the same downwardly. By the time the rotative valve member 114 reaches the position shown in Fig. 13, the pressure responsive member 82 Will have reached the lower end of its stroke and have imparted a blow to the end of the peen 94. No further movement will occur thereafter until the valve member 114 rotates back to the Fig. 14 rotative'position of the parts, whereupon a new cycle commences.

It will be apparent that the timing of any given cycle of operation depends upon the speed of rotation of the valve member 114. Since the valve member 114 is driven from an external source, it can be rotated at any selected speed, particularly if connected with a variable speed drive, such as a Variable speed electric motor 44. The speed variations made possible in this device, insofar as the number of impacts per unit of time is concerned, depend upon speed variations of the drive member, and a wide range of speeds may be obtained by manipulating controller 45 where the drive member has a wide range of speed variation.

The

ports

79 and 80 prevent recoil of the pressure responsive reciprocating member 82. The

ports

79 and 80 are so located that when the pressure responsive member 82 is at the lower end of its stroke, as illustrated in Fig. 2, the port 80 will be sealed thereby but the port 79 will be slightly open. Thus as any recoil action occurs, bleeding of the air in the chamber 52 above the pressure responsive member or piston 82 through the bore 79 stops and recoil is prevented. Upon the reverse stroke of the piston 82, the ports 79 is closed and, at the end of the stroke, a part of the port 80 is open to vent air pressure below the piston 82 only so lon-g as the piston member does not recoil. Closing of the bleed passage 80 in the event of recoil brings into play the pressure remaining within the bore to resist or damp continuance of recoil.

It is interesting to observe that apart from the pressure responsive member 82 and the peen 32 to be driven thereby, the only moving parts in this mechanism consist Of-the driving shaft 46 and the valve element 114. This makes possible a construction in which wear of the parts is reduced to a minimum and low cost and simple construction is made feasible. Observe in this connection that the valve 114 is readily Iaccessible for repair and inspection by removing the end member 56 and disconnecting the shaft 46 from the valve element 114. The connection between the latter parts is preferably of the rib and groove type which is effected and disengaged easily and without requiring the use of connectors between the parts. Removal of the end member 56 makes possible gripping of the Valve element 114 at the projection 116 thereof for removal for purposes 4of inspection, replacement or repair. -It will be understood that means for rotating the peen 32, as here illustrated, may be omitted if desired, by simply disconnecting the belt 36.

The embodiment of the invention illustrated in Figs. 1 to 16, inclusive, is directed to a construction in which one -cycle of the pressure responsive member occurs upon each revolution of the valve member. In this instance the maximum speed of reciprocation is limited so that the number of cycles equals the number of revolutions of the driving member. This relationship can be varied, and the speed of the pressure responsive member can be greatly increased by providing an arrangement accommodating multiple reciprocations of the pressure responsive member during each revolution of the valve member. This can be accomplished simply and easily by properly selecting the number and location of the passages and ports in the valve and in the body. As an illustration of the manner in which this may be accomplished, I have shown a modied embodiment of the invention in Figs. 17 to 23, inclusive, which is so constructed as to provide two oscillations 4or cycles of reciprocation of the pressure responsive member for each revolution of the valve element.

In the construction illustrated in Figs. 17 to 23, the parts are constructed substantially the same as illustrated in the preferred embodiment of the invention, and, to the extent that the parts are similar, the same reference numerals will be applied thereto. The tubular body member 50 has an end member 56 mounted on one end thereof and provided with the air inlet passage 60 for supplying air to a chamber portion S3 between the end member 56 and the valve element 114 and associated parts. The end chamber 56 has the bushing 58 therein journalling the rotatable shaft 46 of a variable speed drive means, such as a motor 44, by means of which the valve element 114 is rotated. A valve housing having bottom wall and cylindrical wall 102 seats in the bore 52 and journals the valve element 114. The portion of the structure below the valve housing in Fig. 2 will be substantially the same in the modied embodiment.

The body 50 has two

longitudinal inlet passages

66 and 66 formed therein, each open at its lower end for communication with the interior of the bore 52 in the manner illustrated in Fig. 2, and each closed by a plug 68 at its upper end to separate the same from the chamber 53. The

passages

66 and 66 are preferably substantially diametrically opposed, as illustrated in Fig. 18. Exhaust passage 72 constitutes a third longitudinal passage in the body wall and preferably is located substantially 45 degrees displaced from one of the inlet passages, here shown as inlet passage 66. 'I'he lower end of the passage 72 communicates with the bore 52 and the upper end of the passage is closed by a plug 74 to separate the same from the chamber 53. The

passages

66 and 66 extend longer than the passage 72, as seen by comparison of Figs. 17 and 22. Exhaust port 78 is formed in the tubular body 50 at the level of the upper end of the passage 72 but is displaced therefrom approximately 45 degrees, as best seen in Fig. 19. Each of the,

passages

66 and 66 opens to the bore 52 at a port 70, and the upper end of the passage 72 opens to the bore 52 at a passage` 76. l

The cup-shaped valvehousing has two diametrically opposed ports 106 formed therein at the level of the ports 70 and registering therewith. A port 108 in the housing wall 102 registers with the port 76 which communicates with the passage 72. The port 110is formed in housing' wall 102 and registers with the exhaust port 78. Two ports 112 are formed in the bottom wall 100 of the valve liis'ing equispaced from the center thereof and substantially diametrically opposed.

The rotary valve member 114 has a longitudinal passage 150 extending therethrough and spaced from the center thereof the same distance that the ports 112 are spaced from the center of the end wall 101) of the valve housing, so that upon each revolution of the valve member 114 the passage 15) will successively register and communicate with the two end wall ports 112. A lateral port 152 projects from the passage 150 at the level of the ports 106 of the valve housing so as to communicate with said housing ports las? successively. As seen in Fig. 18, a line drawn between the centers of the end wall ports 112 is Substantially at right angles to a line drawn between the ports 106 and, consequently, the arrangement is such that air entering the passage 6d and the chamber 53 and thence owing into the passage 150 is alternately delivered at a port 106 and a port 112, as illustrated in Figs. 17 and 20, respectively. The valve body 114 has a pair of longitudinal passages 154 arranged in diametrically opposed relation and spaced apart the same distance as the passages 112 with which the same are adapted to register in the rotative position or the parts illustrated in Figs. 17 and 18. The passages 154 terminate in laterally outwardly extending ports 156 at the level of the ports 108 and 11i) and adapted to register therewith, as illustrated at the lower portion of Fig. 19. Two similar grooves 158, each slightly more than 90 degrees in extent, are formed in the periphery of the member 114 at the level of the

ports

108 and 110 and are adapted during a predetermined portion of each rotation of the member' 114 to establish communication between the

ports

108 and 110, as illustrated in Fig. 20.

In the operation of the device, the parts are positioned as illustrated in Figs. 17, 18 and 19 at the start of the upstroke of the pressure responsive member or piston. Air under pressure enters the passage 60, chamber 53, passage 150, and then passes through

ports

152, 1456 and 7|] and into the longitudinal passage 66 leading to the 'bottom of the bore 52 so as to permit the air to act upon the pressure responsive member or piston and force the same upwardly. At that time, as illustrated in Fig. 19, one of the

passages

154, 156 in the valve member 114 will register with the exhaust port 73, 110 and both of the passages 154 will register with the bottom passages 112 in the valve housing. Air contained in the bore 52 above the pressure responsive member is therefore discharged through one of the ports 112, one of the valve passages 154-156, the port 110 and the exhaust port 78. The

ports

112 and 154 will preferably be slightly larger than the port 152 communicating with the valve passage 150 so that the same will be in communication to establish exhaust to atmosphere through exhaust port 7S slightly in advance of commencement of register of the supply'

ports

150, 152 with the ports 1616 and 70 leading to' intake passage 66. This size relation also permits said exhaust ports to remain open after the

inlet ports

156, 152 pass out of communication with the

housing ports

106 and 70. Thus the full upstroke ofthe pressure responsive member is provided by the air supplied to the bottom or the bore 52 during the time in which the passage 152 communicates with the

inlet passage

66 or 66'.

Further rotation of the valve member 114 brings the parts to the position illustrated in Figs. 2O to 22 for the down stroke of the pressure responsive member. In this position the passage 150 communicates with one of the bottom wall ports 112 to supply air under pressure to the upper part of the bore 52. The part of the bore below the piston is placed in communication with atmosphere through passage 72, ports 76 and 198, one of the grooves 158, port 110 and outlet port 78. `In this connection the grooves 158 will be so oriented relative to the passage 150 as to establish a path for discharge of air from the bottom 8 of the bore 52 slightly in advance of registration of passage with port 112, and will remain in communication with the

ports

108 and 110 until a time shortly after the passage 150 passes out of communication with the port 112.

Thereupon, continued rotation of the member 114 will bring the passage 150 to a point substantially diametrically opposed to the position illustrated in Fig. 18, at which it will supply air under pressure to the passage 66 for another upstroke of the piston. Still further revolution of the valve member will bring the passage 150 into communication with the second of the two bottom wall ports 112. Thus, by the time 360 degrees of revolution of the valve element have occurred, two complete cycles of the piston member will have occurred.

The multiple cycling or oscillation of the reciprocating member relative to each rotation of the valve makes possible very high speeds of oscillation of the pressure responsive member or piston, and these high speeds may be controlled by controlling the rate of rotation of the valve driving shaft 46, as by regulation of the variable speed motor. The speed of the motor need not be as great in a multiple cycle device, thus eliminating 4bearing wear and other adverse conditions in instances Where extremely high speed operation is required. It is interesting to observe that this result occurs without sacrifice of the total force of the impacts or blows imparted to a peen driving any given period of time, which total force remains substantially constant at both low and high speeds in both the single cycle and the multiple cycle embodiments and depends upon the air pressure and related conditions. The combination of wide range of speed variations and very high upper speed ranges without sacrifice of strength of impact make possible the accomplishment of mechanical operations not hitherto possible with impact mechanisms, such as riveting machines and spinning riveters.

While the preferred embodiments of the invention have been illustrated and described, it will 4be understood that changes in the construction may be made within the scope of the appended claims without departing from the spirit of the invention.

l claim:

l. A luid pressure actuated device comprising a housing having a chamber and intake and exhaust passages each communicating at its opposite ends with said chamber, an exhaust port adjacent to said exhaust passage, a pressure responsive member reciprocable in said chamber, a valve housing seated in one end of said chamber and having an inner end wall and a tubular side wall, said end wall having an aperture eccentric thereof and said tubular wall having ports communicating respectively with said intake and exhaust passages and with said exhaust port, said tubular wall intake port being spaced lengthwise from said remaining tubular wall ports, a valve element rotatable in said valve housing and having a iirst passage extending lengthwise therethrough and adapted to register with the end wall aperture of said valve housing in one rotative position, said valve element having a second passage extending from its outer end and adapted to register with said intake passage in a second rotative position and a third passage extending from its inner end and registering with the inner end wall aperture of said valve housing and said exhaust port in said second position, said valve element having a groove in its outer surface adapted to establish communication between said exhaust passage and exhaust port in another rotative position of said valve, means for supplying fluid under pressure into said housing at the outer end of said valve and into said iirst and second passages of said valve element, means for rotating said valve, and an impact member actuated `by said pressure responsive member.

2. A fluid pressure actuated device as defined in claim l, wherein said housing chamber is defined by a bore extending therethrough, end members mounted on the ends of said housing, the end member adjacent said valve 9 having a pair of openings, said valve rotating means including a rotatable member journaled in one opening and connected to said valve, said .second opening constituting part of said fluid supply means.

3. A uid pressure actuated device comprising a housing having a chamber and a plurality of passages each communicating at its opposite ends with said chamber, a pressure responsive member reciprocable in said chamber, said housing having a valve socket having spaced ports each communicating with one of said passages and ports communicating directly with said chamber and with a uid pressure outlet, respectively, a valve element rotatable in said socket, means for rotating said valve element, and means for supplying fluid under pressure to said housing for iiow therein under control of said valve, said valve having a plurality of fluid-directing means successively communicating with said socket ports upon rotation thereof to effect reciprocation of said pressure responsive member, and an impact member actuated by said pressure responsive member.

4. A uid pressure actuated device as defined in claim 3, wherein said iluid supply means and valve rotating means are located adjacent to one end of said housing and said valve socket is located between said fluid supply means and said housing chamber.

5. A fluid pressure actuated device comprising a housing having a chamber, a plurality of passages and an outlet, a piston reciprocable in said chamber, a valve rotatable in said housing and having a plurality of passages, means for rotating said valve, means for supplying fluid under pressure to said housing for ilow therein under control of said valve, the passages of said housing and valve cooperating to define a plurality of ow paths leading to opposite ends of said chamber and leading from opposite ends of said chamber to said outlet, said valve successively opening and closing said paths in a predetermined sequence to cause reciprocation of said piston, and impact means actuated by said piston.

6. A uid pressure actuated device comprising a housing having a chamber, a plurality of passages and an outlet, a piston reciprocable in said chamber, a valve rotatable'in said housing and having a plurality of passages,fmeans for rotating said valve, means for supplying uid under pressure to said housing for ow therein un- Ider control of said valve, the passages of said housing and valve cooperating to define a plurality of ow paths leading to opposite ends of said chamber and leading from opposite ends of said chamber to said outlet, said valve successively opening and closing said paths to cause a plurality of oscillations of said piston upon each revolution of said valve.

7. A iuid pressure actuated device comprising a housing having a chamber, a plurality of passages and an outlet, a piston reciprocable in said chamber, a valve rotatable in said housing and having a plurality of passages, means for rotating said valve, means for supplying uid under pressure to said housing for flow therein under control of said valve, the passages of said housing and valve cooperating to define a plurality of ow paths leading to opposite ends of said chamber and leading from opposite ends of said chamber to said outlet, said valve successively opening and closing said paths in a predetermined sequence to cause reciprocation of said piston, and impact means actuated by said piston, said housing having a valve receiving socket including a cylindrical wall and an end wall, said Valve constituting a cylindrical plug having a snug tit in said socket, at least one housing passage opening at each of said cylindrical and end Walls.

8. A uid pressure actuated device comprising a housing having a chamber, a plurality of passages and an outlet, a piston reciprocable in said chamber, a valve rotatable in said housing and having a plurality of passages, means for rotating said valve, means for supplying uid under pressure to said housing for ow therein under control of said valve, the passages of said housing and valve cooperating to define a plurality of flow paths leading to opposite ends of said chamber and leading from opposite ends of said chamber to said outlet, said valve successively opening and closing said paths in a predetermined sequence to cause reciprocation of said piston, and impact means actuated by said piston, said housing having a valve receiving socket including a cylindrical wall, said valve constituting a cylindrical plug, one of said passages and said outlet opening at said cylindrical Wall, said plug having a peripheral groove extending par tially therearound to establish communication between said last named passage and said outlet at selected rotative position of said plug.

9. A uid pressure actuated device comprising a housing having a chamber, a plurality of passages and an outlet, a piston reciprocable in said chamber, a valve rotatable in said housing and having a plurality of passages, means for rotating said valve, means for supplying uid under pressure to said housing for ow therein under`control of said valve, the passages of said housing and valve 4cooperating to define a plurality of flow paths leading to opposite ends of said chamber and leading from opposite ends of said chamber to said outlet, said valve successively opening and closing said paths in a predetermined sequence to cause reciprocation of said piston, and impact means actuated by said piston, said housing having a valve receiving socket including a cylindrical Wall and an end Wall, said valve constituting a cylindrical plug having a passage extending from end to end eccentrically thereof and adapted once in each revolution thereof to register with an eccentric housing passage located in said socket end wall.

l0. A uid pressure actuated device comprising a housing having a chamber, a plurality of passages and an outlet, a piston reciprooable in said chamber, a valve rotatable in said housing and having a plurality of passages, means for rotating said valve, means for supplying uid under pressure to said housing for ow therein under control of said valve, the passages of said housing and valve cooperating to dene a plurality of flow paths leading to opposite ends of said chamber and leading from opposite ends of said chamber to said outlet, said valve being located adjacent one end of said chamber, a transverse member separating said valve and chamber and having an aperture, said valve having passages alternately registering with the aperture of said transverse member and respectively communicating with said fluid supply means and with said outlet.

l1. A iluid pressure actuated device comprising a housing having a chamber, a plurality of passages and an outlet, a pistou reciprooable in said chamber, a valve rotatable in said housing and having a plurality of passages, means for rotating said valve, means for supplying fluid under pressure to said housing for flow therein under control of said valve,l the passages of said housing and valve cooperating to deiine a plurality of ow paths leading to opposite ends of said chamber and leading from opposite ends of said chamber to said outlet, said valve being located adjacent one end of said chamber, two longitudinal passages leading from said valve to the remote end of said chamber, said valve alternately opening said last named passages, one of said last named passages communicating with said iluid supply means when open and the other of said last named passages communicating with said outlet when open.

12. A uid pressure actuated device comprising a housing having a chamber, a plurality of passages and an outlet, a piston reciprocable in said chamber, a valve rotatable in said housing and having a plurality of passages, means for rotating said valve, means for supplying uid under pressure to said housing for ilow therein under control of said valve, the passages of said housing and valve cooperating to denne a plurality of flow paths leading to opposite ends of said chamber and leading from opposite ends of said chamber to said outlet, said housing passages including a plurality of spaced inlet passages leading to each end of said chamber, said valve having a uidV intake passage alternately communicating with inlet passages leading to opposite ends of said charnber.

13. A huid pressure actuated device comprising a housing having a chamber, a plurality of passages and an outlet, a piston reciprocable in said chamber, a valve rotatable in said housing and having a plurality of passages, means for rotating said valve, means for supplying fluid under pressure to said housing for iiow therein under control ot said valve, the passages of said housing and valve cooperating to define a plurality of flow paths leading to opposite ends of said chamber and leading from opposite ends of said chamber to said outlet, said housing passages including a plurality of spaced inlet passages leading to each end of said chamber, said valve having a fluid inlet passage alternately communicating with said inlet passages leading to opposite ends of said chamber, and a plurality of exhaust passages alternately connecting said outlet to opposite ends ot' said chamber.

14. A device as defined in claim 13, wherein said valve exhaust passages are arranged in equiangular relation.

15. A device as defined in claim 5, wherein said valve rotating means operate at variable speed and independently of said piston.

16. A device as defined in claim 5, wherein said valve rotating means is a variable speed motor, and a controller for regulating the speed of said motor.

17. A valve adapted to direct fluid flow alternately through different passages in diierent ow paths through a pressure actuated device to an exhaust outlet, comprising a valve housing seated in said device and having an end wall and a tubular side wall, said end wall having an aperture eccentric thereof and said tubular wall having ports respectively registering and communicating with said passages and with said exhaust outlet, one tubular wall port being an intake port and being spaced lengthwise and circumferentially from said other tubular wall ports, a valve element rotatable in said housing, said valve element having a passage extending lengthwise therethrough and adapted to register with said end wall aperture in one rotative position, a passage extending from the end thereof opposite said housing end wall and adapted to register with said intake port in a second rotative position, and a passage extending from the end thereof adjacent said housing end Wall and registering with the end wall aperture of said valve housing and with the tubular wall port communicating with said exhaust outlet in said second rotative position, said valve element having a groove in its peripheral surface adapted to establish communication between the tubular wall port registering with said exhaust outlet and one of said tubular wall ports spaced iengthwise from said intake wall port in another rotative position of said valve element, and means for subjecting to uid pressure the end of said valve element opposite said housing end wall.

18. A valve adapted to direct flow of fluid in a pressure actuated device having a housing with a chamber, a plurality of passages and an outlet, a valve member rotatable in said housing and having a plurality of passages, the passages of said housing and valve cooperating to dene a plurality of flow paths leading to opposite ends of said chamber and leading from opposite ends of said chamber to said outlet, and means for rotating said valve to successively open and close said paths at least twice during each revolution.

19. A valve adapted to direct how of uid in a pressure actuated device having housing with a chamber, a plurality of passages and an outlet, a valve socket having a tubular wall and an end wall, said tubular Wall having apertures communicating with said housing passages and said end wall having an eccentric aperture, a cylindrical valve plug rotatable in said socket and exposed to fluid under pressure, said plug having a plurality of passages cooperating with said socket apertures and said housing passages to detine a plurality of ow paths leading to opposite ends of said chamber and leading from opposite ends of said chamber to said outlet, and means for rotating said plug to successively open and close said ow paths.

References Cited in the tile of this patent UNITED STATES PATENTS 1,921,753 Holman Aug. 8, 1933 2,652,811 Beche Sept. 22, 1953 2,672,847 Bergmann Mar. 23, 1954 2,679,826 Leavell June 1, 1954