|Publication number||US3572216 A|
|Publication date||Mar 23, 1971|
|Filing date||Apr 23, 1969|
|Priority date||Apr 23, 1969|
|Publication number||US 3572216 A, US 3572216A, US-A-3572216, US3572216 A, US3572216A|
|Inventors||Donald W Seesody|
|Original Assignee||Applied Power Ind Inc|
|Export Citation||BiBTeX, EndNote, RefMan|
|Referenced by (53), Classifications (15)|
|External Links: USPTO, USPTO Assignment, Espacenet|
March 23, 11971 w, SEESODY 3,572,215
FLUID FORCE APPLYING DEVICE Filed April 23, 1969 A56 00 24 B4 Q /32 v M4 #4 W lNl/l/VTOR 0. M 5:53 00 MGM J Miran [y United States Patent O US. Cl. 9233 8 Claims ABSTRACT OF THE DISCLOSURE A work holding clamp in the nature of a self-contained hydraulic cylinder-piston unit in which one of the force applying members, for example the piston or ram, is rotatable and axially movable in its force-applying stroke.
BACKGROUND It has long been common practice to provide hydraulically actuated single or double acting cylinder-piston or ram devices for use in applying force in an axial direction in the accomplishment of diverse work. In some instances, the force application has been a pushing or spreading force, and in other instances, it has been a pulling force.
It has also been heretofore proposed to provide swingable clamping devices which utilize means such as a helical spline connection between relatively movable members for imparting rotation to the clamp carrier as it is moved axially, and it is not uncommon to utilize hydraulic power for actuating such clamping devices.
However, in all known instances, these swingable clamping devices have consisted of separate structures and have been entirely independent of the power or force applying devices used to actuate the same. Thus, the prior clamps and their attendant actuators have been undesirably bulky, and have moreover required the use of external mechanisms such as springs and/or the use of multiple hydraulic systems. Furthermore, the need for purchasing the swing clamp as a separate attachment resulted in added expense, and these attachments were rather restricted in their applications and use.
Also, in the prior swingable clamp structures, the splining between the relatively movable members has generally been such as to cause rotation of the clamp carrying member for the full axial movement thereof. Accordingly, the axial clamping forces imparted by the clamp throughout its effective stroke have heretofore been distorted and otherwise adversely affected by the accompanying rotational movement thereof, thus further increasing the frictional resistance to which the clamp is exposed.
SUMMARY OF THE INVENTION It is accordingly a primary object of the present invention to provide a force mechanism which obviates all of the aforesaid objections and disadvantages of prior devices of this general type.
Another object of this invention is to provide an improved force mechanism which indexes a given number of degrees in a circular arc and thereafter drives straight ahead solely in an axial direction.
Still another object of the invention is to provide an improved hydraulic force applying device which is entirely self-contained in an exceedingly compact and unitary package without need for any external springs or other external mechanisms and without using multiple hydraulic systems.
A further object of the present invention is to provide a force mechanism which is especially adaptable for use as a hydraulic swing clamp but which may be readily adapted for either pull or push types of linear actuation,
3,5722% Patented Mar. 23, 1971 single or double-acting types of hydraulic systems, use with clamping arms of diverse types and varying lengths, and use with hydraulic cylinder-piston devices having either a solid or a hollow piston.
Force applying devices embodying the present improvements comprise generally, a body having a central bore, a cylindrical guide member non-rotatably confined within the bore of said body and having a cam slot formed in the cylindrical exterior thereof, a piston having a portion slidably confined within the bore of said body and having a bore slidably received by the cylindrical guide member, a cam follower carried by the piston and operable in the cam slot of the guide member to guide the piston in its movement, and means for axially displacing the piston along the bore of said body.
These and other objects and advantages of the invention will become apparent from the following detailed description.
THE DRAWINGS A clear conception of the several features of the present invention and of the mode of constructing and of operating a typical swing clamp embodying the improvements may be had by referring to the drawings accompanying and forming a part of this specification wherein like reference characters designate the same or similar parts in the several views.
FIG. 1 is a central longitudinal section through a typical swing clamp having a single acting hydraulic ram and embodying the features of the present invention, the piston and clamp being shown in fully extended position;
FIG. 2 is a similar section through the device of FIG. 1 but showing the piston and clamp in indexed and clamping position;
FIG. 3 is a central longitudinal section through another embodiment of a swing clamp wherein the ram is of the double acting hydraulic type and the guide member is hollow, the piston and clamp again being shown in fully extended position; and
FIG. 4 is a plan view of the swing clamp with the clamping arm being shown as swung to indexed and clamping position by means of broken lines.
DETAILED DESCRIPTION While the invention has been shown and described herein as being embodied in a swing clamp of a particular construction wherein the clamping element is indexed in a circular arc and then is driven straight downwardly in its clamping stroke, it is not intended or d sired to unnecessarily restrict or limit the invention by reason of such specific embodiments since the improvements may be used to advantage in other types of force applying devices which include a reciprocating piston and in which advantages may be obtained by rotating the piston during its movement. It is also contemplated that certain descriptive terms used herein shall be given the broadest possible interpretation consistent with the disclosure.
Referring to FIGS. 1 and 2 of the drawings, the typical force applying device shown therein as embodying the invention comprises generally a body 10 formed with a central bore 12 slidably receiving the enlarged portion 16 of a piston 14.
The body 10 is provided with a radial port 18 entering the bore 12 on one side of the portion 16 f the piston, the port 18 being formed in a customary manner to receive an inlet fitting adapted to be connected t a suitable source of supply of pressurized hydraulic fluid so that hydraulic fluid under pressure may be Selectively supplied to the bore 12 to forcibly axially displace the piston within the bore of the body 10. The portion 16 of the piston 14 is also provided with the usual annular groove and seal 20, and the reduced portion of the piston 14 is embraced in the usual manner by a suitable sealing ring 22 confined within an annular groove at the end of the bore 12 of the body 10.
In the embodiment shown in FIGS. 1 and 2, the piston 14 is displaced axially downwardly by fluid under pressure supplied through the port 18, and a coil spring 24 compressed between the underside of the piston portion 16 and the base 26 of the body serves to return the piston to its extended position upon release of pressurized fluid to the upper portion of the bore 12. It is also preferable to place the spring 24 in torsion during movement of the piston and compression of the spring, for accomplishing this purpose, the upper end of the spring is suitably attached as at 28 to the piston portion 16 and the lower end of the spring 24 is attached as at 30 to the base 26.
The base 26 may be suitably secured to the end of the body 10 as by means of an annular series of machine screws 32 or the like, and the hydraulic force applying device is thus of unitary structure and is entirely selfcontained.
In accordance with the present invention, provision is made for causing rotation or indexing of the piston 14 during its axial movement, such rotation of the piston serving to swing a clamping arm 34 or the like secured to the outer extending end of the piston 14 as by means of a bolt 36 through a desired number of degrees shown in the present instance as 90. Thus, the clamping arm 34 which may be provided with a work engaging saddle 38 or the like is swung out of the way of the work upon extension of the piston 14 with the clamp being swung into working engagement upon power movement of the piston.
To perform the indexing operation, a cylindrical guide member or post 42 is non-rotatably confined within the bore 12 of the body 10, the post 42 being shown as secured at one end within a central aperture 44 of the base 26 as by means of a pin or pins 46. The cylindrical exterior of the guide member 42 is formed with a cam slot 48 of a configuration such as will give the desired indexing to the piston 14 as will hereinafter become apparent.
The piston 14 is formed with a central bore 52 slidably received by the inner end of the guide member 42, and a cam follower 54 is carried by the piston 14 so as to be operable in and along the cam slot 48 of the guide member 42 to guide the piston 14 in its movement. As shown, the cam follower 54 may conveniently comprise a ball seated within a detent 56 formed in the bore 52 of the piston 14.
In the embodiment shown, the piston 14 is moved downwardly upon introduction of fluid under pressure via port 18 to the displacement chamber formed by the bore 12, and as it moves downwardly, the piston simultaneously indexes in a circular motion to move it through a 90 arc by reason of the ball 54 which operates in the cam groove 48. At the end of the 90 index or such other degree of are as might be desired, the piston will be caused to move in a straight line as the ball 54 follows the straight portion 58 of the cam groove. Thus, during the first portion of its travel, the clamping arm 34 is swung from an inactive out-of-the-way position to a position wherein it is aligned with the work, and during the straight terminal portion of its movement, a clamping force is provided which is not in any way distorted or otherwise adversely affected by torsional strains. After the clamping operation is completed and the hydraulic pressure is released from the upper end of the pressure chamber, the piston is free to move upwardly and such movement is provided in the embodiment of FIGS. 1 and 2 by the compression spring 24. During its return stroke, the piston 14 obviously initially moves in a straight upward path and subsequently indexes in an are as provided by the cam 48 back to its starting position whereby the clamp 34 is out of the way of the work to permit unobstructed access to the work.
Referring now to FIG. 3, the force applying device shown therein is essentially the same as that shown in FIG. 1 except that hydraulic pressure is used for actuating the ram in both directions and the guide member is formed hollow for the reception of suitable implements. However, the device still includes a body formed with a central bore 112 which slidably receives the enlarged portion 116 of the piston 114.
The body 110 is again provided with a radial port 118 entering the bore 112 about the portion 116 of the piston, and the usual seals 120 and 122 are again provided for sealing between the piston and the body.
However, instead of the spring for returning the piston to extended position, the body 110 is formed with a second radial port 124 communicating with the lower portion of the chamber formed by the bore 112 below the enlarged portion 116 of the piston. Thus, the piston is extended by introducing pressurized fluid via port 124 to the lower portion of the chamber 112, and the piston is moved axially downwardly toward clamping position by exhausting fluid from port 124 and admitting pressurized fluid through port 118 to the chamber 112 above the piston portion 116.
In the device of FIG. 3, the base 126 may again be suitably secured to the end of the body 110 as by means of an annular series of machine screws 132 or the like, and an annular seal is preferably provided for sealing between the end of the body 110 and the base 126. Also, since the device of FIG. 3 is fully pressurized for actuation of the piston in both directions, it is preferable to provide a seal 128 between the bore 152 of the piston and the exterior of the guide member 142.
The piston 114 of the device shown in FIG. 3 is again rotatable during a portion of its axial movement, and the extending end thereof may be provided with a suitable clamping arm 134 as hereinabove described with reference to FIGS. 1 and 2. The clamping arm 134 may be suitably secured as by means of a bolt 136 to the end of the piston, and the extending end of this arm may be provided with a suitable work-engaging saddle 138 or the like, Once again, the indexing operation is performed by means of a cylindrical guide member 142 non-rotatably confined within the bore 112, and in this instance, the guide member 142 is shown as being in the nature of a tube or hollow cylindrical member which may be suitably adapted to receive any desired implement. The tubular guide member 142 is again preferably secured within a central aperture 144 of the base 126 as by means of pins 146, and the cylindrical external surface of the member 142 is formed with a cam slot 148 of desired configuration.
The piston 114 is formed with a bore 152 slidably received by the end of the guide member 142 and a cam follower 154 is seated within a detent 156 formed in the bore of the piston 114. A convenient cam follower is again shown as being in the nature of a ball seated within the detent 156, the ball being operable in and along the cam slot 148 as hereinabove described, the arcuate portion 148 of the cam slot terminating in a straight portion 158 so that the clamp will follow a straight line path after indexing in an arcuate path for performance of the clamping action.
1. A work holding swing clamp comprising a body having a central bore,
a cylindrical guide member fixed within the bore of said body, said member having a cam slot therein including an arcuate portion and a straight terminal portion,
a piston assembly having a first portion slideably confined within the bore of said body and also having a second portion extending outwardly of said body in slideable and sealable contact therewith,
a clamp arun secured to said outwardly extending portion,
a cam follower carried by said piston assembly and 0perable in said cam slot of said guide member to impart a rotary motion to said piston assembly on movement of said cam follower through said arcuate portion of said cam slot and axial motion to said piston assembly on movement of said cam follower through said straight terminal portion of said cam slot, and
means for axially displacing said piston assembly along the bore of said body.
2. The clamp according to claim 1 wherein the cam follower includes a ball element confined partially within a detent formed in said piston assembly.
3. The clamp according to claim 1 wherein said means for axially displacing said piston assembly along the bore of said body includes a pressurized fluid acting on said piston assembly in one direction and a spring acting on said piston assembly in the opposite direction.
4. The clamp according to claim 1 wherein said means for axially displacing said piston assembly in both directions includes a pressurized fluid admitted selectively to opposite sides thereof.
5. The clamp according to claim 1 wherein said cylindrical guide member is a hollow, open-ended tube.
6. The clamp according to claim 1 wherein said body is provided with a base and said cylindrical guide member extends through an aperture in the base and centrally into said bore of said body.
7. The clamp according to claim 1 wherein said piston assembly has a bore therein slideably received by said cylindrical guide member.
8. A work holding swing clamp comprising a body having a central bore,
a hollow open ended guide member fixed within the bore of said body, said member member having a cam slot therein including an arcuate portion and a straight terminal portion,
a piston assembly having a first portion slideably confined Within the bore of said body and a second portion extending outwardly of said body in slideable and scalable contact therewith,
a clamp arm secured to said outwardly extending second portion,
a cam follower carried by said piston assembly and operable in said cam slot of said guide member to impart a rotary motion to said piston assembly on movement of said cam follower through said arcuate portion of said cam slot and axial motion to said piston assembly on movement of said cam follower through said straight terminal portion of said cam slot, and
means for admitting a pressurized fluid selectively to opposite sides of said piston assembly to axially displace said piston assembly along the bore of said body.
References Cited UNITED STATES PATENTS 1,602,209 10/1926 Proell 92-31X 2,752,801 7/1956 Olson 269-93X 3,339,463 9/1967 Updegrave 92-31 3,457,838 7/1969 Rowe 92-33 2,117,225 5/ 1938 Stein 92-33 2,806,450 9/1957 Geyer 92-33 2,883,144 4/1959 Kendig 92-33X 2,938,399 5/1960 Briggs 92-33X 3,046,802 7/1962 Cupedo 92-31X 3,207,468 9/1965 Lauducci et al 92-31X 3,218,937 11/1965 Dettlof 92-33X 3,255,806 6/1966 Meyer et a1 92-33X 3,397,879 8/1968 Morawski et a1 269-91 3,450,382 6/1969 Calim 92-31 3,453,938 7/ 1969 Fewel 92-33 FOREIGN PATENTS 47,661 Germany 92-33 221,843 5/1910 Germany 92-33 290,306 9/1913 Germany 92-33 MARTIN P. SCHWADRON, Primary Examiner L. I. PAYNE, Assistant Examiner U.S. Cl. X.R. 74-55; 269-91
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|U.S. Classification||92/33, 269/32, 74/55, 269/91|
|International Classification||B25B5/06, B23Q3/06, B23Q3/08, F15B15/06|
|Cooperative Classification||B25B5/062, B23Q3/08, F15B15/063, B23Q2703/04|
|European Classification||B23Q3/08, F15B15/06C, B25B5/06B1|