US3475946A

US3475946A - Pressing tool,specifically hand press

Info

Publication number: US3475946A
Application number: US444098A
Authority: US
Inventors: Friedrich Gunther Laux
Original assignee: LAUX FRIEDRICH G
Current assignee: LAUX FRIEDRICH G
Priority date: 1963-12-13
Filing date: 1965-03-22
Publication date: 1969-11-04
Anticipated expiration: 1986-11-04
Also published as: GB1090024A; DE1465912A1; DE1465916A1; DE1465916B2; DE1465912B2; DE1465877A1; DE1465877B2

Description

Nov. 4, 1969 F. G. LAUX PRESSURE TOOL, SPECIFICALLY HAND PRESS 2 Sheets-Sheet F'iled March 22. 1965 INVENTOR M M M R m w W EEE 5: E:

FIG. 4

United States Patent 3,475,946 PRESSING TOOL, SPECIFICALLY HAND PRESS Friedrich Giinther Laux, 301 Konigsweg, 1 Berlin 39, Germany Filed Mar. 22, 1965, Ser. No. 444,098 Claims priority, appliclation Ggrmany, June 12, 1964,

Int. (:1. B21d 9/08 US. Cl. 72-409 7 Claims ABSTRACT OF THE DISCLOSURE This invention relates, in general, to tools for compressing articles such as electrical connectors, and more particularly relates to such tools having advantageous force-multiplying and actuating features.

One feature of this invention pertains to the provision, in a compression tool, of a rotary eccentric linkage which is driven by a fluid pressure-actuated rack moved along a substantially linear path.

Another feature of this invention pertains to the provision, in a tool such as is described above, of a fluid pressure piston assembly which is pivotally coupled relative to an eccentric linkage so as to serve as a manual actuating handle for the linkage.

An advantage of the features described above is a resultant mechanical advantage which is significantly higher than that generally obtained by prior art tools of related types.

These and other and further features, advantages, and new results of this invention will be more clearly illustrated, specifically pointed out, and fully claimed in the following specification and claims, and in the appended drawings, in which:

FIG. 1 is a side elevation view of a compression tool constructed in accordance with this invention;

FIG. 2 is a partially sectioned side elevation View of the tool of FIG. 1;

FIG. 3 is a section view taken along the line XIXI of FIG. 2; and

FIG. 4 is a partial section view taken along the line XIIXII of FIG. 2.

Referring now more particularly to the drawings, it may be seen that the illustrated tool comprises, generally, a body formed by a pair of side plates 91, a pair of

handles

102, 103 coupled to the body, and a pair of opposed die members 5, 6 mounted between the plates 91.

A pair of parallel grooves 3, 4 are formed in the side pieces 91, to receive die members 5 and 6 in sliding relationship. At one end of grooves 3, 4, die member 6 abuts against a movable thrust-bolt 18, and at the other end of the grooves, a stop-bolt 9 is provided to engage die member 5 so as to capture the dies within the tool. The stop bolt 9 is formed with a knob 12 at one end to facilitate insertion and withdrawal of the bolt in bores 10, 11 in order to permit changing of the die members. An annular groove 13 or equivalent detent means may be provided on the bolt 9 to coact with side plates 91 or bores 10, 11, for retention purposes. And, a torsion spring element 50 is coupled to die members 5, 6 at its opposite ends 58, 59, to act as a spacer for biasing the Patented Nov. 4, 1969 die members into spaced-apart relationship within the tool. In use, the biasing eifect of spring element 50 is overcome by force transmitted to die member 6 from movable thrust-bolt 18; movable die member 6 is thus advanced toward fixed die member 5 so as to compress an article between the opposed working faces 54, 55 of the die members.

The movable thrust-bolt 18 which advances die member 6 toward die member 5, is controlled by a drive assembly comprising: pressure transfer members 20, eccentric pivot journals 21, toothed pinion wheel 71, toothed rack member 72, and handle 103 which includes piston and cylinder 76. In brief, the operation of this assembly relies upon the toothed rack 72 to convert linear motion into rotary motion of pinion wheel 71 about the pinion journal 23; the rotary motion of pinion wheel 71 is then translated into linear motion of thrust bolt 18 by means of pressure transfer members 20, which are coupled to eccentric pivot journals 21. The pivot journals 21 are directly coupled to pinion wheel 71 for rotation about pinion journal 23, but are eccentric with respect to the central axis of journal 71 so as to achieve the desired linear displacement of thrust-bolt 18 at wheel 71 rotates. The thrust-bolt 18 is provided with shaped end portions 19 which fit within guide grooves 3, 4, so as to assure linear displacement of the bolt in line with die member 6. This power transmission train provides a high mechanical advantage which results in die member 6 being urged toward die member 5 with a substantially higher force than might be obtained through direct force take-01f from a manual or fluid pressure input force alone.

For various reasons, operation of this tool often will require rack member 72 to advance, withdraw, and advance again, while rotating pinion wheel 71 in one direction only. In order to permit this mode of operation to occur, toothed rack 72 is pivotally coupled to the end of piston 75 so that it may swing into or out of engagement with the teeth of pinion wheel 71, and a holding pawl 132 is provided on the body of the tool for preventing rotation of wheel 71 in a clockwise direction (as seen in FIG. 2). Pawl 132 is pivotally mounted to side plates 91 by means of a peg 133, and is provided with a compression spring 134 to bias the tip of the pawl into engagement with the teeth on pinion wheel 71. The pawl is further provided with a knurled extension lever 135, which may be manually depressed to disengage the pawl from the pinion Wheel 71 for rapid positioning of dies 5, 6. Such rapid positioning may be accomplished, conveniently, through use of key bar 70 which is coupled to the end of pinion journal 23 for manual rotation of pinion wheel 71. Toothed rack 72 pivots about peg 73 on a fork extension 74 at the end of piston 75, and a tension spring 128, anchored at its opposite ends to a projection 127 on rack 71, and to fork 74, serves to bias rack 72 into engagement with pinion wheel 71 in the direction shown by arrow 129.

The

handles

102, 103 which are coupled to the body of this tool, comprise a substantially fixed handle 102, and a movable handle 103, respectively. The fixed handle 102, which is employed for supporting and positioning the tool, comprises a base 98 which is secured to the side plates 91 by means of pegs 99. A threaded bore 100 within base 98, receives a mating threaded extension 101 on the handle 102, to facilitate removal and reattachment.

Movable handle 103 serves a dual function: in one capacity it is a housing for cylinder 76 and piston 75 which actuate the tool in response to fluid pressure supplied from a fluid pressure source (not shown); in a second capacity, the handle may be manually pivoted relative to the body of the tool so as to produce rotation of pinion wheel 71 independently of fluid pressure in cylinder 76. Handle 103 comprises: a tubular base 87 which is pivotally coupled to side plates 91 by means of projecting journals 88; cylinder body 76; and tubular connector 111 which provides means for introducing pressurized fluid into cylinder 76. As shown most clearly in FIG. 3, projecting journals 88, covered by caps 89, are fitted within mounting holes 90 in side plates 91, so that the caps 89 serve as anti-friction bearings between the journals 88 and the holes 90.

When the tool is to be used with fluid pressure actuation only, handle 103 is locked against rotation about journals 88 by means of locking peg 93. FIGURES 3 and 4 illustrate operation of this locking peg most clearly. As shown in FIG. 3, the peg extends through bores in side plates 91, and is provided at one end with a retention ring 94, and at the other end with a knob 92 which enables an operator to rotate the peg, manually, about its own axis. A retention plunger 95, located within a bore in knob 92, is biased against a dimple 97 in side plate 91 by means of a compression spring 96, in order to retain the peg 93 in a desired rotary position. The outer cylindrical surface of peg 93 cooperates with a mating groove 125 formed in tubular base 87 of handle 103 to prevent pivotting of the base 87 about journals 88. Along the length of peg 93, a portion of the cylindrical surface is cut away to form a recess 124. When it is desired to free handle 103 for pivotal motion about journals 88, the peg 93 is rotated by means of knob 92 until recess 124 is located in substantially opposed relation to groove 125. The surface of peg 93 is then fully disengaged from groove 125 and tubular base 87 may be pivoted freely on journals 88.

When handle 103 has been freed for pivotal motion about journals 88, manual operation of this compression tool may be achieved by alternately swinging handle 103 toward and away from handle 102. FIG. 2 illustrates clearly that the central axes of pivot peg 73 for rack 74, and of pivot journals 88 for handle 103, are offset from one another by an amount, e, as shown in FIG. 4. As a result of this offset, or eccentricity, pivotal motion of handle 103 causes toothed rack 72 to advance along a substantially linear path relative to pinion wheel 71, thereby producing rotation of the pinion wheel. For example, as shown in FIG. 2, counter-clockwise rotation of handle 103 toward handle 102 from the position shown, will displace rack member 72 toward the right, and will cause counter clockwise rotation of pinion wheel 71. As handle 103 is returned in a clockwise direction, to the position shown in FIG. 3, holding-pawl 132 will prevent pinion wheel 71 from rotating in a clockwise direction, and bias spring 128, acting on rack member 74, will permit the teeth on the rack to disengage successively from the teeth on the pinion wheel to achieve sliding relative motion between the rack and wheel.

To achieve fluid pressure operation of this compression tool, handle 103 is locked in the position shown in FIG. 2 by means of locking peg 93, and fluid under pressure is introduced into hose 105. The hose is secured to a sleeve 108 by a screw collar 104 which has internal threads 113 which engage external threads on sleeve 108. This sleeve is coupled, in turn, by

threads

110, 119 to cylinder 76. Screw collar 104 is actually coupled to the end of a further connector member 106 which is connected, in turn, to the end of hose 105. An O-ring seal 109 is positioned between the members 106 and 108.

The member 106 carries a spring ring 123 to retain the screw collar 104 on the end of the member 106. The end of the member 106 is formed with an annular rim 122 to prevent the screw collar 104 from being pulled off the end of member 106.

The members 106 and 108 incorporate ball valves, which are adapted to open when the two members 106 and 108 are connected so as to allow pressurized fluid to be applied to the piston 75, and which are adapted further to close when the two members 106 and 108 are 4 disconnected, thus preventing leakage of fluid from either the hose or the cylinder 76.

The member 106 has a tubular extension 107 which houses a ball valve 114. The ball 114 can either abut a seat 116 to prevent liquid from passing out of the member 106 or abut a seat 112 to allow the liquid to pass out of the member 106. The ball 114 is urged towards the seat 116 by a spring 115.

Similarly, the member 108 houses a ball 117 which can either abut a seat 121 or a seat 118, and is urged towards the seat 121 by a spring 120.

Connection of the two members 106 and 108 causes the

balls

114 and 117 to be displaced by each other from their seats 116 and 121 respectively, against the action of the springs and respectively, so as to allow pressurized hydraulic liquid to be applied to the piston 75. When the two members 106 and 108 are disconnected, the

balls

114 and 117 are urged back against the seats 116 and 121, respectively, by the

springs

115 and 120, respectively, to prevent any loss of hydraulic liquid from the hose 105 or cylinder 76. Hydraulic operation of this tool thus may be accomplished by successfully reciprocating piston 75 within cylinder 76 until rack 72 has produced the desired rotation of pinion wheel 71.

To achieve the desired mode of operation for piston 75, a compression coil spring 79 is mounted on a stem 78 secured to the cylinder 76. The stem 78 has a head 80 at its free end against which one end of the spring 79 abuts, the other end of the spring abutting against a retaining ring 81 carried by the piston 75. The spring 79 thus urges the piston 75 to the left, as viewed in FIG. 2. The is an O-ring seal 77 between the piston 75 and the cylinretaining ring 81 is held in position by a spring ring 82. There is an O-ring seal 77 between the piston 75 and the cylinder 76.

A tubular connector member 111, including a sleeve 83, is threaded onto the free end of cylinder 76. A seal 84 is positioned between the sleeve 83 and the cylinder, and a limit ring 85 is carried by the piston 75 against a shoulder 86 in the piston. As the piston 75 moves toward the right, the limit ring 85 travels along a recess 131 in the cylinder 76 until it abuts against a shoulder formed at one end of the recess 131. The travel of the piston 75 is thus limited.

It has previously been mentioned in this specification that pinion wheel 71 may be rotated conveniently, without use of handle 103 or fluid pressure, by means of a key handle 70 coupled to pinion journal 23. However, as a result of the interaction of pawl 132 and rack 72 with the teeth on pinion wheel 71, a manual rotation of the pinion wheel by means of key handle 70 will normally be limited to a counter-clockwise direction (as seen in FIG. 2), only. It is a further feature of this invention that release means are provided to permit pinion wheel 71 to be rotated freely about its axis in either direction: Holding pawl 132 may be disengaged conveniently, as previously described, by manually depressing extension lever portion 135 to overcome the biasing action of spring 134. Rack 72 may be disengaged, also, from the pinion wheel 71 by moving handle 103 beyond the position shown in FIG. 2 in a clockwise direction as indicated by arrow 126. Free rotation of pinion wheel 71 is of particular advantage for rapidly positioning the die merlnbers 5, 6 to engage or release an article within the too The invention has thus been described, but it is desired to be understood that it is not confined to the particular rms or usages shown and defined, the same being merely illustrative, and that the invention may be carried out in other ways without departing from the spirit of the invention; therefore, the right is broadly claimed to employ all equivalent instrumentalities coming within the scope of the appendant claims, and by means of which objects of this invention are attained and new results accomplished, as it is obvious that the particular embodiments herein shown and described are only some of the many that can be employed to obtain these objects and accomplish these results.

What is claimed is:

1. A compression tool capable of producing a mechanical advantage on the order of 1:600, for compressing articles between a pair of dies, comprising:

a body;

a toothed pinion wheel rotatably mounted to said body;

a fixed die coupled to said body;

a movable die coupled to said body;

an eccentric linkage coupling said toothed pinion wheel to said movable die for moving said movable die relative to said fixed die upon rotation of said pinion wheel;

a toothed rack member having teeth operatively engaging said pinion wheel for rotating said pinion Wheel in response to displacement of said toothed rack; and actuating means coupled to said body and to said toothed rack for displacing said rack relative to said body.

2. A compression tool in accordance with claim 1 wherein said e'ccentric linkage coupling said pinion wheel to said movable die comprises:

a pivot journal mounted to said pinion wheel and having a central axis which is eccentric with respect to the central axis of said pinion wheel;

a thrust bolt movably coupled to said body for relative motion in line with said movable die; and a pressure transfer member coupled to said thrust bolt and to said pivot journal.

3. A comparison tool in accordance with claim 1 wherein said actuating means comprises a movable handle which is pivotally coupled to said body at a first pivot axis and is pivotally coupled to said toothed rack at a second pivot axis which is eccentric with respect to said first pivot axis.

4. A compression tool in accordance with claim 1 wherein said actuating means comprises a fluid-pressure actuated piston assembly having a piston and cylinder which are displaceable relative to one another and are coupled between said body and said toothed rack for displacing said rack relative to said body.

5. A compression tool in accordance with claim 4 wherein said fluid-pressure actuated piston assembly is mounted as a movable handle which is pivotally coupled to said body at a first pivot axis, and is pivotally coupled to said toothed rack at a second pivot axis being eccentric with respect to said first pivot axis; said further comprising releasable locking means coating with said piston assembly to prevent pivotal motion of said piston assembly as a movable handle.

6. A compression tool in accordance with claim 4 wherein said eccentric linkage coupling said pinion wheel to said movable die comprises: a pivot journal mounted to said pinion wheel and having a central axis which is eccentric with respect to the central axis of said pinion wheel; a thrust bolt movably coupled to said body for relative motion in line with said movable die; and a pressure transfer member coupled to said thrust bolt and to said pivot journal.

7. A compression tool in accordance with claim 6 wherein said tool further comprises releaseable detent means for limiting motion of said pinion Wheel to rotation in one direction only.

References Cited UNITED STATES PATENTS 2,705,432 4/1955 Lazar 72409 2,861,490 11/1958 Rozrnos 72449 3,342,059 9/1967 Laux 72410 2,494,963 1/ 1950 Ray 72409 X 2,587,096 2/1952 Berger 72410 X 2,688,231 9/1954 Northcutt 72409 X 2,696,850 12/1954 Peterson 72409 2,931,260 4/ 1960 Townshend 72409 FOREIGN PATENTS 737,152 9/ 1955 Great Britain.

891,454 3/ 1962 Great Britain. 1,341,705 9/1962 France.

CHARLES W. LANHAM, Primary Examiner E. SUTTON, Assistant Examiner US. Cl. X.R. 72453