US3747441A

US3747441A - Pneumatic tool having combined nut running and crimping mechanism

Info

Publication number: US3747441A
Application number: US00121867A
Authority: US
Inventors: L Amtsberg; W Wallace
Original assignee: Chicago Pneumatic Tool Co LLC
Current assignee: Chicago Pneumatic Tool Co LLC
Priority date: 1971-03-08
Filing date: 1971-03-08
Publication date: 1973-07-24
Anticipated expiration: 1990-07-24
Also published as: DE2210789A1; IT954325B; CA955085A; GB1375103A; BE780316A; NL7203019A; GB1375104A; DE2210789C2; SE398313B; FR2129466A5; GB1375102A

Abstract

A nut running tool in which is combined nut running and nut crimping mechanism. The tool is operative to crimp all six sides of a standard hexagonal nut. A reversible rotary air motor drivingly connected with the mechanism is operable in one direction to cause the mechanism to drive the nut to a predetermined tightness, and is operable in an opposite direction to cause the mechanism to crimp the nut. In one embodiment, control means is selectively operable to determine the direction of rotation of the motor. In a second embodiment, control means is provided which is operable without further intervention of the operator to cause the mechanism to run through a first stage to set the nut, then responds automatically to setting of the nut to cause the mechanism to crimp the nut, and finally responds to the latter action to restore the tool to its normal condition.

Description

United States Patent [1 1 Amtsberg et a1.

[ 1 July 24, 1973 PNEUMATIC TOOL HAVING COMBINED NUT RUNNING AND CRIMPING MECHANISM [75] lnventors: Lester A. Amtsberg, Utica; William K. Wallace, Bameveld, both of N.Y.

[73] Assignee: Chicago Pneumatic Tool Company, New York, N.Y.

221 Filed: Mar. 8, 1971 21 Appl. No.: 121,867

[52] U.S. Cl 81/10, 72/453, 10/155 R [51] Int. Cl B25b 27/00 [58] Field of Search 81/10; 72/453, 452, 72/391; 29/200 B, 211 D; 10/155 R [56] 7 References Cited UNITED STATES PATENTS 3,689,951 9/1972 Van Hecke et a1 81/10 3,646,837 3/1972 Reynolds 81/10 3,603,132 9/1971 Holmes.... 81/55 3,479,714 11/1969 Allsop 81/3 Primary Examiner-James L. Jones, Jr. Attorney-Stephen J. Rudy [57] ABSTRACT A nut running tool in which is combined nut running and nut crimping mechanism. The tool is operative to crimp all six sides of a standard hexagonal nut. A reversible rotary air motor drivingly connected with the mechanism is operable in one direction to cause the mechanism to drive the nut to a predetermined tightness, and is operable in an opposite direction to cause the mechanism to crimp the nut.

In one embodiment, control means is selectively operable to determine the direction of rotation of the motor.

In a second embodiment, control means is provided which is operable without further intervention of the operator to cause the mechanism to run through a first stage to'set the nut, then responds automatically to setting of the nut to cause the mechanism to crimp the nut, and finally responds to the latter action to restore the tool to its normal condition.

12 Claims, 17 Drawing Figures PNEUMATIC TOOL HAVING COMBINED NUT RUNNING AND CRIMPING MECHANISM BACKGROUND OF THE INVENTION This invention is concerned with a pneumatically powered nut runner having crimping mechanism incorporated therein.

A nut runner including nut crimping mechanism is known from U.S. Pat. No. 3,003,378. This known tool is of a hand powered type and resorts to an impacting action to effect crimping of the work.

The general objective of the present invention is to provide a fluid power operated nut runner with mechanism for crimping by means of a squeeze action on all six sides of a standard nut after it has been tightened upon a stud to the required torque. The crimping effect on the nut is of advantage in that it distorts its internal threads so as to lock it to the stud and make its removal difficult. A crimped nut upon a stud is particularly desirable in situations where the article carrying the nut will be subject to continual shocks and vibration which might otherwise tend to loosen the nut from the stud.

Incorporation of the crimping mechanism in the tool is of advantage in that it avoids the necessity of resorting to separate and independent tools to effect the crimping action; and results in a tool of compact nature which is practical and efficient for the operations involved.

A feature of the invention isa combined mechanism in a nut running tool for effecting both the nut running and crimping actions. As will be apparent hereinafter, one embodiment of the tool can be operated selectively to provide only nut runup, or only nut runup-followed by crimping of the runup nut, or only crimping of a nut which has been runup by another tool.

Another feature of the invention lies in a rotatable.

member carrying a group of pivotable jaw elements which provide two distinctive operational functions, namely, to run up a standard hexagonal nut upon a bolt to predetermined seated condition, and subsequently to crimp all sides of the nut into tight engagement with the bolt.

Another feature lies in the association of a wedge with the pivotable jaw elements, the wedge being movable axially of the jaw elements with a camming action against tail ends of the jaw elements so as to force lower jaw face portions angularly in the crimping action to penetrate the work nut. This arrangement provides a desirable mechanical advantage and other benefits in the crimping action which are not obtainable by the mechanism known from U.S. Pat. No. 3,003,378; nor from U.S. Pat. No. 3,421,562. In the latter patent, a female member is slidable over jaw elements to effect a crimping action on a work nut.

A characteristic of each jaw element is a flat planar face at its lower inner end area which defines the jaw. This jaw face serves to contribute to an effective nut engagement area to achieve desired nut runup and also is ccoperuble in a crimping action angularly with a flat side of the work nut so as to compressively displace a triangular volume of metal. This structural arrangement is of decided advantage in that it does not allow the jaw to become locked or bound to the nut in the crimping action; and the jaw may accordingly be readily released.

Another feature of the combined nut running and crimping mechanism is that it is coupled to the motor so as to be responsive to rotation of the motor in one direction to run down the work and responsive to rotation of the motor in an opposite direction to crimp the work.

Another feature of the invention is manually operable air flow control mechanism which permits selective rotation of the motor in one direction or the other.

In a modified or automatically operating form of the invention, an air flow control system is provided which is initially actuable to cause run down of the work to a predetermined degree of tightness; responds automatically to a predetermined tightening of the work to cause crimping of the work; and responds to termination of the latter action to shut off air flow to the motor and to restore the tool to its normal condition,

BRIEF DESCRIPTION OF THE DRAWING In the accompanying drawing:

FIG. 1 is a sectional view of a nut runner embodying the invention;

FIG. 2 is a section on line 22 of FIG. 1;

FIG. 3 is a section on line 3-3 of FIG. 1;

FIG. 4 is a section on line 4-4 of FIG. 1;

FIG. 5 is a detail view of the travel wedge;

FIG. 6 is a bottom end view of FIG. 5;

FIG. 7 is a detail showing the normal or open position of a jaw element allowing reception of a work nut;

FIG. 8 is a detail showing the jaw element pivoted in crimping relation to the work nut;

FIG. 8a is an elevational view of the inner face of the element in FIG. 8b;

FIG. 8b is a detail in side elevation of a jaw element;

FIG. 9 shows the handle of the tool as modified with a valve system allowing the tool to pass automatically through a complete cycle of operation in which a nut is set and crimped; and

FIGS. 10-15 are sectional views taken respectively on the lines l0l0; ll-ll; 12--l2; 1313;'l414; and 15-15 of FIG. 9.

DESCRIPTION OF PREFERRED EMBODIMENT Reference is directed to the accompanying drawings, and now especially to FIGS. 1-8b, wherein is shown a pneumatically powered tool having a general housing 10 which includes an angle head section 11 detachably coupled, as by a threaded connection 12, with the front end of the housing. Supported in the housing is a conventional air driven reversible motor 13 of a radially slidable vane type. An inlet passage 14 to the tool is connectible to an external source of air having a constant pressure. A throttle valve 15 is manually operable to feed inlet air to a passage 16. A manually operable reversing valve 17 in passage 16 normally directs the air flow to one area of the motor chamber to cause forward or clockwise rotation of the motor. In an actuated position, the reversing valve directs air flow to a reverse area of the motor chamber to cause reverse or counterclockwise rotation of the motor.

Rotation of the motor is transmitted through conventional reduction gearing, generally indicated at 18, and

through a splined driving connection 19 to a spindle 21. The spindle extends axially into one arm 22 of the angle head, and is supported therein in bearings 23 and 24. A beveled pinion 25 on the spindle drivingly engages a bevel gear member 26 of a combined nut running and nut crimping mechanism 27 housed in the angle head. The mechanism is shown as arranged in a second arm 28 of the angle head, which arm extends at right angles to the longitudinal axis of the general housing of the tool.

The mechanism 27 has an initial first stage of operation upon application of torque to it by the spindle 21 in one direction to run a work nut 29 down to a predetermined degree of tightness; and it has a subsequent second stage of operation upon receiving torque from the spindle in an opposite direction to crimp the work nut.

The bevel gear member 26 of the mechanism 27 has a tubular body which is supported in a bearing 31 and has a splined driving connection 32 with a surrounding tubular body of a slidable dog 34. The splined connection 32 allows axial movement of the dog relative to the gear member. The dog has a group of end jaws 35 which are drivingly engageable with complementary jaws 36 of a drive nut 37. A return spring 38 normally biases the dog axially to a position wherein the jaws of the dog are disengaged from those of the drive nut. One end of the spring abuts an overhanging shoulder of the drive nut; and its other end is seated upon a ring 39 having a bearing support upon an underlying shoulder of the dog.

A piston 41 having a tubular body sleeved upon the body of the dog is pneumatically operable in an expansible chamber 42 to slide the dog against the resistance of thespring into clutched driving engagementwith the drive nut. A thrust ring bearing 43 is disposed between the piston and an overlying shoulder of the dog. A passage 44 through the angle head connects the expansible chamber with an external hose45 leading to a side port 46 of the housing. Port 46 connects with a chamber 47. The latter also connects with passage 16 leading to the motor; and is supplied with live air from the throttle valve 15.

The drive nut 37 has a tubular body, one end of which is journaled in a bearing 48 seated in'an axial recess of a cap 49 that closes the rear end of the angle head. Bearing 48 is confined to the recess by means of a retaining ring 51. The opposite end of the drive nut has bearing contact with the upper end of the gear member 26; and a thrust ring bearing 52 is provided between the annular flange of the drive nut and the overhead retaining ring 51. By means of this arrangement, the drive nut has rotation relative to the angle head and to the gear member but is curbed against relative axial movement.

The drive nut has an internal helical splined engagement with an upper screw portion of the shaft of a travel wedge 54 (FIGS. 1 and An intermediate smooth cylindrical portion ofthe shaft depends slidably through the body of the gear member 26. A lower shaft portion S5 of larger diameter depends below the gear member and projects slidably through an axial opening of a gland ring 56 into the interior ofa jaw holding sleeve 57. The gland ring is retained in a fixed position to the sleeve and serves as a closure to retain grease in the gear area above. Below the gland ring the shaft of the travel wedge terminates in a wedge head 58 of larger diameter than its shaft portion 55.

The wedge head is splined to the holding sleeve for relative axial movement as well as for rotatably driving the sleeve. To permit rotation of the sleeve, the latter is loosely supported at its upper end in the angle head between an overlying shoulder of the latter and an underlying beveled surface 59 of a sleeve screw 61. The

latter is entered into an open bottom 'end of the angle head. In this arrangement, the holding sleeve 57 has rotation relative. to the angle head but is restrained against relative axial movement. A lower end of the holding sleeve projects externally of the angle head.

The holding sleeve (FIGS. 1, 4, 7) has a group of six internal longitudinally extending spline tracks 62 spaced circumferentially equally apart. In each track is slidably received a separate one of six radial splines 63 formed about the wedge head. Each spline has a downwardly and inwardly tapering flat angle surface 64 which terminates in a tip 65 common to the several splines. The axis of the tip coincides with that of the holding sleeve.

The wedge head normally has a raised position, as in FIGS. 1 and 7, under the bias of a return spring 66, in which position an annular shoulder at its top underlies the gland ring and an annular shoulder 60 of its shaft portion abuts the gear member 26. Also, in this normal position its common tip 65 is abutted slightly rearwardly of its apex by the rounded vertex ends 67 of a group of crimping levers or jaw elements 68.

There are six jaw elements, each located in a separate track 62 of the holding sleeve in underlying relation to the angle surface 64 of a separate one of the splines of the wedge head. The jaw elements are ofa general right triangular form. Each has a base end 69 and an upper tail portion having inner and back walls 71, 72 terminating in the vertex 67. The base end has a rounded back corner or heel 73 pivotally seated in an inside radius or pocket 74 formed adjacent the bottom end of 4 a related track of the holding sleeve; and the base end has a crimping toe or jaw 75 atits inner end. The jaw 75 is flat faced and in extension of the wall 71. A shallow inside radius 75a (FIGS. 8a, 8b) separates the jaw portion 75 from the upper portion of wall 71.

The several jaw elements are constantly urged by means of the load of spring 66 acting through a jaw return plunger 76 to pivot their tail or vertex ends inwardly of the holding sleeve into abutment with the tip of the wedge head and to draw their jaw ends 75 outwardly to an open condition as in FIGS. 1 and 7. The plunger has an elongated axial stem 77 which is slidably received in an axial bore of the'wedge head. The stem 77 terminates at its bottom in an inverted cup portion or head 78 of enlarged diameter which has a bearing contact with the surrounding internal wall of the wedge head. The cup portion has a radial annular lip 79 at its bottom, in the undersurface of which is a group of six radial slots 81 (FIGS. 3, 7) spaced equally apart. In each slot is received a separate lug 82 projecting from below the mid-area of the inner face of a jaw element. The upper wall of each slot is pressed under the load of the spring 66 upon the underlying lug 82 so as to pivot the vertex end 67 of the related jaw element inwardly into abutment with the tip of the wedge head as in FIGS. 1 and 7. The return spring is under constant compression between opposed shoulders of the travel wedge and the plunger.

In this normal position of the jaw elements, their six inner faces 71 are in a substantially vertical position; and their jaws 75 define below the several lugs 82 a hexagonal opening for reception of a hex-form work nut 29, as appears in FIGS. 1 and 7. Accordingly, clockwise rotation of the jaw sleeve in this normal condition of the jaws will rotate and set the work nut.

It can be seen that if the wedge head 58 is caused to move axially downward relative to the holding sleeve 57, its tip 65 and the angle surfaces 64 of its several splines will ride in a camming action over the vertexes 67 of the jaw elements causing the latter to pivot their tail ends outwardly. The outward pivoting will cause the several flat faced crimping jaws 75 to swing inwardly in an arc so as to close upon and forcefully compress or crimp corresponding flats of the work nut, as in FIG. 8. A slight inside radius 83 above the heel 73 of each jaw element is adapted in this outward pivoting action to seat over a complementary radius 84 located above the pocket 74 so as to permit the rear wall of the jaw to limit substantially upon the opposed back wall of the related track of the holding sleeve. This arrangement serves to maintain a proper seated relation of the heel of the jaw to its' pocket during pivoting of the jaw in a crimping direction.

It is to be noted in the crimping action that the jaw ends'75 of the jaw elements move relative to the corresponding flats of the work nut 29 in a radially and upwardly curved path, each defining an are which is concentric with its pivot. The flat face 75 of each jaw in penetrating a corresponding flat of the work-compressively displaces a triangular volume of metal which flows inwardly to obtain a desirable locked condition of the nut and stud. When the jaws are withdrawn, a triangular indentation from which the metal was displaced appears in each flat. The deepest portion of the indentation is toward the work or lower end of the nut from where it extends angularly upward to intersect with the flat side of the nut. This manner of crimping the nut is of decided advantage in that it ensures that the jaws, as

well as the tool willbe readily released from the nut to slide the dog 34 into driving engagement with the drive nut 37. Air also flows from chamber 47 through passage 16 to the motor. Resultant rotation of the motor is transmitted through the

bevel gearing

25, 26 and dog 34 to impart clockwise rotation to the drive nut 37. The clockwise torque of the drive nut is transmitted through the helical splines to draw the travel wedge 54 upwardly so as to frictionally lock its shoulder 60 against the bevel gear 26. With this action, the bevel gear, dog, drive nut and travel wedge rotate as a unit and act through the wedge head 58 to 'rotate the jaw holding sleeve 57 to cause the jaw elements 68 to run down and set the work nut 29. When the work nut is driven to a predetermined degree of tightness, the resultant overload causes the motor to stall. The operator then manually shifts the reversing valve 17 causing inlet air flow to shift its direction and drive the motor in an opposite direction. Consequent reverse rotation of the drive nut 37 relative to the travel wedge 54 causes the latter to travel linearly downward against the force of the return spring 66. In this movement, thewedge head 58 rides down the spline tracks 62 relative to the jaw holding sleeve. At this time, the coned surface of the sleeve becomes loaded against the opposed mating surface 59 of the screw 61 so that the sleeve is restrained against rotation in a loosening direction of the nut. The downwardly moving wedge head cooperates with the several jaw elements 68 to compressively and forcefully close their jaws upon and crimp the work nut. Resistance offered by the jaw elements to further pivoting as their backs stop against the wall of the sleeve stalls the motor. The operator then releases the throttle valve to closed condition, shutting off air flow to the motor. As the holding air acting in chamber 42 on the piston is then vented through the motor, spring 38 disengages the dog 34. With this action, the drive nut 37 spins freely about as the travel wedge is linearly returned to normal by the plunger spring 66. Simultaneously with this action, the several jaw elements are pivoted under the spring load of the plunger 76 to normal open condition as the wedge head restores upwardly. The tool is then lifted from the work; and the reversing valve 17 is manually reshifted to normal condition preparatory to the next work operation.

Since crimping of the work nut occurs after a final torque has been delivered to the work nut, marks left by the biting action of the jaw ends of the jaw elements into all six sides of the work nut provide a permanent indication that the required torque has been delivered. It is apparent that if the tool is used in setting a bolt having a hexagonal head, it would serve not only in delivering a predetermined degree of torque to the bolt, but it would also serve by means of the biting marks made by the jaws in the bolt head to visibly indicate that the bolt head has obtained the required torque. Accordingly, the tool is useable, not only as a nut setting and crimping device, but also as a bolt setting and bolt marking device.

In place of the particular throttle valve 15 and reversing valve 17 shown in FIG. 1, the handle section of the tool (as appears in FIG. 9) is shown as including a modified valving system, generally indicated at 86, controlling flow of inlet air to the motor and to the angle head mechanism 27. The valving system functions automatically following opening of a throttle valve member A to cause the tool to pass through a complete cycle of setting and crimping the work nut and then restoring to normal condition without intervention of the operator.

The valving system includes the throttle valve A, a first slidable control valve B, a reversing valve C, and a second slidable control valve D. An adjustable regulator valve E may be located between the inlet 87 and the throttle valve to vary the volume of inlet air flow to the throttle valve.

Throttle valve A is designed so that after it has been manually depressed to open condition against the force of its return spring 88, it will remain pneumatically depressed until completion of the operating cycle of the tool. It will then be restored automatically to closed condition. I

The chamber 89 under the throttle valve A is con nected through

ports

90, 91, 92 (FIG. 12) and 93 to vent 94 (FIG. 14). When the throttle valve is depressed to open condition, the pressure of supply air developing over the upper area of the valve exceeds the force of its return spring 88 so as to hold the valve in open condition, permitting removal of the operator's hand from the. valve button 95.

Supply air flows through the open throttle valve to a common chamber 470 from where it flows through side port 46a and the external hose 45 (FIG. 10) to pressurize piston chamber 42 (FIG. 1) in the angle head. This causes the piston 41 to force the dog 34 into driving engagement with the drive nut 37, as earlier explained. Air also flows from the common chamber 47a through port 96, chamber 97 of control valve B, and port 98 to passages 99 and 100 (FIG. 12) to the motor feed ports 101 (FIG. causing the air motor 13 (FIG. 1) to operate in a nut tightening direction. The residual exhaust from the motor passes through ports 102, 103 (FIG.

15), 104, 105 (FIG. 9), the chamber 106 underside of the second control valve C to the exhaust port 107.

. Supply air entering chamber 97 of thefirst control valve B passes through a check valved port 108 in valve B through port 109 at the top end of the valve and out of port 110 to port 111 connected with the upper chamber 112 of the reversing valve C. Chamber 113 at the bottom of valve C is connected through port 114 to passage 99 so that at this time valve C is pneumatically balanced by live air in chambers 112 and 113 at its top and bottom.

When the work nut is tightened to 'a predetermined value of torque (as earlier explained) back pressure develops through motor feed passage 99 into chamber 115 of valve B.'The effective area of valve B subject to air pressure is greater at its top end in chamber 115 since the stem end 116 of the valve is exposed through a vent passage 117 to atmosphere. Accordingly, valve B is forced downward below port 96 by pressure in chamber 115 against the force of spring 120. This downward movement of'the valve closes supply port 96 to the motor feed passage 99 and opens it through chamber 115 and port 111 to chamber 112 at the top of the reversing valve C. The pressure air trapped in motor feed passage 99 and in the connected chambers 97 and 113 below both valves B and C exhausts through the motor. This action results in holding control valve B in its shifted. position and causes the reversing valve C to shift down against its return spring 119 below port 105 I Supply air is now directed from port 96 through the upper chamber 115 of control valve B, the upper chamber 112 of the reversing valve C, ports 105, 104 and passage 103 (FIG. 15) to the feed ports 102 to drive the motor in an opposite direction to effect crimping of the work nut, as earlier explained. The residual exhaust from the motor now'passes through the other set of motor feed ports 101 (FIG. 15), then ports 100, 99 (FIG. 9), 114 and the intermediate chamber 106 of reversing valve C to the exhaust port 107. As the crimping action progresses, back pressure from the load on the motor progressively develops through port 104, port 120, lower chamber 121 of the second control valve D and through valve passage 123 to chamber 124 at the top of valve D. When the jaws 68 stop against the wall of the sleeve in the crimping action, back pressure in chamber 124 develops to a value sufficient to shift valve D downward against the force of its return spring 125. Shifting of valve D opens. port 126, permitting flow of supply air from ports 104, 120, 123, 126, 93

(FIG. 14), 92 (FIG. 12) 91 and 90 (FIG. 9) to chamber- 4 89 at the bottom of the throttle valve A. Pressurization of chamber 89 pneumatically balances the throttle valve, causing it to be restored to closed condition by its return spring 88 and thereby stopping flow of all air to the tool. The air trapped in the piston chamber 42 of the angle head then exhausts through the motor, as

earlier explained, permitting the mechanism 27 in the angle head to restore to normal.

What is claimed is:

1. In a nut running tool including a reversible rotary air motor, combined nut running and crimping mechanism for running down a work nut in response to rotation of the motor in one direction and for crimping the work nut in response to rotation of the motor in an opposite direction, and means drivingly coupling the motor with the combined nut running and crimping mechanism. 1

2.- In a nut running tool as in claim 1, wherein control means is selectively operable for feeding operating air to the motor to drive it in a selected direction.

3. In a nut running tool as in claim 1, including control valve means initially manipulative to feed live air to the motor for driving it in the one direction and being responsive to development of a predetermined back pressure upstream of the motor to cause shifting of the live air flow to drive the motor in the opposite direction.

4. In a nut running tool as in claim 1, including control valve means initially manipulative to feed live air to the motor for driving it in the one direction and being responsive to development of a predetermined back pressure upstream of the motor to cause shifting of the live air flow to drive the motor in the opposite direction, and wherein the control valve means is further responsive to development of a predetermined back pressure upstream of the motor during the time the motor is running in the said opposite direction to shut off flow of live air flow to the motor.

5. In a nut running tool as in claim 1, wherein the combined nut running and crimping mechanism comprises a rotatable open-ended sleeve member, pivotable camming jaws retained in the sleeve member, each having an elongated inner wall with a crimping toe at its bottom, the several jaws having a normal pivoted position relative to the sleeve member in which the several inner walls are parallel to the. axis of the sleeve member and define a multi-walled opening for reception of a work nut, and the several jaws being pivotable from this normal position to swing the upper ends of their inner walls outwardly relative to normal so as to carry their toe ends arcuately inwardly of normal to effeet a crimping action upon a work nut received in the opening.

6. In a nut running tool as in claim 5, including a front end section housing the nut running and crimping mechanism having an open front end in which the sleeve member is rotatably mounted, wherein a travel wedge member of the nut running and crimping mechanism projects into a rear open end of the sleeve member above the several jaws, the wedge member having a splined driving connection with the sleeve member and being axially movable relative to both the sleeve member and the several jaws, the wedge member in its axial movement having camming cooperation with the several jaws so as to pivot them from their normal position, and means connects the wedge member with the motor, the means having response to rotation of the motor in said one direction to cause rotation of the wedge member and as a consequence rotation of the sleeve member and having response to rotation of the 7. In a nut running tool as in claim 6, wherein a drive nut has in internal helical spline connection with the travel wedge member, and a gear train drive connects the motor with the drive nut, the drive nut having rotation relative to the travel wedge member and being restrained against relative axial movement.

8. In a nut running tool as in claim 7, wherein pneumatically operable clutch means in interconnected in the gear train having a normal condition disengaging the gear train drive from the drive nut.

9. In a nut running tool as in claim 8, wherein the clutch means includes a slidable dog having clutch jaws drivingly engageable with complementary jaws on the drive nut, a spring normally biases the dog out of clutched engagement with the drive nut, and a piston is pneumatically operable to slide the dog into clutched engagement with the drive nut.

10. In a nut running tool as in claim 9, wherein means is provided for feeding operating air concurrently to the motor and to the piston.

11. A combined n ut running and nut crimping tool comprising a housing, a fluid powered rotary motor within the housing, manipulative valve means controlling fluid flow to the motor selectively operable for causing rotation of the motor in a forward or reverse direction, an angle head section defining a front end of the housing having an arm at an angle to the longitudinal axis of the tool, combined nut running and nut crimping mechanism incorporated in the arm of the angle head section, gearing drivingly coupling the motor to the mechanism, the mechanism being responsive to rotation of the motor in one direction to run down the work to a predetermined degree of tightness and being responsive to rotation of the motor in an opposite direction to squeeze the work.

12. A combined nut running and nut crimping tool comprising a housing, a fluid powered rotary motor within the housing, an angle head section defining a front end of the housing having an arm at an angle to the housing, combined nut running and nut crimping mechanism incorporated in the arm of the angle head section, gearing drivingly coupling the motor to the mechanism, the machanism being responsive to rotation of the motor in a particular direction to run down the work to a predetermined degree of tightness and being responsive to rotation of the motor in an opposite direction to squeeze the work; and control valve means controlling fluid flow to the motor, characterized by a throttle valve actuable to initiate fluid flow to the motor for rotation of the motor in a particular direction, by first valve means having response to a predetermined back pressure developing upstream of the motor to shift the direction of fluid flow to the motor to cause rotation of the motor in an' opposite direction, and by second valve means having response to a predetermined back pressure developing upstream of the motor while the motor is rotating in said opposite direction to cause shut-off of air flow to the motor.

Claims

1. In a nut running tool including a reversible rotary air motor, combined nut running and crimping mechanism for running down a work nut in response to rotation of the motor in one direction and for crimping the work nut in response to rotation of the motor in an opposite direction, and means drivingly coupling the motor with the combined nut running and crimping mechanism.

2. In a nut running tool as in claim 1, wherein control means is selectively operable for feeding operating air to the motor to drive it in a selected direction.

5. In a nut running tool as in claim 1, wherein the combined nut running and crimping mechanism comprises a rotatable open-ended sleeve member, pivotable camming jaws retained in the sleeve member, each having an elongated inner wall with a crimping toe at its bottom, the several jaws having a normal pivoted position relative to the sleeve member in which the several inner walls are parallel to the axis of the sleeve member and define a multi-walled opening for reception of a work nut, and the several jaws being pivotable from this normal position to swing the upper ends of their inner walls outwardly relative to normal so as to carry their toe ends arcuately inwardly of normal to effect a crimping action upon a work nut receIved in the opening.

6. In a nut running tool as in claim 5, including a front end section housing the nut running and crimping mechanism having an open front end in which the sleeve member is rotatably mounted, wherein a travel wedge member of the nut running and crimping mechanism projects into a rear open end of the sleeve member above the several jaws, the wedge member having a splined driving connection with the sleeve member and being axially movable relative to both the sleeve member and the several jaws, the wedge member in its axial movement having camming cooperation with the several jaws so as to pivot them from their normal position, and means connects the wedge member with the motor, the means having response to rotation of the motor in said one direction to cause rotation of the wedge member and as a consequence rotation of the sleeve member and having response to rotation of the motor in said opposite direction to cause said axial movement of the wedge member.

7. In a nut running tool as in claim 6, wherein a drive nut has in internal helical spline connection with the travel wedge member, and a gear train drive connects the motor with the drive nut, the drive nut having rotation relative to the travel wedge member and being restrained against relative axial movement.

11. A combined nut running and nut crimping tool comprising a housing, a fluid powered rotary motor within the housing, manipulative valve means controlling fluid flow to the motor selectively operable for causing rotation of the motor in a forward or reverse direction, an angle head section defining a front end of the housing having an arm at an angle to the longitudinal axis of the tool, combined nut running and nut crimping mechanism incorporated in the arm of the angle head section, gearing drivingly coupling the motor to the mechanism, the mechanism being responsive to rotation of the motor in one direction to run down the work to a predetermined degree of tightness and being responsive to rotation of the motor in an opposite direction to squeeze the work.

12. A combined nut running and nut crimping tool comprising a housing, a fluid powered rotary motor within the housing, an angle head section defining a front end of the housing having an arm at an angle to the housing, combined nut running and nut crimping mechanism incorporated in the arm of the angle head section, gearing drivingly coupling the motor to the mechanism, the machanism being responsive to rotation of the motor in a particular direction to run down the work to a predetermined degree of tightness and being responsive to rotation of the motor in an opposite direction to squeeze the work; and control valve means controlling fluid flow to the motor, characterized by a throttle valve actuable to initiate fluid flow to the motor for rotation of the motor in a particular direction, by first valve means having response to a predetermined back pressure developing upstream of the motor to shift the direction of fluid flow to the motor to cause rotation of the motor in an opposite direction, and by second valve means having response to a predetermined back pressure developing upstream of the motor while the motor is rotating in said opposite direction to cause shut-off of air flow to the motor.