US3353453A

US3353453A - Fastener driving tool

Info

Publication number: US3353453A
Application number: US457767A
Authority: US
Inventors: Howard B Ramspeck
Original assignee: Duo Fast Corp
Current assignee: Duo Fast Corp
Priority date: 1965-05-21
Filing date: 1965-05-21
Publication date: 1967-11-21
Anticipated expiration: 1984-11-21
Also published as: DE1942093U

Description

Nov. 21, 1967 H. B. RAMSPECK 3,353,453

FASTENER DRIVING TOOL Filed May 21, 1965 3 Sheets-Sheet 1 Haw/120' B, PAMsPEc/e 34 5V Mm, A aiemm fa/Wwmd 71? Nov. 21, 1967 H. B. RAMSPECK 3,353,453

' FASTENER DRIVING TOOL Filed'May 21, 1965 v 5 Sheets-Sheet 2 1967 H. B. RAMSPECK 3,353,453

FASTENER DRIVING TOOL Filed May 21, 1965 5 Sheets-Sheet 5 United States Patent 3,353,453 1 FASTENER DRIVING TOOL Howard B. Ramspeck, Chicago, Ill., assignor to Fastener Corporation, Franklin Park, Ill., a corporation of Illinois Filed May 21, 1965, Ser. No. 457,767 16 Claims. (Cl. 91-356) ABSTRACT OF THE DISCLOSURE A control valve on a pneumatic stapler is effective to drive the power piston mounted in the power cylinder through its drive stroke and automatically and sequentially through a return stroke whether or not the trigger has been released. This is accomplished by providing two valve members operatively interrelated with a delay mechanism or lost motion-dashpot connection therebetween to control the return of the piston upon completion of its drive stroke.

This invention relates to a fastener driving tool and, more particularly, to a fastener driving tool including new and improved control means, and to control means for a fastener driving tool.

Commercial pneumatic fastener driving tools generally employ either compression spring or pneumatic piston return means. Thus when the trigger of a fastener driving tool is depressed, the power piston and connected fastener driving blade are driven through the power stroke of a fastener driving operation by the admission of pressurized fluid into the power cylinder of the tool. The power piston will remain at the end of its power stroke until the fluid pressure is released, as by exhausting the cylinder to the atmosphere, at which time the compression spring or pneumatic piston return means is effective to return the piston to its normal or static position. Pneumatic fastener driving tools are known wherein the power piston and driving blade move both down and up automatically upon depression of the trigger, before the trigger is released. This snap-action piston and driving blade operation is desirable in many applications such as upholstery stapling to prevent fraying of the material by the driving blade while the tool is moved along the workpiece.

Accordingly one object of the present invention is to provide a new and improved pneumatically actuated fastener driving tool.

Yet another object of the present invention is to provide a fastener driving apparatus including new and improved control valve means for initiating operation of a fastener driving operation.

A further object of the present invention is to provide a fastener driving tool having new and improved means for driving the power piston and driver blade both down and up automatically before the trigger is released.

A further object of the present invention is to provide a fastener driving apparatus having a control valve which automatically and sequentially connects the power cylinder first to a fluid reservoir and then to the atmosphere without the necessity of releasing the trigger.

Yet a further object of the present invention is the provision of a new and improved control valve for a fastener driving tool which is elfective to cycle the power piston and driver blade through the power and return strokes automatically upon depression of the trigger.

In accordance with these and many other objects, the improved control valve according to the present invention controls a pneumatically actuated fastener driving tool or apparatus of the type having a housing with a forward head portion and a rearwardly extending hollow handle forming a compressed air or fluid reservoir and housing the improved control valve. The head portion includes a generally vertically extending cylinder having an upper open end which may be sequentially exhausted to the atmosphere, or connected to the reservoir of pressurized fluid, by the depression of the trigger. In the normal or static condition of the fastener driving apparatus, the power cylinder is exhausted to the atmosphere. Upon depression of the trigger, the control valve is effective to connect the power cylinder first to the fluid reservoir, and thereafter sequentially and automatically exhausted to the atmosphere with a snap action of the control valve without the necessity of releasing the trigger.

The forward head portion of the tool including the power piston and driver blade may be of any known suitable type, such as the commercially available spring return or pneumatic return types. The illustrated embodiment by way of example discloses a pneumatic return power piston described and claimed in a copending application of Oscar A. Wandel entitled Fastener Driving Tool and filed on even date herewith.

More specifically the improved control valve assembly includes a valve chamber having a first port communicat ing with with atmosphere, a second port communicating with the fluid reservoir, and a third port communicating U with the power cylinder. The ports communicating with the atmosphere and with the fluid reservoir of define valve seats in the valve chamber. A first or upper valve stem means is provided with valve elements alternately cooperable with respective ones of the seats to alternately connect the cylinder port to the port exhausting to the atmosphere or to the port communicating with the fluid reservoir. Additionally the control valve includes a valve cylinder and a second or lower valve stem means having a portion telescopically receivable in a recess in the upper valve stem means and further having integral therewith a piston slideable within the valve cylinder. Differential pressure acting on the valve steam means will move the upper valve stem means down, closing the exhaust of air from the power cylinder to the atmosphere, and simultaneously connecting the power cylinder to the fluid reservoir to provide for driving the power cylinder and driver blade through its power stroke. Time pressurized fluid from the fluid reservoir to act against a lower piston connected to the lower valve stem means so that the differential pressure acting on the upper valve stem means will automatically return the upper valve stem means to its initial or normal position wherein the communication between the power cylinder and the fluid reservoir is blocked, and the power cylinder is exhausted to the atmosphere. Consequently the power piston and driver blade will automatically return to their normal position without the necessity of releasing the trigger. When the trigger is subsequently released, pressurized fluid from the fluid reservoir will enter the valve cylinder and bias the lower valve stem means upwardly against the upper valve stem means so as to hold the upper valve stem means in its normal or static position until such time as the trigger is again depressed to repeat the cycling of the fastener driving tool.

In order to provide the time delay operation of the valve to permit automatic resetting of the power piston, the upper valve means with its upper piston is provided with the recess forming a cylinder and the lower valve stem means is cooperatively associated with the piston having the portion telescopically received in the recess. One of the valve pistons is provided with a skirt depending toward the other to define a dashpot chamber formed between the two pistons. During the power stroke of the fastener driving tool, pressurized fluid from the fluid reservoir is bled at a metered rate into this dashpot cham her to provide a pressure differential on the upper valve stem means and to drive the upper valve stem means upwardly thereby shutting off the pressurized fluid from the 3 power cylinder and exhausting the cylinder to the atmosphere.

Many other objects and advantages of the present invention will become apparent from considering the following detailed descriptions in conjunction with the drawings in which:

FIGURE 1 is a fragmentary sectional view of a fastener driving tool embodying the present invention and illustrated with the piston and driver blade at the bottom of its power stroke;

FIGURE 2 is a fragmentary sectional view similar to FIGURE 1, illustrating the fastener driving tool of FIG- URE 1, with the piston and driver blade intermediate its return stroke; and

FIGURE 3 is a fragmentary sectional view of the fastener driving tool of FIGURE 1, illustrating the control valve thereof in its normal or static position.

Referring now specifically to the drawings, there is illustrated a fastener driving tool which is indicated generally as and which embodies a control valve assembly according to the present invention. It is understood that the tool 10 may be of any suitable type having a spring or pneumatically returned power piston; the piston return mechanism of the illustrated tool is described and claimed in the above mentioned Wandel application. However, briefly the tool 10 includes a housing 12 having a forward and generally vertically extending head portion 12a and a rearwardly extending hollow handle portion 12b forming an air or fluid reservoir 14 to which a pressurized fluid, such as compressed air, is supplied in any suitable manner, as by a flexible airline. The head portion 12a of the housing 12 includes a cavity 16 in which is mounted a sleeve forming cylinder 18. An air return chamber 19 is defined in the cavity by the cylinder sleeve 18. The lower end of the cylinder 18 is in communication with the chamber 19 and an open upper end thereof is in continuous communication with a port or passageway 20 formed in the housing. A manually actuated control valve assembly which is indicated generally as 22 normally connects the passageway 20 to the atmosphere through a passage way 24- formed in the hollow handle portion 12b and is operable to a position in which it connects the passageway 26 to the fluid in the reservoir 14. The fluid admitted to the passageway 20 enters the open upper end of the cylinder 18 and drives a power piston 26 which is slidably mounted within the cylinder 18 and which is secured to the upper end of a fastener driver blade 28 downwardly so that the lower end of the driver blade 28 engages and drives a fastener 30 supplied one at a time to a drive track 32 in a nosepiece assembly 34 by a magazine assembly indicated generally as 36.

During the downward movement of the piston 26, the air disposed within the cylinder 18 below the piston 26 is driven through a plurality of ports in the lower wall of the cylinder 18 into the return air chamber 19. When the compressed air disposed above the piston 26 is exhausted to the atmosphere under the control of the control valve assembly 22, air pressure from the return air chamber 19 is effective to act on the lower surface of the piston 26 to return the piston from its displaced position adjacent the lower end of the cylinder 18 to a normal position adjacent the open upper end thereof.

The mechanical construction of the housing 12 and the magazine assembly 36 is disclosed in detail in an application of Thomas H. Dorney, Ser. No. 326,913, filed Nov. 29, 1963, and assigned to the same assignee as the present invention. In general, the head portion 12a of the housing 12 includes a structure defining the cavity 16 in which a flanged portion 18a of the cylinder is received with the interface between the wall of the head portion 12a and the outer wall of the flange portion 18a being sealed by a resilient O-ring 44. An upper opening in the head portion 12a is closed by a closure cap 46 secured to the housing 12 by a plurality of machine screws 48 with a resilient sealing gaskfi i 49 interposed therebe tween. A recess 50 in a depending portion 46a on the closure cap 46 carries a block or bumper 52 of resilient material that engages the upper end of the piston 26 at the termination of its return stroke, and an annular resilient bumper 54 is disposed in the lower end of the cavity 16 to cushion the termination of the power stroke of the piston 26. The bumper 54 is held in position at the bottom of the cylinder 18 by engagement with a shouldered portion 18b formed on the cylinder 18. The lower end of the interior of the cylinder 18 is placed in communication with the cavity 16 through a plurality of peripherally spaced ports or openings 56. The chamber 19 is sealed at its lower end by a resilient O-ring 58 placed between the lower wall of the piston 26 and the inner wall of the cylinder 18.

For the purpose of admitting pressurized air to the cavity 16 there is provided a plurality of small, metered bleed openings or ports 60 in the well of the cylinder 18 communicating with the chamber 19 and spaced above the openings 56 intermediate the length of the cylinder.

To provide means for sealing the interface between the outer wall of the piston 26 and the inner wall of the cylinder 18 there is provided a first O-ring 62 in an annular ring channel or groove 64 in the piston wall. Additionally to provide means for selectively supplying compressed air to the cavity 16, there is provided an additional O-ring 66 in an elongated annular channel or groove 68 forming a check valve so that the O-ring 66 is free to slide in the groove 68 into engagement with the upper and lower end surfaces of the groove 68. Moreover the groove 68 is recessed to provide one or more slots 74 extending from near the upper or outer edge of the groove 68 to below the lower or inner edge thereof. Thus when compressed air is supplied to the upper end of the cylinder 18, the air will pass through the interface by way of the slot 74, but when air is supplied to the lower end of the cylinder 18 below the O-ring 66, the O-ring 66 acts as a check valve and seals against the upper surface of the groove 68 thereby preventing the air from passing around the O-ring.

A thin metal sealing member 76 is provided to prevent escape of air from below the piston 26 around the driver blade 28. The driver blade 28 passes through a close fitting slot 76:: in the sealing member 76 to form a substantial airseal. Of course it is to be understood that in the normal operation of a pneumatically actuated fastener driving tool, compressed air may leak or bleed out around the seals but such air leakage is insignificant in the overall operation of the fastener driving apparatus.

In order to charge the return air chamber 19 with moe highly pressurized air, the bleed opening 60 is positioned to lie between the O-

rings

62 and 66 when the piston 26 is in its lowermost position as indicated in FIGURE 1.

It will be understood that the fastener driving tool 10 is in a normal or static position with the piston 26 in its uppermost position against the bumper 52. In this position the control valve assembly 22 is in a normal or static position discharging the space above the piston 26 to the atmosphere and blocking the flow of pressurized fluid from the reservoir 14. Actuation of the control valve assembly 22 simultaneously blocks the communication of the cylinder 18 with the atmosphere and directs the pressurized fluid from the fluid reservoir 14 into the upper end of the cylinder 18 driving the piston 26 and driver blade 28 downwardly through its power stroke. In the initial downward movement of the piston 26, there will be no bypass of pressurized fluid around the O-

rings

62 or 66 even though the Oring 66 may be in its lowermost position within the groove 68 since the passage of such pressurized fluid is blocked by the lower O-ring 62. The downward travel of the piston 26 drives the air below the piston through the ports 56 into the return air chamber 19 and the piston 26 ends its power stroke against the cleared the bleed openings 60 and pressurized fluid from above the piston 26 bypasses the upper O-rings 66 through the slot 74 and enters into the return air chamber 19 through the bleed openings 60.

Upon completion of the power stroke of the piston 26, the control valve assembly 22 is effective to shut off the communication between the fluid reservoir 14 and the top of the cylinder 18, and to exhaust the upper end of the cylinder 18 to the atmosphere through the

passageways

20 and 24. As soon as the air in the upper end of the cylinder 18 is exhausted to the atmosphere, the pressurized fluid in the return air chamber 19 will be effective to drive the piston 26 upwardly to return to a normal or static position. Initial flow of air from the pressure return valve will take place through both bleed openings 60 and openings 56. The initial air through bleed opening 60 will be effective to raise the upper O-ring 66 against the upper inner surface of the groove 68 to check any further flow of air around the O-ring 66. In this manner the O-ring 66 functions as a check valve when the piston 26 is in its lowermost position, permitting the air to pass downwardly around the O-ring, but effectively blocking the return flow of air upwardly around the O-ring. The pressurized air from the return air chamber 19 will propel the piston upwardly to its uppermost position to return the fastener driving tool to its normal position. Sufficient fluid will leak between the sealing means 76 and the driver blade 28 to discharge the fluid below the piston 26 to the atmosphere upon completion of the return stroke.

According to the present invention the improved control valve assembly 22 is provided for operating the tool 10 by sequentially connecting the open upper end of the cylinder 18 first to the fluid reservoir 14 and thereafter automatically to the atmosphere through passageway 24. The control valve assembly 22 includes a valve chamber 79 defined by an exhaust valve seat 80 carried on the housing 12 and having a downwardly and inwardly tapered port or opening 82 through which the passageway is normally placed in communication with the exhaust passageway 24. The opening 82 can be closed by a resilient O-ring or valve element 84 carried on the upper end of an upper valve stem assembly 86. A resilient valve element 88 is also carried on the upper valve stem assembly 86 disposed above an upper valve piston 90 forming a part of the upper valve stem assembly 86. The resilient valve element 88 normally closes a port or passageway 92 interposed between the :reservoir 14 and the passageway 20 and forming a valve seat. The valve piston 90 closely fits and is slidably mounted within a valve cylinder 94 formed in a valve body 06 that is threadingly received within a tapped opening 98 in the housing 12. A metered leakage of fluid can pass between the side wall of the upper piston 90 and the inner wall of the valve cylinder 94 through the clearance area or passageway 100.

The control valve assembly 22 additionally includes a lower valve stem assembly 102 telescopically received within a recess in the bottom surface of the upper valve assembly 86 defining a lost-motion connection between the

valve stem assemblies

86 and 102 and forming a cylinder 104. The lower valve stem assembly 102 and valve cylinder 104 form a chamber 106.

Forming a portion of the lower valve assembly 102 is a lower valve piston 108 slidably received within the valve cylinder 94. An O-ring 110 seals the side surface of the lower valve piston 108 with the cylinder 94. A resilient valve element 112 is also carried on the lower valve stem assembly 102 on the piston 108 and engages against an annular projection or skirt 114 extending contiguous with the outer surface of the upper piston 90 downwardly from the lower end thereof to define a dashpot or time-delay chamber 116 therebetween. An additional O-ring or valve element 118 pneumatically seals the lower valve assembly 102 against the inner wall of the cylinder 104. A metered bleed passage 12.0 forming a dashpot or time-delay mecha- 6 nism bypasses the O-ring 118 to provide communication between chamber 106 and the dashpot chamber 116. Additionally a port 122 extends through the side wall of the cylinder 104 near its upper end to exhaust chamber 106.

A pilot valve assembly is included in the control valve assembly 22 to initiate the operation thereof and to permit the assembly 22 to be operated with a minimum manually applied force. This pilot valve assembly includes an operating pin 124 that is slideably mounted within an axial bore formed in a member 126 that is threadingly received within an opening 128 in the valve body 96.'A trigger 129 provides for depression of the operating pin 124. An O-ring 130 seals the interface between the valve body 96 and the member 126. The upper end of the ope-rating pin 12.4 is tapered and carries an O-ring 132 that operates as a valve element to control communicatlon between the reservoir 14 and a bore or opening 134 through a passageway 136, or to selectively exhaust the bore 134 to the atmosphere through a clearance space forming an exhaust opening 138 around the operating pin 124. The bore 134 communicates through a passageway 142 with a chamber 140 formed between the lower end of the cylinder 94 and the lower piston 108.

From the above description of the control valve assembly 22, its operation is believed clear. However, briefly, assuming the control valve assembly 22 to be in its normal or static position, as indicated in FIGURE 3, pressurized fluid from the fluid reservoir 14 passes through passageway 136, over the O-ring valve element 132, into the bore 134, through passageway 142, and into the control chamber 140 below the lower piston 108 carried by the lower valve assembly 102. Since the under surface of the lower valve element has a larger air-contact area from below than from above, the differential pressure is effective to drive and maintain the lower valve assembly 102 in its upper position and at the same time the upper valve assembly 86 is driven and held upwardly, as indicated in FIGURE 3.. With the upper valve assembly 86 in its up position, the passageway 20 is placed in communication with the exhaust to the atmosphere through passageway 24 and opening 82.. In this manner in the normal position of the tool the fluid in the upper open end of the piston 18 is exhausted to the atmosphere. Moreover any fluid in chamber 106 or in the dashpot chamber 116 is also exhausted to the atmosphere through passageway 120 and port 122. The valve element 188 seated against the port 92 is effective to block the communication between the fluid reservoir 14 and the passageway 20.

When the operating pin 124 is depressed upwardly by manual squeezing of the trigger 129, pressurized fluid to the control chamber 140 is cut off by the seating of the valve element 132 against the opening of passageway 136 and the air from the control chamber 140 is exhausted to the atmosphere through the passageway 142, bore 134, and exhaust opening 138. Under such conditions both the upper and lower

valve stem assemblies

86 and 102 move downwardly due to the differential pressure acting on them, thereby connecting the fluid reservoir 14 to the upper end of the power cylinder 18 through the passageway 20 as best illustrated in the position of FIGURE 1.

Pressurized fluid will enter into the dashpot chamber 116 between the lower surface of the piston and the valve element 112 at a metered rate as determined by the size of the metered bleed passageway 120. The pressurized fluid entering the dashpot chamber 116 will create a pressure differential below the upper valve stem assembly 86 greater than that above the upper valve stem assembly and pressurized fluid entering the dashpot chamber 116 through the metered passageway will aid in driving the upper valve assembly 86 upwardly, closing off the pressurized fluid to drive the power piston 26 and opening the exhaust port from passageway 24 to exhaust the fluid from the upper end of the cylinder 18 to the atmosphere. At the same time any fluid in the chamber 106 will be exhausted to the atmosphere through port 122 and the tapered opening 82.

As soon as the fluid from the fluid reservoir 14 is cut off to the power cylinder 18, and the upper end of the power cylinder 18 is exhausted to atmosphere, the power piston 24 will be driven upwardly by the return action of the return mechanism. In the illustrated embodiment the compressed fluid from the air return chamber 19 will be discharged below the power piston 26 to drive the piston upwardly to its normal position in the manner heretofore described.

To complete the cycle of operation of the control valve, when the trigger 129 is released, the operating pin 124 moves down and fluid from the fluid reservoir 14 again enters the chamber 140 below the lower valve assembly 102 so that the pressure differential acting on the lower valve assembly will drive the lower valve assembly upwardly to its static position as indicated in FIGURE 3.

Although the present invention has been described by reference to only a single embodiment thereof, it will be apparent that numerous other modifications and embodiments will be devised by those skilled in the art, for example, the trigger 129 may be automatically actuated rather than manually actuated. It is intended therefore by the appended claims to cover those embodiments which will fall within the true spirit and scope of the present invention.

What is claimed as new and desired to be secured by Letters Patent of the United States is:

1. A control valve assembly for controlling a pneumatic fastener driving apparatus of the type having a power piston mounted in a power cylinder actuated in its drive stroke by the communication of the power cylinder with a fluid reservoir and automatically returned through a return stroke during the automatic sequential exhausting of the power cylinder, said control valve comprising first valve means movable between a first position exhausting said power cylinder to the atmosphere and a second position placing said power cylinder in communication with said fluid reservoir; a valve cylinder; a second valve means including a valve piston in said valve cylinder positionable to one position biasing said first valve means into said first position when said valve cylinder is connected to said fiuid reservoir and simultaneously blocking pressurized fluid from said reservoir from acting against said first valve means in a direction to bias said first valve means into said first direction, and a second position wherein pressure differential on said valve means is effective to move said first valve means to its said second position in conjunction with the movement of said second valve means; operating means controlling the position of said second valve means; and time delay means for unblocking said pressurized fluid from acting on said first valve means thereby to return said first valve means to its said first position.

2. A control valve assembly as set forth in claim 1 above and including a valve chamber having a first port communicating with the atmosphere, a second port communicating with the fluid reservoir, and a third port communicating with the power cylinder, said first and second ports respectively defining first and second valve seats; and wherein said first valve means has first and second valve element alternately coopera'ble with a respective one of said seats and movable in said valve chamber between said first position wherein said second valve element closes against said second valve seat to said second position wherein said first valve element closes against said first valve seat.

3. A control valve assembly as set forth in claim 2 above wherein said first valve means includes a valve piston, and said second valve element is carried on one end of said valve piston.

4. A control valve assembly as set forth in claim 2 above wherein said first valve means includes a valve piston, and wherein the valve piston on said second valve means abuts the valve piston on said first valve means to define a dashpot chamber therebetween, and wherein said time delay means comprises means for metering pressurized fiuid into said dashpot chamber when said valve means are in said second and said other positions respectively.

5. A control valve assembly as set forth in claim 4 above wherein said dashpot chamber is defined by a depending skirt extending from one of said valve pistons toward the other, and wherein a valve element is carried by one of said valve pistons to seal between said depending skirt and the other of said valve pistons.

6. A control valve assembly as defined in claim 4 above wherein said means for metering pressurized fluid includes a metered clearance passageway between said valve cylinder and said valve piston carried by said first valve means.

7. A control valve assembly as set forth in claim 2 above wherein said first valve means includes a valve piston and the valve piston on said second valve means abuts the valve piston on said first valve means to define a dashpot chamber therebetween, and wherein said time delay means includes means for metering pressurized fluid from said fluid reservoir into said dashpot chamber.

8. A control valve assembly as set forth in claim 2 above wherein said first valve means includes a valve piston and wherein said first valve means is provided with a recess forming a cylinder; said second valve element being cooperatively associated between said second port and the last mentioned valve piston; said second valve means having a portion telescopically received in said recess; means forming a pneumatic interface seal between the last mentioned cylinder and the last mentioned portion to define a chamber in said last mentioned cylinder above said portion; port means communicating between said last mentioned chamber and said valve chamber; said second valve means including a valve piston movable within said valve cylinder relative to the first mentioned piston, one of said pistons having a depending skirt extending toward the other, a valve element carried by one of said pistons sealing against said skirt to define a dashpot chamber; and air bleed means defining a time delay dashpot and communicating between the last two mentioned chambers.

9. A control valve assembly as set forth in claim 1 wherein said operating means includes a manually initiated operating pin movable between a depressed position exhausting said valve cylinder to the atmosphere and a normal position connecting said valve cylinder to the fluid reservoir.

10. A control valve assembly for controlling a pneumatic fastener driving apparatus of the type having a power piston mounted in a power cylinder actuated in its drive stroke by the communication of the power cylinder with a fluid reservoir and automatically driven through a return stroke by the automatic sequential exhausting of the power cylinder to the atmosphere; said control valve comprising first valve means movable between a first position exhausting said cylinder to the atmosphere and a second position placing said cylinder in communication with said fluid reservoir, second valve means positionable to one position biasing said first valve means into said first posltion; operatnig means controlling the position of said second valve means; and a lost-motion dashpot connection between said valve means effective upon release of said second valve means from said one position to permit return of said first valve means to said first position.

11. A control valve assembly for controlling a pneumatic fastener driving apparatus of the type having a power piston mounted in a power cylinder actuated in its drive stroke by the communication of the power cylinder with a fluid reservoir and automatically returned through a return stroke by the automatic sequential exhausting of the power cylinder to the atmosphere; said control valve comprising first valve means movable between a first position exhausting said cylinder to the atmosphere and a second position placing said cylinder in communication with said fluid reservoir; second valve means positionable to one position biasing said first valve means into said first position and to another position whereby pressure differential on said first valve means between said fluid reservoir and the atmosphere is effective to move said first valve means to its said second position in conjunction with the movement of said valve means; operating means controlling the position of said second valve means; and a lostmotion dashpot connection between said valve means effective upon release of said second valve means from said one position to permit a delayed return of said first valve means to said first position.

12. A snap-acting control valve assembly for controlling a pneumatic fastener driving apparatus of the type having a power piston mounted in a power cylinder actuated in its drive stroke by the communication of the power cylinder with a fluid reservoir and returned through a return stroke by the exhausting of the power cylinder to ambient pressure; said control valve comprising a valve chamber formed in the housing of said apparatus and having a first valve port and seat for communication between said chamber and ambient pressure and having a second valve port and seat for communication between said valve chamber and the fluid reservoir, another port for communicating with the power cylinder of said apparatus, valve means reciprocally movable to alternately close against a respective one of said valve seats to place said last mentioned port selectively in communication with the ambient pressure and with the fluid reservoir, fluid pressure means including a valve cylinder and piston for biasing said valve means against one of said valve seats in response to the pressure of fluid in said valve cylinder; control valve means for controlling the pressure in said cylinder by selectively connecting said cylinder to said fluid reservoir or to the atmosphere; and means automatically returning said valve means against said one of said valve seats after movement therefrom under control of said fluid pressure means.

13. A snap-acting control valve assembly for controlling a pneumatic fastener driving apparatus of the type having a power piston mounted in a power cylinder actuated in its drive stroke by the communication of the power cylinder with a fluid reservoir and returned through a return stroke by the exhausting of the power cylinder to ambient pressure; said control valve comprising a valve chamber formed in the housing of said apparatus and having a first valve port and seat for communication between said chamber and ambient pressure and having a second, opposed valve port and seat for communication between said chamber and the fluid reservoir, another port for communicating with the power cylinder of said apparatus; a valve stem assembly reciprocally movable to alternately close against a respective one of said opposed valve seats to sequentially place said last mentioned port in communication with the ambient pressure and with the fluid reservoir; said valve stem assembly including a piston and having a central recess therethrough forming a cylinder; a second valve stem assembly including a portion telescopically received in said last mentioned cylinder to provide a chamber therein; a port communicating between said chambers; a valve body; a valve cylinder formed in said valve body; said second valve stem assembly including a piston slideably received in said valve cylinder; a chamber formed between said pistons; valve means carried on one of said pistons for seating against the other of said pistons when said pistons are biased together; air bleed means communicating between said last mentioned chamber and said fluid reservoir; air bleed means communicating between the last two mentioned chambers, and means for sequentially connecting the last mentioned cylinder with the fluid reservoir and discharging the last mentioned cylinder to ambient pressure.

14. A fastener driving tool comprising a housing including a power cylinder and a fluid reservoir supplied with fluid under pressure; fastener driving means including a power piston slideably mounted in the power cylinder; a control valve assembly carried on the housing and operable to sequentially connect one end of said power cylinder between a normal position exhausting to the atmosphere and an operated position communicating with said fluid reservoir; said control valve comprising upper valve stem means movable between a first position exhausting said power cylinder to the atmosphere and a second position placing said power cylinder in communication with said fluid reservoir; a valve cylinder, a lower valve stem means including a lower piston in said valve cylinder positionable to one position biasing said upper valve stem means into said first position when said cylinder is connected to said fluid reservoir and simultaneously blocking pressurized fluid from said reservoir from acting against said upper valve stem means in a direction to bias said upper valve stem means into said first direction, and a second position wherein pressure differential on said valve stem means is eflective to move said upper valve stem means to its said second position in conjunction with the movement of said lower valve stem means; a fluid return chamber communicating with the other end of said power cylinder; a fluid bleed passageway intermediate the length of said power cylinder communicating with said fluid return chamber effective to return said power piston to its normal position upon exhaustion of fluid to the atmosphere from the said one end of said power cylinder; operating means controlling the position of said lower valve stem means; and time delay means operable to direct pressurized fluid from said fluid reservoir to act on said upper valve stem means thereby to return said upper Valve stem means to its said first position.

15. A control valve assembly for controlling a pneumatic fastener driving apparatus of the type having a power piston mounted in a power cylinder actuated in its drive stroke by the communication of the power cylinder with a fluid reservoir and automatically driven through a return stroke by the automatic sequential exhausting of the power cylinder to the atmosphere; said control valve comprising first valve means movable between a first position exhausting said cylinder to the atmosphere and a second position placing said cylinder in communication with said fluid reservoir, second valve means positionable to one position biasing said first valve means into said first position; operating means controlling the position of said second valve means; and means intercon necting said valve means effective upon release of said second valve means from said one position to provide a sequential return of said first valve means to said first position.

16. A control valve assembly for controlling a pneumatic fastener driving apparatus of the type having a power piston mounted in a power cylinder actuated in its drive stroke by the communication of the power cylinder with a fluid reservoir and automatically returned through a return stroke during the automatic sequential exhausting of the power cylinder, said control valve comprising first valve means movable between a first position exhausting said power cylinder to the atmosphere and a second position placing said power cylinder in communication with said fluid reservoir; a valve cylinder; a second valve means including a valve piston in said valve cylinder positionable to one position biasing said first valve means into said first position when said valve cylinder is connected to said fluid reservoir and simultaneously blocking pressurized fluid from said reservoir from acting against said first valve means in a direction to bias said first valve means into said first direction, and a second position wherein pressure diflerential on said valve means is effective to move said first valve means to its said second position in conjunction with the movement of said second valve means; operating means controlling the position of said second valve means; and means for 11 automatically unblocking said pressurized fluid from act- 2,989,948 ing on said first valve means thereby to return said first 2 995,114 valve means to its said first position. 3,051,135 3,094,901 References Cited 5 3,106,134 UNITED STATES PATENTS 3,173,340

2,914,032 11/1959 Powers et a1 173169 2,915,754 12/1959 Wandel 91461 X 12 Forrester 173169 Starr 173169 Smith 173169 Wandell et a1. 173169 Osborne 91454 Doyle et a1 91461 X HALL C. COE, Primary Examiner.

Claims

1. A CONTROL VALVE ASSEMBLY FOR CONTROLLING A PNEUMATIC FASTENER DRIVING APPARATUS OF THE TYPE HAVING A POWER PISTON MOUNTED IN A POWER CYLINDER ACTUATED IN ITS DRIVE STROKE BY THE COMMUNICATION OF THE POWER CYLINDER WITH A FLUID RESERVOIR AND AUTOMATICALLY RETURNED THROUGH A RETURN STROKE DURING THE AUTOMATIC SEQUENTIAL EXHAUSTING OF THE POWER CYLINDER, SAID CONTROL VALVE COMPRISING FIRST VALVE MEANS MOVABLE BETWEEN A FIRST POSITION EXHAUSTING SAID POWER CYLINDER TO THE ATMOSPHERE AND A SECOND POSITION PLACING SAID POWER CYLINDER IN COMMUNICATION WITH SAID FLUID RESERVOIR; A VALVE CYLINDER; A SECOND VALVE MEANS INCLUDING A VALVE PISTON IN SAID VALVE CYLINDER POSITIONABLE TO ONE POSITION WHEN SAID VALVE FIRST VALVE MEANS INTO SAID FIRST POSITION WHEN SAID VALVE CYLINDER IS CONNECTED TO SAID FLUID RESERVOIR AND SIMULTANEOUSLY BLOCKING PRESSURIZED FLUID FROM SAID RESERVOIR FROM ACTING AGAINST SAID FIRST VALVE MEANS IN A DIRECTION TO BIAS SAID FIRST VALVE MEANS INTO SAID FIRST DIRECTION, AND A SECOND POSITION WHEREIN PRESSURE DIFFERENIAL ON SAID VALVE MEANS IS EFFECTIVE TO MOVE SAID FIRST VALVE MEANS TO ITS SAID SECOND POSITION IN CONJUNCTION WITH THE MOVEMENT OF SAID SECOND VALVE MEANS; OPERATING MEANS CONTROLLING THE POSITION OF SAID SECOND VALVE MEANS; AND TIME DELAY MEANS FOR UNBLOCKING SAID PRESSURIZED FLUID FROM ACTING ON SAID FIRST VALVE MEANS THEREBY TO RETURN SAID FIRST VALVE MEANS TO ITS SAID FIRST POSITION.