MXPA06010919A - Control device for a power impact tool - Google Patents

Abstract

A control device for use with pneumatic tools includes a torque limiting timing device and pressure regulator, thereby improving on the accuracy of torque ultimately applied to workpieces. Pneumatic tool with a housing and motor with a control device that is in fluid communication with the tool's motor.

Description

CONTROL DEVICE FOR A POWER IMPACT TOOL BACKGROUND OF THE INVENTION This invention relates generally to the field of power impact tools and, in particular, to a control device for a power and power impact tool. very specifically to the time and pressure regulating devices. Power impact tools (eg, pneumatic, hydraulic, electrical, etc.) are well known in the art. Power impact tools produce forces on a work piece by repeatedly impacting a motor driven hammer on an anvil that is mechanically connected, directly or indirectly, to exert a force on the workpiece. Other power impact tools exert linear forces. Other power impact tools exert torque, which is a torsional force. One difficulty in the current power impact tools is the too long period during which the power is applied to the work piece. The accumulation of impacts on any piece of work that is already very tight can cause damage. The current power impact tools are turned off when the operator allows manual shutdown. For example, in a pneumatic hand tool such as a torque wrench, the operator releases the trigger valve to cut the supply of compressed air to the tool motor. The number of impact forces released to the workpiece depends on the reflections and. the attention that the operator of the tool places. During any delay, the work piece may suffer excessive torsion and be damaged. In addition, it may happen that the user operates the tool at a higher air pressure level than originally designed. For example, the user can operate the air compressor that supplies the air to the tool without any pressure regulating means. Additionally, the user operates the air compressor at a level of air pressure higher than desired. As a result, the tool finally receives a higher air pressure than desired, which can ultimately result in torque being applied higher than desired on the work pieces. Accordingly, in the field of power impact tools there is a need for means to provide more predictable amounts of torques that are ultimately applied to a workpiece. Additionally, there is a need for a control apparatus that will limit the time that a force of a power impact tool is applied to a workpiece.

Likewise, there is a need to regulate the air pressure that is ultimately provided to the tool motor. In the field of power impact tools there is a need for a device that provides a method to make the amount of torque, both in time and quantity, more predictable on the work piece. The present invention provides an apparatus and method that are used to control power impact tools. A first general aspect of the invention provides a control device for use with a pneumatic torque control tool having a motor, such a device comprising: a pressure regulator, configured to limit a maximum pneumatic pressure provided to such a motor; and a time limiting device that limits the torque, configured to close the fluid flow to such an engine at a predetermined time. A second general aspect of the invention provides a pneumatic tool comprising: a housing; an engine inside the housing; and a control device in fluid communication with the motor. The foregoing as well as other features of the invention will be apparent from the following more particular description of various embodiments of the invention. BRIEF DESCRIPTION OF THE DRAWINGS Some of the embodiments of this invention will be described in detail, with reference to the following FIGURES, in which similar designations indicate similar members, wherein: FIGURE IA illustrates a cross-sectional view of one embodiment of a power impact tool adapted to receive a control device, in accordance with one embodiment of the present invention; FIGURE IB illustrates a cross-sectional view of one embodiment of a control device, in accordance with one embodiment of the present invention; FIGURE 1C illustrates a cross-sectional view of one embodiment of a control device constructed from at least two separate blocks according to one embodiment of the present invention; FIGURE 2 illustrates a diagrammatic view of one embodiment of a control device, in accordance with one embodiment of the present invention; FIGURES 3A-C illustrate a cross-sectional view of one embodiment of a portion of a control device with the regulator and shut-off valves shown in different operating positions in accordance with the present invention; FIGURE 4 illustrates a cross-sectional view of one embodiment of a handle grip tool with a control device that is integrated within the tool housing, in accordance with the present invention; and FIGURE 5 illustrates an alternative embodiment of the control device with a fixed measuring device, in accordance with the present invention. Although certain embodiments of the present invention will be shown and described in detail, it should be understood that various changes and modifications may be made without departing from the scope of the appended claims. The scope of the present invention will in no way be limited to the number of constituent components, the materials thereof, and the forms thereof, the relative arrangement thereof, etc., and are simply described by way of example of a modality. Although the drawings are intended to illustrate the present invention, the drawings are not necessarily presented to scale. The control device is used with, or as part of, a power impact tool and allows the torque result to limit time as well as limit the air pressure finally provided to the motor of the power impact tool. Power impact tools can include various power impact tools (eg, pneumatic, hydraulic, electrical, etc.). This control device, when used with a power impact tool, for example with a pneumatic power impact tool, provides a fixed duration of the torque from the air motor inside the tool, to a workpiece , such as a nut or bolt. This control device will also effectively place a "roof" on, that is, limit, the maximum amount of air pressure that can be provided to the engine. An engine, as defined and used herein, is any device for converting a first flow of energy into kinetic energy. For example, an air motor converts the energy of a flow of compressed gas that expands to the rotational movement of the mechanical impulse shaft. In another example, an electric motor converts a flow of electricity into the rotational movement of a mechanical impulse arrow. In yet another example the pulse piston and the valves of a drilling machine form a motor for converting the energy of a compressed fluid that expands to the linear movement of a mechanical pulse arrow. In a final example, a hydraulic motor converts the kinetic energy of a fluidly compressed fluid that flows (hydraulic fluid) to the rotational movement of a mechanical impulse shaft. The impulse arrow, in each mode, is rotated by the motor, and the tools, to operate on workpieces (workpiece adapters), are connected directly or indirectly mechanically between the impulse shaft and the workpiece. of work. The control device can adopt various configurations. That is, the control device can be integrated into a new tool (for example inside the housing). Conversely, the control device can be a modular unit that can be fixed to an existing tool (for example behind the housing), or fixed to a new tool. This joint can be fixed or can be removed. In addition, the control device may be remote from the tool housing. In one embodiment, the control device is in fluid communication with the tool motor. Referring now to FIGURE 1A, a mode of a power impact tool 10 is shown in vertical section through the centerline of the tool 10. The tool 10 has a handle 12 containing a channel 50 for receiving a fluid compressible through a port 52 at the base of the handle 12. A channel is a confined path for the flow of a compressible fluid. The channels can be tubes, hoses, holes formed in a block of material, or similar flow limitations. A compressible flow, as defined and used herein, is a fluid with a volume modulus that is less than the volume module of the water. Compressible fluids with low volume modules transfer energy by converting the potential energy from its compressed state to the kinetic energy of a fluid that expands and then to the kinetic energy of a motor rotor. Elemental gases such as helium and nitrogen as well as mixed gases such as air are compressible fluids with low volume modules. The slightly compressible fluids have high volume modules and are used for force transmission. Hydraulic fluids, for example, typically have higher volume modules. Any type of compressible fluid can transfer energy to an engine. The port 52 is equipped with an adjustment 54 for connecting to a supply of compressed fluid. A compressed fluid supply may be, for example, a compressed air hose as used in a car workshop to drive pneumatic tools. Within the channel 50 there is a manually operated valve 62, which is shown in FIGURE IA as a trigger valve 62, which allows the user of the tool to regulate the flow of compressible fluid through the channel 50. By pressing the trigger 60 the valve 62 is opened thus channeling the compressible fluid towards a motor 14 of the tool 10. The channel 50 extends to a rear plate 70 of the tool where the channel 50 terminates in the port 56 sized and configured to receive (see FIGURE IB) a port 250 corresponding to a first channel 202 in a control device 600. Thus, the first channel 202 is the input channel. A control device 600 is a first apparatus that controls at least one function of at least one second apparatus. In addition, a control device 600 can be modular in that it can be manipulated as an individual physical unit (a module). The module comprises a generally solid block or body, within which the mechanisms that implement the control functions are formed. The body can be created from an individual block or constructed from a plurality of sub-blocks. The control device 600 can be manipulated in relation to a second apparatus whose interaction between the control device 600 and the second apparatus results in a change in the operation of the second apparatus. For some examples in the field of tires, a control device 600 can close the air flow to a tool 10 (a second apparatus) after a fixed time or selected by the user, can oscillate the direction of the air flow, As in a drill, you can put a roof over the maximum amount of pressure the tool motor reaches, or you can change the air pressure that enters the second appliance. The control device 600, in the embodiment shown in FIGURE IB, is configured to be removably attached to the tool 10. The apparatus is releasably secured when the user can open and close the connections between the control device 600 and the tool 10. The connectors can be bolts, jaws, pins or similar devices known in the art. In one embodiment, the connections can all be opened or closed by only one movement of the user's hand. It will be apparent that the alternative configurations of the control device 600 are part and portion of the present invention. For example, the control device 600 may be attached to the tool 10. Alternatively, the control device 600 may be remote from the tool 10, but in fluid communication with the motor 14. In addition, the control device 600 may not be modular absolute, but integrated in one or more parts of the tool 10 (for example, the housing, the handle 12, etc.).

Also on the back plate 70 is a port 58 sized and configured to receive the compressed fluid (see FIGURE IB) which is discharged from an output port 252 of a second channel 212 of the control device 600. The second channel 212 is the output channel 212. The back plate 70 can be, for example, the back plate 70 of a pneumatic torque wrench Model 749 made by the Chicago Pneumatic Tool. In one embodiment the back plate 70 has a cylindrical boss 74, which can accommodate a motor bearing. inside, which is used as an alignment mechanism for aligning the control device 600 to the tool 10. With reference to FIGURES IA and IB, in one embodiment, the control device 600 has a structure 80 that contains a dimen- sioned cavity 78 and configured to slidably receive the cylindrical protrusion 74 of the back plate 70. In one embodiment, the back plate 70 may further comprise an alignment pin 72 that is sized and configured to be slidably received in a cavity 76 in the device 600 control. In an alternative embodiment, the cavities 76 and 78 may be in the back plate 70 and the cylindrical protrusion 74 and the alignment pin 72 may be part of the control device 600. In another alternative embodiment, the rear plate 70 has at least one alignment mechanism and at least one cavity, with at least one corresponding cavity and at least one corresponding alignment mechanism integrated in the control device 600. FIGURE 2 shows a modality of a device 600 control in a partial diagram view. One embodiment of the control device 600 includes a shut-off valve 100 that can close the flow 214 of compressible fluid to the engine at a predetermined time after initiating the flow of compressible fluid through the control device 600. The control device 600 further includes a regulating valve 500 which can limit the maximum fluid pressure that is ultimately provided to the motor 14 of the tool. In the embodiment of FIGURE 2 the compressible fluid flows through an inlet port 250 into a first channel 202, through the regulating valve 500, then through an intermediate channel 502 then through the closing valve 100 open deflected, in and through a second channel 212 and discharged from port 252 to inlet 58 (FIGURE 1A) of motor 14 of tool 10. Valve 500 comprises a valve chamber 520, a valve body 514, a deflector mechanism 516 and seals 518. Valve chamber 520 has ports 550, 558 to a plurality of channels 202 and 502. First port 550 which is connected to channel 202 is located along the exterior of valve 500 above than the second port 558 that leads to the intermediate channel 502. The valve body 514 that fits slidably within the valve chamber 520 has at least one passage 530. In the embodiment shown in FIGURE 2, the valve body 514 has a degree of freedom of translatory movement. In this embodiment, the valve body 514 also has a degree of freedom of rotational movement because the valve body 514 has rotational symmetry about its axis. The rotational symmetry of the valve body 514 obviates the need for the valve body 514 to maintain a specific rotational orientation within the valve chamber 520 during operation. The degree of freedom of movement that opens and closes the valve 500 is the degree of operational freedom. In an alternative embodiment, the valve body 514 and the valve chamber 520 may not be of rotational symmetry. In other alternative embodiments, a valve 500 operates by rotary sliding instead of translation movement. Those skilled in the art will appreciate the advantages of minimizing the mass 514 of the valve body within other design limitations. The deflection mechanism 516 is any mechanism or combination of mechanisms that exerts force on the valve body 514 in a direction aligned with respect to the degree of freedom of operative movement of the valve body 514 and over at least a portion of the range of motion of the valve body 514. The deviation mechanism 516 is typically a spring, but it can be a compressible fluid or other elastic members. In the embodiment of FIGURE 2, a first end of the valve body 514 of the regulating valve 500 has an extension 508. The extension 508 is an extension of rotational symmetry of the valve body 514 with a uniform diameter and smaller than the maximum diameter of the valve body 514. The extension 508 typically has a predetermined length. When the valve body 514 is in its deviated position, the extension 508 bears against one end of the valve chamber 520 with which a chamber 532 is created. The chamber 532 (or actuator chamber) can be considered an additional extension. of the 520 valve chamber. The end surface of the valve body 514 is exposed to the pressure of the compressible fluid that can be received in the chamber 532 through at least one passage 530. The chamber 532 is in fluid communication, through the passages 530, with the ports 550, 558 and the valve chamber 520. Thus, as the fluid enters via the first channel 202 through the port 550, it also enters via the passage 530 into the chamber 532. The pressure of the fluid accumulating in the chamber 532 exerts a force on the end surface of the chamber 532. valve body 514 and extension 508 of valve body 514 and, thereby, on valve body 514 itself. This exerted pressure counteracts the deflection produced by the spring 516. The regulating valve 500 further includes a vent 561 which is an opening at atmospheric pressure. The vent 561 is in constant fluid communication with the valve chamber 520. Therefore, when the fluid enters the valve chamber 520 and finally the actuating chamber 532, it forms sufficient fluid pressure to counteract the deviation produced by the spring 516. When the fluid pressure within the actuating chamber 532 exceeds the force of the spring 516, the valve body 514 is moved such that the ports 550 are closed, effectively closing the fluid flow from the channel 202 through the regulating valve 500. However, due to the uneven relationship between port 550 and port 558, when the valve body 514 moves to close port 550, port 558 remains open to intermediate channel 502, thereby allowing the pressure of fluid is dissipated from chamber 532, passage 30 and valve chamber 520. In addition, because the regulating valve 500 is provided with a vent 561, any fluid pressure that is formed on the spring side of the valve body 514 is finally dissipated through the vent 561. After this pressure release, fluid out of port 58, the valve body 514 returns to the open position because of the deflection of the spring 516. The continuous opening of the throttle valve (see for example FIGURE 3A) which closes the fluid inlet from the channel 202 while draining the fluid pressure from within the valve 500 (see for example FIGURE 3B) and then returning / reopening the valve 500 (see, eg, FIGURE 3C) is what allows the valve The regulator "hunts" constantly a fixed maximum fluid pressure that is finally provided to the engine 14. Therefore, if the fluid pressure that is sent to the regulating valve 500 exceeds the maximum pressure of the valve 500, the valve body will continuously open and close thereby acting as a regulating device so that it does not allow fluid flow above the maximum pressure, or design, of the valve 500 to reach the engine 14 of the tool. In this way, the regulating valve 500 serves to constantly regulate the flow of fluid from the channel 202 to the intermediate channel 502 and finally to the motor 14. The amount of fluid pressure at which the regulating valve 500 operates can be a function of many. elements including the size of the spring 516 and the area of the face of the valve body 514 facing the actuating chamber 532. For example, the regulating valve 500 can be designed to regulate the air pressure that finally passes to the motor 14 to have a maximum of 90 p.s.i. That is, if the air pressure provided in the first channel 202 is, for example, 125 psi, the automatically and effectively constant regulating valve 500 limits or reduces the air pressure leaving the regulating valve 500 via the channel 502. intermediate to no more than 90 psi The valve body 514 is systematically opened and closed, as required, so as not to admit that the air flow above 90 p.s.i. reach to the engine 14. Similarly, if for example, the fluid pressure provided to the first channel 202 is only 75 p.s.i., this same valve 500 regulates the "limit of 90 p.s.i." it would never receive enough air pressure to overcome the deflection of the spring 516 and would therefore remain constantly open. The intermediate channel 502 goes from port 558 of the regulating valve 500 to port 150 of the closing valve 100. Additionally, extending from the intermediate channel 502 to the closing valve 100, there is another channel 204, designated as the "section" or "pin" channel 204. The pin channel 204 is connected to the shut-off valve 100 in the port 152. The shut-off valve 100 comprises a valve chamber 120, a valve body 114, a diverter mechanism 116 and the seals 110 and 118. The valve 120 of chamber has ports 150, 152, 154, 156, 157 and 158 with respect to a plurality of channels 502, 204, 208, 209, 210 and 212. Valve body 114 is slidably fitted within valve chamber 120 . In the embodiment shown in FIGURE 2, the valve body 114 has some degree of freedom of translation movement. In this embodiment, the valve body 114 may also have some degree of freedom of rotational movement because the valve body 114 has rotational symmetry about its long axis. The rotatable symmetry of the valve body 114 obviates the need for the valve body 114 to maintain a specific rotational orientation within the valve chamber 120 during operation. The degree of freedom of movement that opens and closes the valve 100 is the degree of operational freedom. In the alternative embodiments, the valve body 114 and the valve chamber 120 may not be rotationally symmetric. In other alternative embodiments, a valve 100 operates by rotary sliding instead of translation movement. Those skilled in the art will appreciate the advantages of minimizing the mass of the valve body 114 within other design limitations. The deflection mechanism 116 is any mechanism or combination of mechanisms that exerts force on the valve body 114 in a direction aligned with respect to the degree of freedom of operative movement of the valve body 114 and over at least a portion of the range of motion of the valve body 114. The deflection mechanism 116 is typically a spring, but may be a compressible fluid or other elastic members. In the embodiment of FIGURE 2, a first end of the valve body 114 of the closure valve 100 has a portion 108 of poppit. Portion 108 of poppit is an extension of rotational symmetry of valve body 114 with a uniform diameter and smaller than the maximum diameter of valve body 114. Portion 108 of poppit has a predetermined length 112. When the valve body 114 is in its deviated position, the poppit portion 108 is correspondingly slidably received in a tapered portion 102 of the valve chamber 120. The tapered portion 102 of the valve chamber 120 may be larger than the poppit portion 108 of the valve body 114, so as to form a chamber 104 for receiving compressible fluid from the reservoir 400. The reservoir 400 is a cavity for accumulating compressible fluid. The receiving chamber (or actuating chamber) 104 may be considered a further extension of the valve chamber 120. In an alternative embodiment, the receiving chamber 104 may be wider than the diameter of the poppit portion 108 of the valve body 114. In another embodiment, the receiving chamber 104 may be an extension of the fifth channel 208 that connects the reservoir 400 to the poppit end, or deviated end, of the valve chamber 120. In another embodiment, there is no discrete receiving chamber 104, since the narrow poppit portion of the valve chamber 120 is a port directly toward the reservoir 400. The end surface 106 of the poppit portion 108 is exposed to fluid pressure. compressible that can be received in the receiving chamber 104. The fluid pressure in the reservoir 400 exerts a force on the end surface 106 of the poppit portion 108 of the valve body 114 and, thereby, on the valve body 114 itself. The receiving chamber 104 can be considered as an expandable and contractile chamber having a movable wall, this moving wall being the end surface 106 of the poppit portion 108 of the valve body 114. In a mode wherein the valve operates by rotation, the actuating chamber 104 may be completely separated from the main chamber of the valve. The pressure of the compressible fluid at a given moment in the tank 400 depends, in the first instance, on the flow rate to the tank 400. The flow rate is controlled by a measuring device 300. The meter device 300 can be fixed or can be adjusted by the user. For example, the meter device 300 may be a fixed orifice, as illustrated in FIGURE 5, which will control the flow rate at a fixed predetermined amount depending on the attributes (eg, size, diameter, configuration, material, etc.). .) of the fixed hole 300. In this type of mode, the user can not adjust the flow rate of the meter device 300. Alternatively, the meter device 300 may be a device that allows the user to adjust and define, perhaps within certain parameters, the flow rate. One embodiment of a meter device 300 that allows the user to adjust it is a needle valve 300 ((see, for example, FIGS IB, 1C and 2) The needle valve 300 comprises a needle valve seat 304 within a third channel, a needle valve body 302 and an extension accessible to the user of the needle valve 306. The needle valve seat 304 comprises a tapered channel portion concentric to the needle valve body 302, an arrow bearing for securing the arrow of the needle valve body 302 and a seal to prevent leakage through the arrow bearing The third channel is the inlet channel to the reservoir In one embodiment the threaded extension 306 is threaded to a threaded portion 308 of the third channel 206. In an alternative embodiment, extension 306 is provided with a locking mechanism, for example: a clamping thread, to prevent vibrations caused when the tool is operated to change Adjustment The user selects the amount of time between the introduction of the compressible fluid to port 250 (e.g. by depressing trigger 60 (FIGURE IA)), and closing the poppit valve 100 when adjusting needle valve 300. The higher the flow rate, the faster the tank will reach a sufficient pressure to close the closing valve 100. Referring now to FIGS. 3A-C, at a point in the operating cycle in which the pressure of the compressible fluid in the receiving chamber 104 exerts more force on the valve body 114 than the diverter mechanism 116, the valve body 114 begins to move against the deviation (FIGURE 3A). At the boundary, or near it, between the poppit receiving portion 102 of the valve chamber 120 and the other valve chamber 120, the valve chamber has a seal 110. The seal 110 prevents pressure leakage from the receiving chamber 104 to the other valve chamber 120 while the valve body 114 moves against the deviation for the predetermined length 112 of the portion 108 of poppit. The valve body 114 moves against deflection by the force exerted on the end surface 106 of the poppit portion 108 by the compressible fluid from the reservoir 400 as it reaches the receiving chamber 104. As shown in FIGURE 3B, when the valve body 114 moves against the deviation more than the predetermined length 112 of the poppit portion 108, the seal 110 is avoided, exposing the entire area determined by the body cross section 114. from valve to pressure from reservoir 400 through receiver chamber 104. The same pressure on the increased area creates an excessive increase in the anti-deflection force, whereby the valve body 114 is hit to the anti-deflection (closed) position (FIGURE 3C). The valve body has a channel through which the compressible fluid flows 214 from the intermediate channel 502 to the second channel 212 when the valve 100 is open (FIGURE 3A). This channel is wider than ports 150 and 158 (FIGURE 2) of the valve chamber for intermediate channel 502 and second channel 212 so that flow 214 through valve 100 is not affected by the initial anti-movement. - deviation for the predetermined length 112 of the portion 108 of poppit (FIGURES 3A-B). Therefore, from the perspective of the fluid flow 214 through the valve 100, nothing happens until the valve body 114 closes (FIGURE 3C). When valve 100 closes (FIGURE 3C) port 152 and port 157 of ventilation are exposed (open) to the portion of the valve chamber 120 at the deviated end of the valve chamber 120. The deviated end of the valve chamber 120 is the end of the valve chamber 120 where the valve body 114 rests when the force exerted by the diverter mechanism 116 predominates as shown in FIGURE 3A. When the valve body 114 is in the deviated position, or within the predetermined length 112 of the poppit portion 108 of the deviated position, the port 152 and the ventilation port 157 are closed by the surfaces of the valve body 114. Ventilation port 156 is allowed to open, relative to the position of valve body 114. When the valve body 114 moves to the anti-deviation position, as shown in FIGURE 3C, the port 152 and the ventilation port 157 are open. Port 152 receives compressible fluid from pin chamber 204. The pin chamber 204 connects the intermediate channel 502 (the fluid inlet channel, FIGURE 2) to the valve chamber 120 when the valve body 114 is in the anti-deflection position (FIGURE 3C). The compressible fluid from the pin channel 204 provides sufficient pressure to "lock" the valve 100 in the anti-dive position. The vent port 157 is always open, whereby the valve chamber is ventilated when the valve body 114 is in the anti-deviation position. Therefore, when the user stops pulling the trigger 60 of the tool 14, the configuration of the port 152 and the ventilation port 157 allows the draining of any fluid, and fluid pressure, from the reservoir 400 to the atmosphere. The flow of fluid from the valve 100 and the reservoir 400 is indicated by the arrow 222. This pin channel 204, after stopping the activation of the trigger 60, allows the valve body 114 to return to the deflection, or open position ( see FIGURE 3A). The other vent port 156 in the valve chamber 120"which is always open, prevents excessive formation of fluid pressure from the spring side of the valve body 114. The vent port 156 discharges the compressed fluid to the channel 210 of the valve body. Ventilation channel 210 gives open air, in the case of a pneumatic device, or a return line in the case of compressible fluids that are not normally released into the atmosphere, such as hydraulic fluid or dry nitrogen. any mode, the venting channel 209 prevents the compressible fluid 222 and 224 as well as its excessive pressure from the valve chamber 120 and the reservoir 400 (FIGURE 2) through the fifth channel 208 and the receiving chamber 104 from dissipating. Ventilation channel 209 is narrow enough, compared to pin channel 204, for the valve 100 to remain locked while the pressure of the compressible fluid that is being dissipating exceeds the pressure exerted by the deflection spring. However, when the supply of compressible fluid is shut off, for example when the trigger 60 is released (FIGURE 1) in the present embodiment, the vent 209 dissipates 222 and 224 the pressure from the valve valve 120 and the reservoir 400, allowing that the deflection force on the valve body 114 again predominates and moves the valve body 114 back to its deviated position (FIGURE 3A). As shown in FIGS. 3A-C, the regulating valve 500 and the closing valve 100 are shown in various positions. In FIGURE 3A, the flow of fluid through both valves 500, 100 is adequate and reaches the engine 14, via the first channel 202, the intermediate channel 502 and the channel 212. FIGURE 3B illustrates how, due to the excessive Air pressure from the first channel 202, the valve body 514 in the regulating valve 500 has been closed. Likewise, FIGURE 3C illustrates how the regulating valve 500 opens again because the ventilation of the excessive air pressure via the intermediate channel 502 and the air can continue in the closing valve 100 (and further to the motor 14). of the tool in FIGURES 3A, 3B). The diverter mechanism 116 may be a spring. At the anti-deflection end of the valve chamber 120, a ring seal 118 provides a bumper for the valve body 114 as it closes. In one embodiment, the ring seal 118 can also help seal the joint between a portion of the control device 600 (FIGURE IB) that contains most of the valve chamber 120, and a second portion that forms the anti-tip end. diverted from the valve chamber 120. In the embodiment of FIGURES 3A-C, the anti-deviated end of the valve body 114 has a recess for receiving one end of a coil spring 116. The recess helps maintain the alignment of spring 116 during operation. Referring again to FIGURE 2, the first channel 202 also has a port 160 towards a third channel 206. The third channel 206 provides a restricted flow of the compressible fluid from the first channel 202 to the reservoir 400. In the embodiment of FIGURE 2 , the flow restriction is a variable flow restriction wherein the amount of flow restriction is determined by the position of a needle valve 300 adjustable by the user. An alternative embodiment includes a fixed orifice instead of a needle valve 300 adjustable by the user. The compressible fluid from the third channel 206 flows through the flow restriction to the reservoir 400. The reservoir 400 accumulates compressible fluid, increasing the pressure within the reservoir 400. The reservoir 400 has an outlet through a fifth channel 208 that leads to the portion of the receiving chamber 104 of the valve chamber 120. The pressure in the receiving chamber 104 exerts a force on an end surface 106 of the poppit portion 108 of the valve body 114. The force derived from the pressure opposes the biasing force on the valve body 114. The rate at which the tank is filled with compressible fluid is determined by the flow restriction. The closer the needle valve 300 is to close, the longer it takes for the reservoir 400 to accumulate sufficient fluid to create sufficient pressure to exert sufficient force to overcome the deflection force on the valve body 114. Therefore in the position of the needle valve 300 determines the amount of time between the start of the fluid intake (when the operator presses the trigger 60 (FIGURE IA) on a pneumatic torque wrench, for example) and the locked valve 100, which closes the motor 14 of the tool 10. In addition to minimizing the energy expended and avoiding conditions of excess torque by a tool operation limited by time, the adjustment of the valve 300 of The needle can be used to compensate for unavoidable changes in the properties of the valve spring 116 during the life of the tool 10. Likewise, the needle valve 300 can be adjusted to provide different times for different work situations. For example, tightening a twenty-point bolt thirty-two centimeters (eight inches) long would not take more time than the one required to tighten a two-point bolt fifty-four centimeters (one inch) long. Referring again to FIGS. 1A and IB, valve 100, needle valve 300 and channels 202, 204, 206, 208, 212 and 502 are contained within the modular structure 80 designed to be aligned with and attached in a manner separable to a tool 10. The alignment mechanisms 72, 74, 76 and 78 comprise means for ensuring that the input port 250 and the discharge port 252 of the control device 600 match by seal with the fluid supply port 56 and the input port 58 of the motor of the tool 10, respectively. In one embodiment, the back plate 70 of the tool 10 has a cylindrical extension 74 that fits a corresponding recess 78 in the device 600 control. The rear plate 70 is further equipped with at least one bar 72 arranged asymmetrically corresponding to at least one hole 76 in the control device 600. The bars 72 are arranged asymmetrically so that there is only one orientation of the control device 600 that allows the apparatus 600 to be received in the tool 10. That orientation is that to which the ports of the apparatus 250 and 252 and the tool are placed. they will line up properly. The fixing mechanism can be something as simple as a bolt through the control device in a threaded hole of the tool. Those skilled in the tool making art will be aware in many different ways of performing the fixation. The requirements for the fixing mechanism are that a seal is created against leakage of the compressible fluid and that it can be reused. In a particular modality, a control device 600 is integrated with a handle 12 comprising a trigger valve 62 and 60 and associated channel 50, port 52 and adjustment 54. In this embodiment, the motor 14 and the elements of a pulse train from an impulse shaft of the motor 14 to an output setting are modular and detachably attached to the integrated handle 12 and the control device 600. This mode makes all the elements that control the flow of energy to the engine 14 are in a module. In alternative embodiments the control device 600 may not be modular, ie integrated into one or more parts of the tool 10. With reference to FIGURE 1C, the body of one embodiment of the control device 600 may be manufactured with two or more blocks (also called parts or sub-blocks) 82 and 84. In one embodiment, the first block 84 is machined to contain the valve chamber 120 (FIGURE 2), the reservoir 400, the alignment holes 76 and 78, the mechanisms of fixing, the ports 250 and 252 of entry and discharge, and all the channels except the third channel 206. All the characteristics of the first block 84 can be formed by drilling and machining. The second block 82 contains the third channel 206 and the needle valve 300. The third channel 206 can be formed by drilling and machining. In assembly, the spring 116 and the bumper seal 118 are inserted before the valve body 114, and an annular chamber end 180 with the poppit seal 110 after the valve body 114. The annular chamber end 180 forms the receiving chamber 104 and the valve chamber extension 102. The installation of the needle valve 300 requires at least one seal (not shown). The assembly of the two blocks 82 and 84 closes the valve chamber 120 and the reservoir 400. The blocks 82 and 84 can be attached or fixed by bolts or by permanent means such as welding. Generally, an assembly that can be separated (bolts) is preferred, as this allows the valve 100 to be maintained and restored. FIGURE 4 illustrates a sectional elevation of a tool 10, in this particular embodiment a tool with a handle or with a handle of the sword Similarly, the control device 600 may be integrated into the tool body 10. Although this invention has been described in connection with the specific embodiments described in the foregoing, it will be apparent that many alternatives, modifications and variations will be apparent to the experts in the art.

Accordingly, the embodiments of the present invention as described in the foregoing are illustrative and not limiting. Various changes can be made without departing from the spirit and scope of the invention as defined in the following claims.

Claims (12)

1. CLAIMS 1. A control device for use with a pneumatic torque control tool having a motor, characterized in that the device comprises: a pressure regulator, configured to limit a maximum pneumatic pressure provided to such a motor; and a torque limiting time control device configured to shut off fluid flow to such a motor at a predetermined time.
2. 2. The control device according to claim 1, characterized in that the predetermined time is adjustable by the user.
3. 3. The control device according to claim 1, characterized in that the predetermined time is fixed.
4. 4. The control device according to claim 1, characterized in that the pressure regulator is a regulating valve.
5. The control device according to claim 1, characterized in that the torsion-limiting time control device is a shut-off valve.
6. The control device according to claim 1, characterized in that the device is releasably fixed to the tool.
7. The control device according to claim 1, characterized in that the device is modular.
8. The control device according to claim 1, characterized in that the device is integrated into the tool.
9. 9. The control device according to claim 1, characterized in that the device is far from the tool.
10. 10. A pneumatic tool characterized in that it comprises: a housing; an engine inside the housing; and a control device in fluid communication with the motor, wherein the control device includes a pressure regulator, configured to limit a maximum pneumatic pressure provided to the motor; and a torque limiting time controller device configured to shut off fluid flow to the engine at a predetermined time.
11. The pneumatic tool according to claim 10, characterized in that the control device is releasably fixed to the housing.
12. 12. The pneumatic tool according to claim 10, characterized in that the control device is integrated into the housing.