Improvements in or relating to trigger valves for pressurised fluid operated devices

Abstract

An actuation trigger for a device, comprising or including: a dose chamber for containing a charge of high pressure working fluid received from a high pressure source; a dose valve biased closed to seal the dose chamber from a working chamber and contain the charge in the dose chamber; a hammer operated by a piston having a driven chamber on a first side of the piston and a trigger chamber on a second side of the piston sealed from the first side, the driven chamber receiving high pressure working fluid directly or indirectly from the high pressure source; a trigger valve selectively supplying or releasing high pressure working fluid to or from the trigger chamber, such that when the hammer has high pressure working fluid in both the drive chamber and the trigger chamber, the hammer is held in a first position by a force imbalance, and when high pressure working fluid is released from the trigger chamber, the hammer is driven to or towards a second position, towards the trigger chamber, the hammer striking the dose valve when driven to or towards the second position, dislodging the dose valve to unseal the dose chamber and the working chamber, allowing the charge to enter the working chamber to do work therein.

Description

TECHNICAL FIELD

[0001] The present invention relates to triggering and valving for pressurized fluid power devices.

[0002] In particular, although not exclusively, the present invention is directed to apparatus and methods for triggering and valving for pressurized fluid power devices, whether high or low pressure, and for venting the devices. BACKGROUND

[0003] There are pressure systems that use fluid, whether high or low pressure, such as air or another gas, or a liquid, to drive a work load. The work load can be a reciprocating piston, a shot projectile, or a pressure that acts on an article with a pressure pulse. In such applications, it is necessary to introduce pressurized fluid into an area that is capable of doing work on the work load, such as a working chamber. One such method of introducing pressurized fluid to the work load is through a valve that isolates the work load directly or indirectly from a reservoir and a source of pressurized fluid. The valve opens under event action, such as triggered by an external signal. An amount of high pressure working fluid is transferred to the work load and then closed again, the high pressure working fluid begins to do work. For example, the high pressure working fluid can then expand to drive the work load down the working chamber.

[0004] Prior art pneumatic triggering systems are not suitable for generating very short instantaneous pressure pulses, they are typically valve control systems that operate in an on / off fashion. The timeframe from open to close is typically relatively long, and from the perspective of working fluid usage, this can be inefficient. The reason for the inefficiency is that a large amount of working fluid is used due to the slow opening / closing, especially considering the high pressure. Furthermore, the working fluid that is then introduced is not allowed to expand in a way that is efficient to generate work - typically not expanded by a high multiple, just filling the work cycle and pushing it. This also means that the cycle rate of such prior art systems is relatively low.

[0005] Prior art systems that achieve high cycle rates are exceptionally complex, and can suffer from early wear or inconsistent cycle times.

[0006] To date, triggering systems have additional drawbacks. For example, conventional pneumatic triggers, such as those in nail guns and the like, are typically designed to be integrated into a "tethered" system only, meaning that they do not have an "on-board" pressure supply - they do not need to use working fluid efficiently, as there is a relatively cheap, inexhaustible supply - such as from a compressor that the tool is tethered to.

[0007] Regulatory and general safety design requirements ensure portable pneumatic / mechanical systems are safe and inert when not in use, during transport, and during maintenance. To date, prior art systems have separate valve systems to accomplish this goal, which introduces complexity, part count, and cost. Additionally, incorporating additional parts and mechanisms to accomplish the "ensure safety" function is counter to those performance goals / metrics / philosophies when considering applications requiring high performance in the areas of light weight, portability, ergonomics, functional simplicity, and / or low manufacturing cost.

[0008] Additionally, such tethered systems need to be able to cut off from a separate air supply, and thus must be able to vent pressure from these systems prior to cutting off their pressure supply to enable safe cut off, ensuring system inertness. These systems will generally "back blow" any charged chambers through the pressure supply tube or pipe. Such systems are not compatible with high thermodynamic efficiency designs that allow for untethered use. These blow off valves must be integrated into the system itself.

[0009] Conventional trigger spool systems place the critical "switching" O-ring on the spool, which must necessarily be smaller in diameter than the spool bore in which it slides. This placement of the switching O-ring becomes unsuitable for high pressure applications because the sealing / sliding diameter is defined by the smallest possible spool diameter and the thickness of the seal. This means the switching O-ring is too thin to switch high pressure operating fluids in long cycles. This is because the switching O-ring (i.e. the spool bore) has a small area available. This results in a small area and thin switching O-ring, and thus a weak switching O-ring.

[0010] Opening valves is complex in high pressure applications. The forces acting can be very large, and the time frame to open such a valved control is very small. All of this must be done in a controlled repeatable manner to provide a reliable and efficient system that does the most work with the lowest volume of high pressure operating fluid.

[0011] Therefore, it is necessary to provide these systems with a reliable, robust, repeatable trigger system.

[0012] Additionally, there is a need to be able to vent pressure from behind the work load as it moves or is moved into position to do work or fire.

[0013] For example, but not limited to, when the working chamber is a closed volume, and the work load is a reciprocating piston within that chamber. Even in very efficient systems, where nearly all of the pressure in the working fluid is used as work against the work load, such as sending a piston down to the far end of the working chamber, there can still be residual pressure behind the work load (e.g. piston). This residual pressure will prevent or slow the work load (e.g. piston) from returning up the chamber to start the next cycle of work.

[0014] In another example, all the pressure from the working fluid can be utilized, but pressure builds up upon return of the workload. This could occur in a closed working chamber with a piston, or when it is open, and, for example, a projectile is frontally loaded into the chamber and pushed downwards. In examples where the working chamber can be open, the pressure behind the workload (e.g., a projectile) needs to be released because it is pushed downwards into the working chamber before being acted upon by the pressurized fluid.

[0015] The need to relieve this pressure is to allow the workload to return to the ready "launch" position, or to allow the workload to be inserted into the working chamber with minimal resistance. In other words, the return or insertion of the workload will generate increased pressure because the volume occupied by the fluid decreases when the workload is moved to the ready position.

[0016] An example of such an exhaust valve that reduces this "back pressure" is that when the port is opened by a component, the back pressure is released to the atmosphere through the inlet valve. This component opens the inlet valve and is retracted to its initial position, for example, by using residual pressurized fluid behind the workload. However, combining this opening component with the need to open the exhaust port requires a higher load than desired in some cases, because the opening component can be pushed back against springs or similar devices with sufficient force to launch it. In this application, the return of the workload may be hindered. In such applications, the exhaust port can also be opened while the pressurized fluid is still doing work on the workload. This results in inefficient use of the pressurized fluid charge, as the high pressure is released to a lower pressure environment such as the atmosphere instead of doing work on the workload. Furthermore, while it is a simple solution, it results in complex sealing and manufacturing, and makes the overall assembly less compact.

[0017] Alternative venting solutions are known that avoid the high forces and inefficiencies associated with opening the vent valve while the working fluid may still act on the workload. However, these are mechanically complex, require numerous sealing elements, and present other manufacturing and assembly challenges, making them less compact solutions overall.

[0018] In this specification, which has referenced patent specifications, other external documents, or other sources of information, this is generally for the purpose of providing background for discussing the features of the invention. Unless otherwise specifically stated, references to such external documents should not be construed as an admission that such documents or sources of information are prior art in any jurisdiction or constitute part of common general knowledge in the art.

[0019] The object of the present invention is to provide an improved trigger valve for a pressurized fluid engine or device, or to provide a reliable, repeatable trigger valve for a pressurized fluid engine, or to overcome the above-mentioned disadvantages or to satisfy the above-mentioned desires, or at least to provide a useful option for the public. SUMMARY

[0020] In a first aspect, the invention consists in an actuation trigger for a device, comprising or including:

[0021] a dose chamber for containing a charge of high pressure working fluid received from a high pressure source,

[0022] a dose valve biased closed to seal the dose chamber from the working chamber and to retain the charge in the dose chamber,

[0023] a hammer operated by a piston having a driven chamber on a first side of the piston receiving high pressure working fluid directly or indirectly from the high pressure source and a trigger chamber on a second side of the piston sealed from the first side,

[0024] a trigger valve for selectively supplying high pressure working fluid to the trigger chamber or releasing high pressure working fluid from the trigger chamber,

[0025] such that when the hammer has high pressure working fluid in both the driven chamber and the trigger chamber, the hammer is held in a first position by a force imbalance, and when high pressure working fluid is released from the trigger chamber, the hammer is driven to or towards a second position, towards the trigger chamber,

[0026] the hammer striking the dose valve when driven to or towards the second position, dislodging the dose valve to unseal the dose chamber and the working chamber, allowing the charge to enter the working chamber to do work therein.

[0027] Preferably, the force imbalance is caused by a working area of high pressure working fluid on the trigger chamber side of the piston being greater than a working area of high pressure working fluid on the driven chamber side of the piston.

[0028] Preferably, the trigger valve is a spool valve.

[0029] Preferably, when the dose valve is open from the dose chamber to the working chamber, whether via the trigger valve or otherwise, there is no supply from the high pressure source to the dose chamber.

[0030] Preferably, the trigger valve takes action to selectively release high pressure working fluid from any of the dose chamber, the driven chamber or the trigger chamber ("operating chamber") to ambient or to supply high pressure working fluid directly or indirectly to any of the dose chamber, the driven chamber or the trigger chamber, in order to trigger the device, the trigger valve having at least two positions:

[0031] a first valve position for supplying the operating chamber directly or indirectly from the high pressure source to a primed working state, wherein the trigger valve:

[0032] opening the supply to the dose chamber and closing any discharge path therefrom, and

[0033] opening the supply to the dose chamber and the trigger chamber to prepare for but not actuate the opening of the dose valve,

[0034] a second valve position for actuating the device and closing the supply from the high pressure source, wherein the trigger valve:

[0035] closing the supply to the device and in particular to the dose chamber and the trigger chamber, and

[0036] discharging the trigger chamber to ambient.

[0037] Preferably, the trigger valve has a third valve position ensuring safety of the device, wherein the trigger valve:

[0038] blocks the supply to the dose chamber,

[0039] discharges the dose chamber to ambient, and

[0040] optionally discharges one or more of the remaining operating chambers.

[0041] Preferably, when the trigger valve closes the supply to the device, the high pressure working fluid is prevented from leaving the high pressure source.

[0042] Preferably, the trigger chamber is filled prior to the dose chamber when supplied.

[0043] Preferably, the hammer slides along a first sliding axis and the dose valve slides along a second sliding axis.

[0044] Preferably, the first and second sliding axes are at least parallel and preferably concentric.

[0045] Preferably, the dose valve is an annular ring having an annular ring sealing surface sealing the dose chamber from the working chamber.

[0046] Preferably, the dose valve is biased closed by a spring.

[0047] Preferably, the hammer has a resilient element on the first and / or second side assisting or slowing down the force imbalance.

[0048] Preferably, the hammer is returned to or towards the first position at least partially by the dose valve or the return of the high pressure working fluid to the trigger chamber.

[0049] Preferably, the hammer is acted upon by the pressure in the working chamber to slow down its continued movement in the direction of the dose valve.

[0050] Preferably, the working load is:

[0051] a captured, e.g. a piston, or

[0052] an un-captured and expelled from the working chamber, e.g. a projectile, or

[0053] a pressure wave that otherwise works within the working chamber.

[0054] Preferably, the high pressure working fluid is a compressible or incompressible fluid.

[0055] Preferably, the high pressure working fluid is in the range 15 bar to 100 bar.

[0056] Preferably, the fluid is a gas.

[0057] Preferably, the working load is a captured, e.g. a piston, or un-captured and expelled from the working chamber, e.g. a projectile, or a pressure wave that otherwise works within the working chamber.

[0058] Preferably, there is an exhaust valve, wherein,

[0059] using the high pressure working fluid on the rear surface of the working load, the working load is driven on, within or from the working load from the first end of the working chamber to or towards the opposite second end of the working chamber,

[0060] fluid pressure is received into the return chamber from a front surface or region of the working load, the fluid pressure being at least partially due to the working load moving down the working chamber towards the second end,

[0061] the exhaust valve is adapted to open due to the fluid pressure in the return chamber acting on a working face of the exhaust valve, the exhaust valve when open allowing the high pressure working fluid present on the rear surface in the working chamber to be exhausted from the working chamber to a lower or ambient pressure location, the high pressure working fluid exiting via a side wall of the working chamber to the exhaust valve,

[0062] a pressure differential is thereby created from the front surface to the rear surface, returning the working load from the second end to or towards the first end.

[0063] Preferably, the exhaust valve exhausts the working fluid at an angle that is not parallel to a longitudinal axis extending between the first end and the second end, rather than substantially parallel to the longitudinal axis.

[0064] Preferably, the exhaust from the working chamber is at a right angle or close to a right angle relative to the longitudinal axis.

[0065] Preferably, the exhaust valve at least partially defines an exhaust chamber along a flow path from the side wall to the exhaust valve, prior to exhaust to the lower or ambient pressure.

[0066] Preferably, the pressure zones (front and back) of the exhaust chamber are different from each other, allowing force to be realized on the exhaust valve based on the pressure in the exhaust chamber.

[0067] Preferably, a net force acts on the exhaust valve to overcome or increase the bias to close, the net force resulting from one or both of the varying effective pressure zones or pressures on the first side of the exhaust valve in fluid communication with the back surface and / or on the second side of the exhaust valve in fluid communication with the front surface.

[0068] Preferably, the net force varies over time.

[0069] Preferably, the exhaust valve slides parallel to the longitudinal axis.

[0070] Preferably, the exhaust chamber pressure zones are at least partially realized by seals on the exhaust valve front and back, as well as inner and outer diameters.

[0071] Preferably, working fluid flows from the working chamber into the exhaust chamber, causing the exhaust chamber pressure, which keeps the exhaust valve open.

[0072] Preferably, the one or more fluid connections or the sum of these connect the working chamber to the exhaust chamber and are not the same in size or flow rate as the exhaust from the exhaust chamber to lower pressure or ambient pressure, causing different flow rates into and out of the exhaust chamber.

[0073] Preferably, the lower pressure is atmospheric or ambient surrounding the device.

[0074] Preferably, there is a check valve from the lower pressure into the return chamber.

[0075] Preferably, the check valve opens if there is a pressure imbalance between the working load front and back when the exhaust valve is open.

[0076] Preferably, the check valve is located in the exhaust valve, between the exhaust chamber and the return chamber.

[0077] Preferably, the check valve is provided by an O-ring, X-ring, lip seal or other continuous or variable cross-section sealing element that moves to block flow from the return chamber into the exhaust chamber, but allows flow from the exhaust chamber into the return chamber.

[0078] Preferably, the check valve opens when the pressure in the exhaust chamber exceeds the pressure in the return chamber, so that the exhaust chamber pressure can then be recirculated and act on the front of the working load to help drive it back to the first end.

[0079] Preferably, the return chamber is located outside of and around the working chamber.

[0080] Preferably, the exhaust valve is located at or towards the first end.

[0081] Preferably, the exhaust valve is an annular ring that is translatable along a longitudinal axis extending from the first end to the second end.

[0082] Preferably, the longitudinal axis is a principal axis of the working chamber.

[0083] Preferably, the annular ring is located outside the working chamber.

[0084] Preferably, the return chamber receives the working fluid under pressure from the working chamber via at least one fluid connection therebetween.

[0085] Preferably, a first of the at least one fluid connection is located at or towards the second end of the working chamber.

[0086] Preferably, a second of the at least one fluid connection is located between the first end and the first fluid connection.

[0087] Preferably, the second fluid connection comprises a one-way valve from the working chamber to the return chamber.

[0088] Preferably, there is a baffle within the return chamber between the working face of the exhaust valve and the fluid received from the working chamber.

[0089] Preferably, there is one or more openings in the baffle to slow the development of pressure against the working face compared to the development of pressure on the opposite side of the baffle.

[0090] In another aspect, the invention consists in a high pressure fluid operating system comprising or including:

[0091] a dose chamber for containing a charge of high pressure working fluid, the dose chamber being in fluid communication with a first side of the piston operatively connected to the hammer, and the dose chamber being in selective fluid communication with a second side of the piston,

[0092] the piston being in force imbalance at the first position when supplied with high pressure working fluid on both the first side and the second side, and

[0093] the piston being in force imbalance when the high pressure working fluid is selectively removed from the second side of the piston and urged to or towards the second position to do work.

[0094] Preferably, the hammer is held in the first position by a force imbalance from equal pressures between a trigger chamber and a driven chamber, the pressure regions in the trigger chamber and the driven chamber being different such that the net force towards the first position is greater.

[0095] Preferably, there is a resilient element on either or both the first side or the second side.

[0096] Preferably, the high pressure working fluid is a compressible fluid.

[0097] Preferably, the high pressure working fluid is in the range of 15 bar to 90 bar.

[0098] Preferably, the fluid is a gas.

[0099] Preferably, there is no supply from the high pressure source to the dose chamber when the dose valve is open from the dose chamber to the working chamber, whether via the trigger valve or otherwise.

[0100] Preferably, the device comprises an exhaust valve comprising or including:

[0101] a working load within or operable by the working chamber, the working chamber being able to selectively receive some or all of the high pressure working fluid charge from the dose chamber, using the high pressure working fluid on a rear surface of the working load, the working load being driven from a first end of the working chamber to or towards an opposite second end of the working chamber,

[0102] a fluid pressure being received into the return chamber from a front surface of the working load, the fluid pressure being at least partially due to the working load moving down the working chamber towards the second end,

[0103] the exhaust valve being adapted to open due to the fluid pressure in the return chamber acting on a working face of the exhaust valve, the exhaust valve when open allowing the high pressure working fluid present on the rear surface in the working chamber to be exhausted from the working chamber to a lower pressure location, the high pressure working fluid exiting to the exhaust valve via a side wall of the working chamber,

[0104] a pressure differential thus being created from the front surface to the rear surface, returning the working load from the second end to or towards the first end.

[0105] In yet another aspect, the present invention consists in an actuation trigger for a device, comprising or including:

[0106] a dose chamber for containing a high pressure working fluid charge received from a high pressure source,

[0107] a dose valve biased closed to seal the dose chamber from a working chamber and contain the charge in the dose chamber openable under controlled action to allow the charge to enter the working chamber,

[0108] a trigger valve selectively supplying high pressure working fluid from the high pressure source to the dose chamber and controlling the opening and closing of the dose valve whether directly or indirectly,

[0109] wherein there is no supply from the high pressure source to the dose chamber when the dose valve is open from the dose chamber to the working chamber, whether via the trigger valve or otherwise.

[0110] Preferably, the slide valve has:

[0111] a first valve position for supplying the dose chamber from the high pressure source, directly or indirectly, to a primed state, wherein the trigger valve:

[0112] opens the supply to the dose chamber and closes any drain path therefrom, and

[0113] opens the supply to any other operating chamber to prepare but not actuate the opening of the dose valve,

[0114] a second valve position for actuating the device and closing the supply from the high pressure source, wherein the trigger valve:

[0115] closes the supply to the device and in particular to the dose chamber, and

[0116] allows the other operating chamber to actuate the opening of the dose valve.

[0117] Preferably, the trigger valve has a third valve position for ensuring the safety of the device, wherein the trigger valve:

[0118] blocks the supply to the dose chamber, and

[0119] drains the other operating chamber.

[0120] Preferably, there is an exhaust valve comprising or including:

[0121] a working load within a working chamber, using pressurised fluid on a rear surface of the working load, the working load being driven from a first end of the working chamber to or towards an opposite second end of the working chamber,

[0122] a fluid pressure being received into a return chamber from a front surface of the working load, the fluid pressure being at least partially due to the working load moving down the working chamber towards the second end,

[0123] the exhaust valve being adapted to open due to the fluid pressure in the return chamber acting on a working face of the exhaust valve, the exhaust valve when open allowing the high pressure working fluid present on the rear surface in the working chamber to exit the working chamber to a lower pressure location via a side wall of the working chamber,

[0124] therefore creating a pressure differential from the front surface to the rear surface, thereby returning the working load from the second end to or towards the first end.

[0125] In another aspect, the invention consists in an actuation trigger for a device comprising or including:

[0126] a trigger valve for selectively controlling the supply of high pressure working fluid from a high pressure source to one or more operating chambers to in turn control a working chamber that uses a charge of high pressure working fluid to act on a working load, wherein the trigger valve has:

[0127] a first valve position for supplying one or more operating chambers from a high pressure source directly or indirectly to a pre-charge state, wherein the trigger valve:

[0128] opens the supply to one or more operating chambers, and

[0129] closes any drain path from it to ambient pressure to prepare the working chamber for work, but not for working the working chamber,

[0130] a second valve position for actuating the device, wherein the trigger valve:

[0131] closes or opens the supply to one or more operating chambers to allow the working chamber to be charged and work,

[0132] a third valve position for ensuring the safety of the device, wherein the trigger valve:

[0133] closes the supply from a high pressure source to one or more operating chambers, or

[0134] unloads one or more operating chambers to ambient pressure, thereby rendering the device inoperable or inert.

[0135] Preferably, the trigger valve is any one or more of a rotary valve (whether a ball or otherwise), a spool valve, a two-way or multi-way directional control valve, or any combination thereof.

[0136] Preferably, one or more operating chambers control a charge valve to deliver a charge into a working chamber.

[0137] Preferably, there is a vent valve, wherein,

[0138] using high pressure working fluid on a rear surface or area of the working load, the working load is driven within or from the working chamber from a first end of the working chamber to or towards an opposite second end of the working chamber,

[0139] fluid pressure is received into a return chamber from a front surface or area of the working load, the fluid pressure being at least partially due to the working load moving down the working chamber towards the second end,

[0140] The exhaust valve is adapted to open due to fluid pressure in the return chamber acting on a working face of the exhaust valve, the exhaust valve when open allowing high pressure working fluid present on the back face in the working chamber to exit the working chamber to a lower pressure location via the side wall of the working chamber,

[0141] A pressure differential is thus created from the front face to the back face, returning or moving the working load from the second end to or towards the first end.

[0142] Preferably, there is no direct path from the high pressure source to the working chamber, regardless of the position of the trigger valve.

[0143] In yet another aspect, the present invention consists in an apparatus comprising or including:

[0144] a dose chamber for containing a charge of high pressure working fluid received from a high pressure source,

[0145] a dose valve biased closed to seal the dose chamber from the working chamber and to retain the charge in the dose chamber,

[0146] a hammer operated by a piston having a driven chamber on a first side of the piston receiving high pressure working fluid directly or indirectly from the high pressure source and a trigger chamber on a second side of the piston sealed from the first side,

[0147] a trigger valve for selectively supplying high pressure working fluid to the trigger chamber or releasing high pressure working fluid from the trigger chamber,

[0148] such that when the hammer has high pressure working fluid in both the driven chamber and the trigger chamber, the hammer remains force unbalanced in the first position, and when high pressure working fluid is released from the trigger chamber, the hammer is driven to or towards the second position, towards the trigger chamber,

[0149] the hammer striking the dose valve when driven to or towards the second position, de-seating the dose valve to unseal the dose chamber and the working chamber, allowing the charge to enter the working chamber to do work therein.

[0150] Preferably, the force unbalance is caused by a working area of high pressure working fluid on the trigger chamber side of the piston being greater than a working area of high pressure working fluid on the driven chamber side of the piston.

[0151] Preferably, the trigger valve is a spool valve.

[0152] Preferably, the trigger valve is triggered to selectively discharge high pressure working fluid from any of the dose chamber, the slave chamber or the trigger chamber ("operating chamber") to the ambient environment or to supply high pressure working fluid directly or indirectly to any of the dose chamber, the slave chamber or the trigger chamber to trigger the device, the trigger valve having at least two positions:

[0153] a first valve position for supplying the operating chamber from the high pressure source directly or indirectly to a ready to work state, wherein the trigger valve opens the supply to:

[0154] the slave chamber and the trigger chamber,

[0155] the dose chamber and closes any discharge path from any of them, and

[0156] a second valve position for actuating the device and closing the supply from the high pressure source, wherein the trigger valve:

[0157] closes the supply to the device and in particular to the dose chamber and the trigger chamber, and

[0158] discharges the trigger chamber to the ambient environment.

[0159] Preferably, the trigger valve has a third valve position for ensuring safety of the device, wherein the trigger valve:

[0160] blocks or closes the supply to the dose chamber and the trigger chamber,

[0161] discharges the dose chamber, and

[0162] discharges the trigger chamber.

[0163] Preferably, the trigger valve closes the supply to the device and the high pressure working fluid is blocked from leaving the high pressure source.

[0164] Preferably, the trigger chamber is filled before the dose chamber when supplied.

[0165] Preferably, the hammer slides along a first sliding axis and the dose valve slides along a second sliding axis.

[0166] Preferably, the first sliding axis and the second sliding axis are at least parallel and preferably concentric.

[0167] Preferably, the dose valve is an annular ring having an annular ring sealing surface sealing the dose chamber from the working chamber.

[0168] Preferably, the dose valve is biased closed by a spring.

[0169] Preferably, the hammer has an elastic element on the first side and / or the second side assisting or slowing down the force imbalance.

[0170] Preferably, the hammer is returned to or towards the first position at least partly by the return of the dose valve or high pressure working fluid to the trigger chamber.

[0171] Preferably, the work is a load and acts on the load, the load being:

[0172] captured within the working chamber, e.g. a piston or the like, or

[0173] not captured and expelled from the working chamber, e.g. a projectile or the like, or

[0174] a pressure wave that otherwise works within the working chamber.

[0175] Preferably, the high pressure working fluid is a compressible fluid.

[0176] Preferably, the high pressure working fluid is in the range 15 bar to 90 bar.

[0177] Preferably, the high pressure working fluid is a gas.

[0178] Preferably, there is an exhaust valve, comprising or including:

[0179] a working load that works on, within or from the working chamber using the high pressure working fluid on the rear face of the work, the working load being driven from a first end of the working chamber to or towards an opposite second end of the working chamber,

[0180] a fluid pressure received into the return chamber from the front face of the working load, the fluid pressure being at least partly due to the working load moving down the working chamber towards the second end,

[0181] the exhaust valve being adapted to open due to the fluid pressure in the return chamber acting on the working face of the exhaust valve, the exhaust valve when open allowing the high pressure working fluid present on the rear face in the working chamber to be exhausted from the working chamber to a lower pressure location, the high pressure working fluid exiting via the side wall of the working chamber to the exhaust valve,

[0182] a pressure differential thus being created from the front face to the rear face, returning the working load from the second end to or towards the first end.

[0183] In another aspect, the invention consists in a method of actuating a device, comprising or including the steps of:

[0184] filling the dose chamber with a charge of high pressure working fluid,

[0185] filling the driven chamber on the first side of the hammer with high pressure working fluid,

[0186] filling a trigger chamber on a second side of the hammer with high pressure working fluid, the first and second sides being separated by a piston operably connected to the hammer such that the hammer is force imbalanced in the first position,

[0187] releasing the high pressure working fluid from the trigger chamber to drive the hammer to or towards the second position,

[0188] actuating the dose valve by the hammer striking the dose valve to dislodge the dose valve from a sealed position, in which the dose valve seals the dose chamber from the working chamber, to an unsealed position such that charge enters the working chamber to do work therein, when the dose valve is in or towards the second position.

[0189] Preferably, the force imbalance is provided or mitigated at least in part by a biasing member such as a spring.

[0190] Preferably, the step of returning the hammer to or towards the first position is at least in part by the dose valve acting on a part of the hammer or return of the high pressure working fluid to the trigger chamber.

[0191] Preferably, the high pressure working fluid is supplied directly or indirectly from a high pressure source.

[0192] Preferably, the method comprises the step of filling the driven chamber directly or indirectly from a high pressure source.

[0193] Preferably, the method comprises the step of selectively filling the trigger chamber and the dose chamber or releasing the trigger chamber and / or the dose chamber via a trigger valve.

[0194] Preferably, the trigger valve is a spool valve.

[0195] Preferably, the trigger valve acts to selectively release high pressure working fluid from any of the dose chamber, the driven chamber or the trigger chamber ("operational chamber") to ambient or to directly or indirectly supply high pressure working fluid to any of the dose chamber, the driven chamber or the trigger chamber to fire the device, the trigger valve having at least two positions:

[0196] a first valve position for directly or indirectly supplying the operational chamber from a high pressure source to a primed working state, wherein the trigger valve:

[0197] opens supply to the dose chamber and closes any discharge path therefrom, and

[0198] opens supply to any other chamber to prepare but not actuate opening of the dose valve,

[0199] a second valve position for firing the device and closing supply from the high pressure source, wherein the trigger valve:

[0200] shutting off the supply to the device and in particular to the dose chamber and the trigger chamber, and

[0201] allowing the operation chamber to actuate the opening of the dose valve.

[0202] Preferably, the trigger valve has a third valve position which ensures the safety of the device, wherein the trigger valve:

[0203] blocks the supply to the dose chamber, and

[0204] discharges the other chambers.

[0205] Preferably, the method comprises the step of: when the dose valve is open from the dose chamber to the working chamber, whether via the trigger valve or otherwise, there is no supply from the high pressure source to the dose chamber.

[0206] Preferably, the method comprises: providing an exhaust valve, including or comprising the step of:

[0207] using the high pressure working fluid on the back surface of the working load, by work within or from the working chamber, to drive the working load from a first end of the working chamber to or towards an opposite second end of the working chamber,

[0208] receiving fluid pressure from the front surface of the working load into the return chamber, the fluid pressure being at least partially due to the working load moving down the working chamber towards the second end,

[0209] opening the exhaust valve due to the fluid pressure in the return chamber acting on a working face of the exhaust valve, the exhaust valve when open allowing the high pressure working fluid present on the back surface in the working chamber to exit the working chamber to a lower pressure location, the high pressure working fluid exiting via a side wall of the working chamber to the exhaust valve,

[0210] thereby creating a pressure differential from the front surface to the back surface, returning the working load from the second end to or towards the first end.

[0211] Preferably, the exhaust valve exhausts the fluid pressure at an angle that is not parallel to a longitudinal axis extending between the first end and the second end, rather than substantially parallel to the longitudinal axis.

[0212] Preferably, the exhaust from the working chamber is at a right angle or close to a right angle relative to the longitudinal axis.

[0213] Preferably, the exhaust valve is at least partially defined along a flow path from the side wall to the exhaust valve, prior to the exhaust to the lower pressure.

[0214] Preferably, the pressure regions (front and back) of the exhaust chamber are different to each other, thereby allowing a force to be realised on the exhaust valve based on the pressure in the exhaust chamber.

[0215] Preferably, the net force acting on the exhaust valve to overcome or increase the bias to close is generated by one of both of the varying effective pressure area or pressure on the first side of the exhaust valve in fluid communication with the back surface and / or on the second side of the exhaust valve in fluid communication with the front surface.

[0216] Preferably, the net force varies over time.

[0217] Preferably, the exhaust valve slides parallel to the longitudinal axis.

[0218] Preferably, the exhaust chamber pressure area is achieved at least in part by the seals on the front and back of the exhaust valve and the inner and outer diameters.

[0219] Preferably, the fluid pressure flows from the working chamber into the exhaust chamber causing the exhaust chamber pressure which keeps the exhaust valve open.

[0220] Preferably, the one or more fluid connections or the sum of these connect the working chamber to the exhaust chamber and are not the same size or flow as the exhaust which connects the exhaust chamber to lower pressure or ambient pressure, thereby causing a different flow into and out of the exhaust chamber.

[0221] Preferably, the lower pressure is atmospheric or ambient surrounding the device.

[0222] Preferably, there is a check valve from the lower pressure into the return chamber.

[0223] Preferably, the check valve opens if there is a pressure imbalance between the front and back of the working load when the exhaust valve is open.

[0224] Preferably, the check valve is located in the exhaust valve between the exhaust chamber and the return chamber.

[0225] Preferably, the check valve is provided by an O-ring, X-ring, lip seal or other continuous or variable cross-section sealing element that moves to block flow from the return chamber into the exhaust chamber but allows flow from the exhaust chamber into the return chamber.

[0226] Preferably, the check valve opens when the pressure in the exhaust chamber exceeds the pressure of the return chamber, so that the exhaust chamber pressure can then be recirculated and act on the front of the working load to help drive it back to the first end.

[0227] Preferably, the return chamber is located outside of and around the working chamber.

[0228] Preferably, the working load is captive within the working chamber, such as but not limited to a piston, or is non-captive and expelled from the working chamber, such as but not limited to a projectile, or is a pressure wave that otherwise does work within the working chamber.

[0229] Preferably, the exhaust valve is located at or towards the first end.

[0230] Preferably, the exhaust valve is an annular ring that is translatable along a longitudinal axis extending from the first end to the second end.

[0231] Preferably, the longitudinal axis is a primary axis of the working chamber.

[0232] Preferably, the annular ring is located outside the working chamber.

[0233] Preferably, the return chamber receives the working fluid under pressure from the working chamber via at least one fluid connection therebetween.

[0234] Preferably, a first of the at least one fluid connection is located at or towards the second end of the working chamber.

[0235] Preferably, a second of the at least one fluid connection is located between the first end and the first fluid connection.

[0236] Preferably, the second fluid connection comprises a one-way valve from the working chamber to the return chamber.

[0237] Preferably, there is a baffle within the return chamber between the working face of the exhaust valve and the fluid received from the working chamber.

[0238] Preferably, there is one or more openings in the baffle to slow the development of pressure against the working face compared to the development of pressure on the opposite side of the baffle.

[0239] In another aspect, the invention consists in an actuation trigger for a device as described herein with reference to any one or more of the accompanying drawings.

[0240] In another aspect, the invention consists in a high pressure working fluid operated system as described herein with reference to any one or more of the accompanying drawings.

[0241] In another aspect, the invention consists in a device as described herein with reference to any one or more of the accompanying drawings.

[0242] In another aspect, the invention consists in a method of actuating a device as described herein with reference to any one or more of the accompanying drawings.

[0243] As used herein, the term "and / or" means "and", or "or", or both.

[0244] As used herein, the term "(s)" following a noun means the plural and / or singular form of that noun.

[0245] As used in the present specification, the terms "comprise", "comprising", "include", "including" or "has" are meant to be interpreted as "including but not limited to". As used in the present specification, the term "consisting essentially of means "comprising at least the specified components of which the essential characteristics are not altered". When interpreting each statement in this specification that includes one or more statements of incorporation by reference, each of the incorporated materials can be employed in the practice of the application, but need not. When interpreting statements in this specification that include more than one recited claim, the term "consisting essentially of means that the claim is limited to the specified components of which the essential characteristics are not altered.

[0246] References to a numerical range, for example, 1 to 10, disclosed herein are also intended to incorporate reference to all rational numbers within that range, for example, 1, 1.1, 2, 3, 3.9, 4, 5, 6, 6.5, 7, 8, 9, and 10, as well as rational numbers within any range of that range, for example, 2 to 8, 1.5 to 5.5, and 3.1 to 4.7.

[0247] The entire disclosure of all applications, patents and publications, to the extent any are cited in the above description, is hereby incorporated by reference.

[0248] The application can also be said broadly to consist in the parts, elements and features referred to or indicated in the specification of the application, individually or collectively, and any or all combinations of any two or more of said parts, elements and features, and where specific integers are mentioned in this specification and are preceded by the term "comprising", the combination of features is not limited to that combination per se but the application is not to be limited in this respect to that combination per se but the application is to be interpreted as also including any other combination of the features mentioned in this specification, individually or in any combination.

[0249] Other aspects of the application can become apparent from the following description which is given by way of example only and with reference to the accompanying drawings. BRIEF DESCRIPTION OF DRAWINGS

[0250] A preferred form of the present application will now be described with reference to the accompanying drawings, in which:

[0251] Figure 1 A vertical section through a pressurised fluid power device is shown, the device incorporating an exhaust valve for use with the present application, the exhaust valve being closed, the working load being to or towards the first end ready to work,

[0252] Figure 2 A similar view is shown with the working load having moved down the working chamber under the action of the working fluid and the pressure generated by this movement having actuated the exhaust valve to open, Figure 1

[0253] Figure 3 A similar view is shown with the working load having moved down the working chamber under the action of the working fluid and the pressure generated by this movement having actuated the exhaust valve to open, Figure 1

[0254] Figure 3 ​​B, just as the work load starts to move down the work chamber, the check valve closes, and

[0255] Figure 3 C, the work load is moving back up the chamber and if there is any pressure differential between the front and back of the work load, the check valve will open,

[0256] Figure 3 D showing a reed valve performing the check valve function, and

[0257] Figure 4 A similar view showing a vertical section along the longitudinal axis of the air engine of the invention with trigger valve, showing a further variant of the exhaust valve incorporating a check valve, the air engine being in a pre-armed state, the exhaust valve closed, and the work load pre-armed to be fired,

[0258] Figure 5 A similar view to Figure 4 but in which the trigger valve has been actuated to a second valve position to release the hammer to strike the dose valve and charge the work chamber, sending the work load down the work chamber towards the second end, and the exhaust valve opening under the pressure of the return chamber to allow the pressure behind the work load to vent to atmosphere, the exhaust port on one side of the work chamber being clearly visible,

[0259] Figure 6 A similar view to Figure 5 in which the hammer and piston are pre-armed to return to the pre-strike position, and the work load is returning up the work chamber,

[0260] Figure 7 A similar view to Figure 6 but in which the one-way check valve in the exhaust valve has opened to allow recirculation to the return chamber,

[0261] Figure 8 A close-up arrangement of the trigger valve of Figure 4 in which the trigger valve is in a pre-triggered state or first valve position, and the trigger valve train is pressurised from a high pressure source,

[0262] Figure 9 A close-up arrangement of the trigger valve of Figure 4 in a pre-triggered state or first valve position, showing the trigger / tipping chamber being charged and retaining the hammer back via the hammer piston, the trigger valve train supplying high pressure working fluid from the dose chamber and high pressure source to the tipping chamber,

[0263] Figure 10 A close-up arrangement of the trigger valve of Figure 5A close-up of the arrangement of the trigger valve shows the trigger valve in the second valve position, and the valve system is now open to dump the high-pressure working fluid from the dump / trigger chamber, thereby allowing the pressure-driven hammer in the driven chamber to strike, and opening the dosing valve to fill the working chamber (the working load has moved down the working chamber under the action of the pressurized fluid packing).

[0264] Figure 11 A close-up cross-sectional view of another variation of the trigger valve arrangement is shown, used to control the dumping of the dumping chamber in the following situations: (A) at the sealing element on the trigger valve piston, (B) at the discharge port of the spool valve orifice of the trigger valve piston, and (C) when feeding the dumping chamber through the delivery port of the dosing chamber, and

[0265] Figure 12 It shows the relationship with Figure 8 A similar view, but with a trigger valve in the third valve position to ensure device safety, allowing the high-pressure working fluid in the dosing chamber to be discharged into the surrounding environment, and optionally triggering the chamber and the driven chamber to prevent the hammer launcher from entering the dosing valve. Detailed Implementation

[0266] Reference Figures 1 to 12 The preferred embodiments of the present invention will be described below.

[0267] Figure 1 In and more specifically in Figure 4 The diagram illustrates a device 1 operating on a high-pressure working fluid, with the example shown being from a nail gun or fastening gun. However, this arrangement can be used in any device that utilizes a high-pressure working fluid (also interchangeably referred to herein as high-pressure fluid) to perform work on a workload.

[0268] It will be understood that the high-pressure working fluid can be a highly compressed gas, liquid, or other working material flowing under high pressure. In a preferred embodiment of the invention, the high-pressure working fluid is a non-flammable fluid within the operating range of the fluid to which the invention applies.

[0269] The device 1 consists of a workload 4, which is received in a working chamber 3. The working chamber is partially defined by sidewalls 31. In this example, the working chamber is a working chamber with a constant cross-section and is cylindrical, integrated with the sidewalls 31. However, the working chamber 3 can be a working chamber with a cross-section different from a circle and can take any necessary shape, such as, but not limited to, elliptical, square, or other shapes. In most instances, the working chamber will be a working chamber with a constant cross-section along its length. However, in some specialized applications, the cross-section can be changed, and the workload will be able to accommodate such a change in cross-section.

[0270] As shown, the workload 4 can be, for example, a piston used in fastening guns (such as nail guns) or in pest control traps, and is therefore a capture type. Alternatively, the workload 4 can be non-capture type, such as a projectile fired from the working chamber 3, or a pressure wave utilized in other ways.

[0271] In the example shown, the workload 4 is a piston 22, which also carries a striker or anvil 43. Due to the movement of the workload 4, the striker or anvil 43 can perform work on a fastener (e.g., a nail). Alternatively, the striker can be in different forms to achieve different results; for example, it can be flat or otherwise contoured to take action to repel pests by delivering energy to organic or inorganic matter.

[0272] In other forms, the device can perform work by releasing high-pressure working fluid packing material into or from the working chamber. This work can be a pressure wave from the device, affecting a physical object as a working load within the working chamber, whether as a capture by a reciprocating piston or as a projectile being removed or expelled from it. Alternatively, the work can be transmitted from or from the working chamber to exert influence on the exterior of the equipment.

[0273] The working chamber 3 and the device 1 have a first end 5 and a second end 8, and the working load 4 has a rear surface 9 and a front surface 7. The working load 4, in the process of doing work, moves from the first end 5 to the second end 8.

[0274] As shown, a return chamber 10 exists. In a preferred embodiment, as shown, the return chamber 10 is annular and surrounds the working chamber 3. In this arrangement, for example... Figure 2 As shown, the outer or external surface of the sidewall 31 defines a portion of the return chamber 10. However, the return chamber 10 may take other forms and may only partially surround the working chamber 3, may not be partially defined by the sidewall, or may be separate from it. For example, although not shown, the return chamber may be a separate volume that is fluidly attached to the working chamber only by a flexible or other means of conduit.

[0275] The return chamber 10 is in fluid communication with the working chamber 4 at least from the vicinity of the second end 8. In the example shown, there are two fluid communication paths: a first fluid communication path 17 adjacent to or toward the second end 8, and a second fluid communication path 18 midway between the second end 8 and the first end 5.

[0276] The working surface 28 of the exhaust valve 2 is fluidly connected to the return chamber 10, such as... Figure 1 As shown. Valve component 37 (e.g., as...) Figure 2The O-ring 34 seen forms part of the working face 28. In the example shown, the exhaust valve 2 is annular and can slide back and forth along a valve slide axis, which in this case is the longitudinal axis 15 of the device. The longitudinal axis in this case is the axis parallel to the line of motion, or the slide axis of the working load. In the embodiment shown, this also happens to be the central principal axis of the working chamber. The working face 28 is that face or those faces having a surface normal parallel to the valve slide axis, which in this example is the longitudinal axis 15, as these are the faces upon which pressure acts and will produce a resultant force in the direction of the valve slide axis of the exhaust valve. In other words, the working face, in some instances referred to as the effective face or effective area, is that face or those faces lying in a plane perpendicular to the slide axis of the component upon which they act, such as the valve or piston.

[0277] However, in other forms, the exhaust valve 2 need not be an annular ring and need only be fluidly connected to perform the exhaust valve function described. For example, the exhaust valve can be fluidly connected to perform the same function as described here, but not physically connected to the body, but can be, and can also be a spool valve or the like.

[0278] As Figure 1 Seen, the exhaust valve 2 is normally biased closed by a biasing member 29, such as a spring. As Figure 1 Seen, the exhaust valve 2 in the closed position 11 closes the outlet 30 of the side wall 31 of the working chamber 3. Thus, the outlet or exhaust port of the working chamber 3 for this and other embodiments passes through the side wall at a right angle or near right angle to the longitudinal axis of the device 1, or at least not parallel to the longitudinal axis.

[0279] In the embodiment shown and preferably in all embodiments, the exhaust valve 2 receives exhaust through the side wall 31 of the working chamber 3, and preferably the exhaust then exits through a side of the device 1 via the exhaust port 32. However, in other forms, the outlet for the exhaust can be through another area of the device 1, but at least from the side wall of the working chamber.

[0280] In a further variation, although not shown, the exhaust port can be parallel with the hammer, but offset from the central axis by the back wall 77. Such a variation can use a spool valve (similar to a spool valve of a trigger valve) rather than the annular ring exhaust valve described above.

[0281] However, exhaust valve 2 can be a separate valve arrangement actuated from return chamber 10. For example, although not shown, it can be a separate ring piston valve, or other type of valve, such as a spool valve acting parallel or at an angle to working chamber 3 or return chamber 10. Similarly, although return chamber is shown as an annular chamber around working chamber, it can be a separate volume, in turn connected to an exhaust valve as mentioned above. Such an arrangement can be desirable for many reasons, for example but not limited to, when the arrangement does not need to be so compact or space limitations prevent it.

[0282] When in the open position 12 as Figure 2 shown, the leftward sliding of exhaust valve 2 provides a path of exit or flow of high pressure working fluid (even though the pressure is reduced after doing work) from working chamber 3, through exhaust valve port 33, via outlet 30, to exhaust 32, as shown by the arrows, as compared to the position of exhaust valve 2. Figure 1 In the preferred form, exhaust 32 is at or to a lower pressure, for example to atmosphere or ambient environment 14. Exhaust 32 as shown here is an opening in housing 36 of device 1.

[0283] In some examples, there can be a lower pressure on front surface 7 as compared to back surface 9, that is, a pressure differential in favor of back surface 9, or even a pressure balance, as the working load moves or returns to the first end 5 to the ready position. This is particularly so in the case of high speed movement of the working load, and the dynamic effects of the working fluid prevent pressure equalization or leakage that would otherwise occur in slow speed operation. This pressure on the front surface can be the same fluid as the high pressure working fluid, or it can be different. For example, the high pressure working fluid can be compressed carbon dioxide, and the fluid on the front surface can be ambient environment fluid, such as air.

[0284] This pressure differential or balance will resist movement of working load 4 to first end 5. This is because as working load 4 moves back to first end 5, the working fluid there is trapped and compressed as working load 4 moves. Since return chamber 10 and front surface 7 are normally closed volumes, this will reduce the consistency, at least the speed, of return to the ready position at first end 5, and can even completely prevent return of the working load.

[0285] As Figure 3 A to Figure 3As shown in D, in this case, a one-way valve or check valve 23 may be present, such as the reed valve 24 shown. The reed valve (as shown is a flat-section elastic ring) is biased outward by its own elastic properties to properly close the chamber port 35. This allows the lower pressure outside the return chamber 10, or at least behind the front surface 7, to enter the return chamber 10 evenly through the chamber port 35 and reach the front surface 7, eliminating any pressure imbalance with the rear surface 9. The valve 24 is adjusted or selected so that it opens under the desired pressure differential.

[0286] At least Figure 2 and Figure 5 A one-way valve 19 is shown, connecting the working chamber to the return chamber. This valve is effective when exposed to any residual pressure following the working load 4, such as... Figure 2 and Figure 5 As shown, when the workload 4 has traveled to or toward the second end 8, the check valve opens. If any residual pressure is present, this will be allowed to pass from the working chamber 3 to the return chamber 10 via the check valve 19. Thus, the device can capture and utilize any existing pressure that has done work to return the workload 4 to the first end 5 while moving the workload to or toward the second end.

[0287] In a completely sealed system, this should theoretically not happen. However, in reality, this can occur if there is an air leak, for example, from the front of the front surface 7 through the anvil opening 45 as the workload travels downward toward the second end, or through a seal at that location or elsewhere to the surrounding environment or atmosphere. Such a check valve 23 is used if there is an undesirable pressure imbalance that would prevent the workload from returning.

[0288] Figures 4 to 12 Actuation was shown Figures 1 to 3 The device and therefore also actuates the trigger valve arrangement of the exhaust valve, shown in the diagram and the exhaust valve thereby actuated, albeit indirectly. In this variant, a one-way valve is built into the exhaust valve 2, and in effect allows recirculation back to the return chamber 10.

[0289] Figures 1 to 3 The general architecture of the variant shown is retained, with exhaust valve 2 (section line (in) Figure 4 Add) in moving and in Figure 5 , Figure 6 , Figure 9 and Figure 10 The open position 12 shown has an exhaust chamber 21. When the exhaust valve 2 is opened 12, such as... Figure 9 As shown, the exhaust chamber 21 is fluidly connected to the outlet 30 in the side wall 31 of the working chamber 3 via the exhaust valve port 33. Figure 9 andFigure 10 As shown, the exhaust chamber 21 has a leak path, or a flow differential with the exhaust port 32. This flow path differential or leak path between the exhaust chamber 21 and the exhaust port 32 is adjusted to create sufficient pressure in the exhaust chamber 21 to overcome the biasing member 29. In the case where the biasing member 29 has a very low spring constant, then the path differential or leak path also only needs to be small to generally be sufficient force.

[0290] Thus, when the exhaust valve 2 is actuated open, the working fluid (which is otherwise trapped between the back face 9 and the working chamber 3) can now exit the working chamber 3 as the working load 4 returns to the first end 5. Thus, a pressure differential is created between the front face to the back face, favoring an increase in pressure on the front face to return the working load from the second end to or towards the first end when the exhaust valve is open.

[0291] The actuation of the trigger dose valve 48 needs to be triggered to deliver the working fluid 6 from the dose chamber 52 to the working chamber to drive the working load 4 of these variants of the device 1. Figures 1 to 12 This is controlled by the trigger valve 50 arrangement as shown in Figures 4 to 12 and shown in more detail in combination with the hammer 46 in Figures 8 to 12 .

[0292] The device has pressurized fluid (e.g., working fluid 6) that drives the hammer 46 as shown in detail in Figure 8 . The hammer 46 can slide linearly, in this case again parallel to the longitudinal axis 15, as shown in Figure 8 (the hammer 46 always to the left) and Figure 10 (the hammer 46 moving to the right) comparison.

[0293] When looking at Figure 10 , one can see that on the left side of the hammer 46 there is a slave chamber 49 and on the right side of the hammer 46 there is a dump chamber or trigger chamber 47 (better seen in Figure 8 ). These two chambers are separated by the hammer piston 51 and its seal that essentially seals the two chambers from each other, preventing working fluid from flowing from one chamber to the other.

[0294] In the preferred variant, the pressure acting in the slave chamber 49 and the dump chamber 47 is the same, as both of them receive pressurized working fluid from the same source 72, either directly or indirectly. In Figure 4 , the source 72 is shown as a pump, but it could also be a tank or a reservoir, or a combination of these. Figure 8In the example shown in more detail, the driven chamber 49 is pressurized indirectly from the pressure source 72 via the dosing chamber. However, it can be supplied directly by the dumping chamber 47, or independently of these chambers, for example, by the source 72. This can be achieved through a direct connection between the source 72 and the driven chamber 49, for example, through a conduit between the two.

[0295] like Figure 9 As seen, the hammer piston 51 presents a driving effective region 75 in the driven chamber 49 and a dumping effective region 76 in the dumping chamber 47. In this example, the effective region is the area on which the working fluid in each corresponding chamber of the hammer piston 51 operates to move the hammer piston 51. The effective region is the region orthogonal to the operating or sliding axis of the hammer piston 51. Whether the surface forming this effective region is orthogonal to the operating axis or otherwise is not important. However, in the example shown, the surface presented in each chamber of the hammer piston 51 is also orthogonal to the operating axis.

[0296] In a preferred embodiment, Figure 9 In the indicated pre-launch position, there is a net force that drives the hammer piston 51 and hammer 46 fully into the driven chamber 49, where... Figure 9 The hammer is fully to the left. The hammer / hammer piston assembly rests against the stop 74. In a preferred embodiment, the stop includes an energy absorber (such as an O-ring shown) or a sufficiently resilient rigid metal stop to prevent deformation during multiple hammer movements. The net force and the stop provide a repeatable and consistent pre-firing position for the hammer 46 each time. This results in the dose valve 48 opening repeatedly and consistently upon impact with the hammer 46.

[0297] In a preferred embodiment, this net force is achieved by the dumping effective region 76 being larger than the driven effective region 75, since the working fluid pressure in each chamber is the same. However, it is also conceivable that different pressures could be supplied (e.g., the pressure supplied to the driven chamber could be adjusted to be lower than the pressure in the dumping chamber), with or without the same or different effective regions, or by supplying additional bias, such as bias from the spring. The advantage of using only the working fluid to operate the hammer is that residual energy can be removed (through the dumping chamber), whereas if a biasing element such as a spring is present, there might be energy in the spring that needs to be overcome. However, the biasing element may be useful in overcoming any inherent friction.

[0298] As shown, the driven chamber 49 is filled with working fluid 6 from the dosing chamber 52 via the port 57. Figure 9However, the driven chamber 49 can be filled directly from the source 72 without requiring any intermediate chambers, such as the dose chamber. In this example, the dose chamber 52 is an annular chamber that surrounds the working chamber, and both are concentric on axis 15. The port 57 can be modified with fixed or adjustable restrictive elements, baffles, or other restrictive geometries (e.g., reduced diameter) to restrict flow from the dose chamber 52 to the driven chamber 49.

[0299] At least in Figure 8 The dumping chamber 47 seen in the image is filled from source 72, which is selectively selected by trigger valve 50. When trigger valve 50 is in... Figure 8 In the first valve position shown, there is a fluid path from source 72 to dump chamber 47, via trigger valve 50, and down to dump passage 56. Dosing chamber 52 is also filled, in this case through port 58. The filling of dump chamber 47 and dosing chamber 52 can be sequential, i.e., one is filled before the other, and in a preferred embodiment of the invention, dump chamber 47 begins filling before dosing chamber 52. Figure 8 As seen, this passage is typically filled from a source of high-pressure working fluid 72. The filling time of the dump chamber 47 and the dosing chamber 52 is determined by the relative positions of the valve core seal 62 and the valve core passage 64. In a preferred embodiment, as described above, this timing ensures that the dump chamber 47 is filled or at least begins to fill before the dosing chamber 52.

[0300] The passageways for filling the dosing chamber 52 and unloading the chamber 46 are provided by the trigger valve 50, which in this case is a slide valve.

[0301] like Figure 8 As shown, seals are formed at various points on the valve core seal 62 between the inner diameter of the spool valve bore 65 and the outer diameter of the spool valve. These seals are each separate from the gasket 61. In a preferred embodiment, the gasket 61 allows the valve core seal 62 to have a small amount of axial movement, i.e., in the direction of movement of the valve core 63 of the trigger valve 50. This reduces friction on the seals and allows the seals to partially roll or move, for example, when they are O-rings, thereby further reducing friction.

[0302] Which of these valve core seals 62A, 62B, 62C, and 62D is providing a seal depends on the position of the valve core 63 along the valve core bore. The valve core 63 can move linearly relative to the valve core bore 65 and is... Figure 8 The arrows in the diagram indicate this.

[0303] In such Figure 8The first valve position shown is the primed firing position, where the dose chamber 52, dump chamber 47 and driven chamber 49 are all pressurised with working fluid 6 from the source 72, then the valve core seals 62A and 62D seal between the valve core bore inner diameter and the valve core 63 outer diameter. The shim 61 has a fluid communication path, such as a hole, from its outer diameter to its inner diameter. The valve core shim 61 allows working fluid to move from the valve core bore inner diameter / shim outer diameter to the shim inner diameter / valve core outer diameter. Thus, working fluid 6 can enter the valve core bore 65 at its outer diameter, for example from the source of high pressure working fluid 72, and travel as far as the shim inner diameter / valve core outer diameter and along it as the valve core seals allow, in this case, the seals 62A and 62D. Working fluid cannot move beyond these seals as they seal on the valve core bore inner diameter and the valve core outer diameter. Figure 8

[0304] For clarification, the shim 61 is a hollow cylinder which is packed between the valve core seals 62. The shim 61 has a passage through it to allow fluid to pass out of or into their outer diameter fluid connections to ports, dump passages or outlets to the ambient environment, or into or out of their inner diameter to the valve core 63 which forms the spool of the trigger valve 50. The valve core has a valve core passage 64, for example as a relief in the outer diameter of the valve core 63, which allows fluid to pass under the valve core seals 62 and thus from one adjacent shim 61 to the next. This allows fluid to flow selectively from the dose chamber to the dump chamber or to the ambient environment, and from the dump chamber to the ambient environment - this is explained further later.

[0305] Although there are two further seals 62B and 62C within the spool bore, in the primed firing / filling position they are each located adjacent to the valve core passage 64, which position allows working fluid to bypass the seals 62B and 62C. Figure 8

[0306] Thus, any port within the bounds of these two seal rings 62A and 62D can allow the flow of working fluid. Thus, fluid 6 from the source 72 can enter the port 58 and fill the dose chamber 52 (and then via the port passage 57 into the driven chamber 49), and enter the dump passage 56 to pressurise the dump chamber 47.

[0307] In the primed firing / filling (first valve position) position, as shown in Figure 1 1, the hammer 46 is held in place by the net force acting axially on the hammer piston 51 via the driven chamber 49 and the dump chamber 47, and thus the hammer 46 is held in the position as previously described Figure 8

[0308] In the primed firing / filling (first valve position) position, as shown in Figure 1 1, the hammer 46 is held in place by the net force acting axially on the hammer piston 51 via the driven chamber 49 and the dump chamber 47, and thus the hammer 46 is held in the position as previously described Figure 8 ​​​In this, the device 1 is primed and ready to fire. The dose chamber 52 is full and primed with high pressure working fluid 6 and is held closed from the working chamber 3 by the pressure of the working fluid 6 and the cage spring 54. The dose valve 48 is normally biased closed by a combination of pressure or spring force or just pressure or spring force. In the case where spring force is used to close the dose valve 48, this spring force is transmitted to the dose valve 48 via a surrounding element known as the spring cage 53. As Figure 9 The spring cage 53 is seen to capture the cage spring 54 in a compressed state at one end and to bias the spring cage 53 to the right.

[0309] The spring cage 53 can be part of the dose valve 48 or separate from it.

[0310] The opposite end of the spring cage 53 engages the dose valve 48. In this case, the spring cage under engages the dose valve 48 to transmit the bias of the cage spring 53 to help close the dose valve 48.

[0311] As Figure 9 The spring cage 53 is seen to extend to the left of the dose valve 48 into the dose chamber 52 to allow sufficient spring length to provide the correct closing force and travel distance for the dose valve 48. This length can be adjusted as required to vary the closing force. The spring cage 53 features a mouth 55 to allow unrestricted flow from the dose chamber through the dose valve opening into the working chamber.

[0312] The high pressure fluid has also travelled to both sides of the hammer piston 51 and as described keeps it out of balance. In this case, because the pressure on either side of the hammer piston 51 is the same. However, the effective area on each side of the hammer piston 51 is different (the effective area on the trigger chamber side is greater than the effective area on the driven chamber side) and the hammer 46 is not moved as the net force is pressing the hammer 46 against the stop 74. However, as already mentioned, there is a different pressure for each chamber of the hammer or vice versa to hold the hammer in place and an optional spring (not shown) acting on the hammer 46 to drive the hammer or assist its return.

[0313] The high pressure fluid from the dose chamber has travelled to the driven chamber 49 via the mouth passage 57. The high pressure fluid from the dose chamber has also primed the dump chamber 47 via the trigger valve 50 via the mouth 58.

[0314] However, in other forms, the driven chamber 49 can be supplied with high pressure fluid directly from the high pressure fluid source and not via any intermediate volume such as the dose chamber.

[0315] In the illustrated variant, the trigger valve 50 is a spool valve. This spool valve has a moving spool 63 which can selectively open and close paths as described and preferably has three positions. A first valve position, for example as illustrated in Figure 8 , directly or indirectly supplies the operating chamber from the high pressure source to a primed state. In this position, the trigger valve opens the supply to the dose chamber and closes any discharge path therefrom and opens the supply to the dose chamber and the trigger chamber to prepare but not actuate the opening of the dose valve. A second valve position, for example as illustrated in Figure 10 , actuates the device and closes the supply from the high pressure source. In this position, the trigger valve closes the supply to the device and in particular to the dose chamber and the trigger chamber and discharges, dumps or releases the high pressure operating fluid in the trigger chamber to ambient. As illustrated in Figure 12 , the trigger valve also has a third valve position which ensures the safety of the device. In this position, the trigger valve blocks the supply to the dose chamber, discharges, releases or dumps the dose chamber to ambient and optionally discharges, releases or dumps one or more of the remaining operating chambers.

[0316] As explained, the trigger valve 50 in the position illustrated in Figure 8 only allows fluid to flow from the source 72 to the dose chamber 52 and from there to the dump chamber 47 in the illustrated embodiment. As mentioned above, the slave chamber can alternatively be supplied directly from the source 72.

[0317] The paths of the trigger valve 50 are understandable when considering that the spool seal 62 only seals on the outer diameter of the spool 63. Thus, it can be seen that in the illustrated embodiment, there is a first fluid path 69 from the port 58 to the left in Figure 8 , through the spool passage 64, around the spool seal 62 and into the dump passage 56 and in turn up to the dump chamber 47. Importantly, there is no path for the source 72 to discharge into the ambient environment 14 when the trigger valve 50 is moved from the primed position to the firing position and the safety ensured position.

[0318] Depending on the application, the release of pressure can be an uncontrolled dump from the operating chamber or can be a slow or otherwise controlled release or discharge. For example, when safety is ensured, it can be desirable to release the air charge into the ambient environment in a slow manner or through a muffler or the like to reduce noise and / or prevent a sudden high pressure flow which can endanger a user or disturb the ambient environment.

[0319] The pressure from the source 72 is also used to charge the dose chamber, the slave chamber and the dump chamber and when the dump chamber is released via the second valve position to fire the device, the source 72 is sealed. Then, only the pressure charge in the dump chamber is dumped into the ambient environment 14.

[0320] Likewise, when the trigger valve 50 is moved to the third valve position, i.e. the safety assurance position, the source 72 is sealed and the working fluid charge in the slave chamber and dose chamber is dumped to the ambient environment 14. In the safety assurance position, the release of the charge from the dose chamber at least ensures the safety of the device and prevents actuation, e.g. the launch of the device / work (if a fastening gun) or the work the device is doing. Optionally, the safety assurance position will release the high pressure working fluid from one or more of the operating chambers (e.g. the dose chamber, the slave chamber and the dump / trigger chamber) thereby preventing any actuation by the high pressure working fluid. When safety assured, optionally, the slave chamber is released sequentially before the dump / trigger chamber - again, in a similar manner to the staging of the ports and bypass channels on the trigger valve. This will prevent the hammer from impacting the dose valve as the slave chamber will start to release before the trigger chamber, thereby maintaining the overall net force against the hammer away from the dose valve.

[0321] Regardless of the position of the trigger valve, in the preferred form there is no direct path from the high pressure source to the working chamber. In other words, there is no ability for the high pressure source to vent from the working chamber in an uncontrolled manner.

[0322] The hammer 46 is triggered by dumping the pressure in the trigger chamber 47 to a lower pressure (e.g. the ambient environment or atmosphere 14) via the dump channel 56. This is achieved by the trigger valve 50 being moved to the launch position as seen in Figure 10 In the example shown, the spool 63 is moved to the left in Figure 10 to allow dumping. The movement of the spool 63 provides a second fluid path 70 as shown in Figure 9 for fluid to dump from the dump chamber 47 via the dump channel 56 to the spool, around the spool seal 62D to the left (in Figure 9 ), and then out. In the manner shown in Figure 10 there is a leak path between the inner diameter of the spool bore 65 and the outer diameter of the spool piston 66, or in the various manners described later.

[0323] The user can actuate the trigger valve 50 using an actuator 73 that engages with the spool 64 of the trigger valve 50. For example an actuation trigger to actuate directly or indirectly, or by other means to drive the trigger valve 50. In this case, the trigger drives the spool 63 of the trigger valve 50 to the left in Figure 9 to dump the trigger chamber 47 via the dump channel 56 and out to the ambient environment 14 via the leak path 60. This actuation can be against a return spring (not shown) that returns the spool 63 to the charge or pre-launch position, whether acting directly on the spool or indirectly on the spool, for example by the trigger.

[0324] Figure 11 A and 1 IB show two further variants of the exit path from the trigger valve 50 to the ambient 14. In Figure 11 A there is a further sealing element of the spool 63, for example a spool seal 62E shown in Figure 11 B as a seal on the spool piston 66 that moves over the inner diameter of the spool bore 65 and against it, or alternatively, the sealing element 62 can be mounted in a groove on the spool bore 65 and seal and move against and against the elongate or non-elongate spool piston 66. Instead of Figure 8 the restriction or leak path in the previous variants in A, this allows the ability to increase the pressure on the spool 63 via the pressure on the spool piston 66 that biases it to the left to open it faster, thus assisting with pressure dump performance. This can be used to force the spool valve 50 to move quickly to the fully open position to dump working fluid from the dump chamber. Thus, if the trigger valve 50 is partially activated, this feature will ensure whether it moves all the way to activation, i.e. dumps the dump chamber.

[0325] Figure 11 B shows a further variant of the exit path when high pressure fluid is being dumped from the dump chamber. This can be in addition to or instead of the path of Figure 11 A. This variant allows the release or bypass flow path 67 to open when the spool 63 has moved far enough to the left. Two variants are shown: a flow path 67A that exits the side of the spool bore 65, or a flow path that uses the spool passage around the spool piston 66 as the flow path 67B.

[0326] This allows a slow release and then a sudden release if there is a leak path initially, and then still protects the spool piston 66 in the extreme case of movement. Additionally, when coupled with a seal such as the seal of Figure 11 A, it allows pressure to assist in moving the spool 63 and then quickly release the pressure.

[0327] Once the trigger chamber 47 is evacuated, the "fire" sequence begins. The dump trigger chamber 47 creates a pressure differential between the slave chamber 49 (higher) and the trigger chamber 47 (dumped to low pressure, e.g. ambient 14).

[0328] The higher pressure in the slave chamber 49 then drives the hammer 46 to strike the dose valve 48, which then opens the dose valve 48 momentarily to allow working fluid 6 from the dose chamber 52 to charge into the working chamber 4 to in turn drive the working load 4. This has a beneficial effect on the available performance of the tool, both in terms of efficiency and packaging.

[0329] The arrangement of the present invention also prevents the dose chamber 52 from being emptied through the port passage 57, as there is no path from there to the ambient 14 under normal trigger use. Also, in addition to the Figure 11 C, there is also no leak path from the port 58 to the ambient of the dose chamber 52 under normal trigger. This is because the spool 63 of the trigger valve 50 never fluidly connects the dose chamber 52 to the ambient 14. The dump chamber 47 and dump passage 56 only dump to the ambient 14 when the spool 63 moves from the primed to the fired position. The source 72 is sealed from the ambient, so there is no continuous outflow path from the high pressure working fluid of the source. In this way, the present invention ensures more efficient use of the working fluid charge in the dose chamber 52.

[0330] The hammer 46 can then return to the primed or first position by reestablishing the back force bias or imbalance on the hammer between the trigger chamber pressure and the pressure in the driven chamber 49, plus any spring force biasing member acting on the hammer. The hammer 46 can then return to the primed or first position.

[0331] Additionally, the hammer 46 can also be at least partially driven toward the dose valve 48 by a spring (not shown), or a spring (not shown) can assist it in returning, away from striking the dose valve 48. There can also be an elastic energy exchange between the hammer 46 and the dose valve 48, such that the hammer 46 bounces back. For example, the dose valve closing (moving left in Figure 9 C) can impart enough energy to the hammer to drive it back at least part way, and the pressure differential of the dump chamber can move it the rest of the way.

[0332] Figure 11 C shows a further option, where there is a transfer port 68 between the dose chamber 52 and the dump passage 56, and thus to the dump chamber 47. Typically, this is a restricted port 68, to allow pressure flow, but limit its volume or velocity. This slightly changes the sequence of operation, and the pressure balance is also significantly changed. The effect is to equalize the pressure on the hammer 46 more quickly after it is struck, allowing the hammer to reset more quickly, and possibly close the dose valve 48 more quickly, resulting in a more efficient drive stroke. This option has a significant trade-off, in that if the trigger is held in the fired position (i.e. all the way left), there is now a leak path from the dose chamber to atmosphere via the trigger spool 63. In this case, the trigger can be a momentary trigger, which then allows the spool 63 to return to the closed state as soon as possible. The flow out of the trigger valve 50 during dumping must be significantly greater than the restricted flow transfer port 68 from the dose chamber to the dump chamber. This means that any pressure signal from the dose chamber to the dump chamber will be lost to the ambient, and thus this is a less preferred variation.

[0333] When the trigger valve 50 is allowed to move back right, such as back toFigure 8 The dump chamber 47 is re-pressurised to help the hammer 46 back to the pre-firing position and the trigger system is now reset.

[0334] High pressure pneumatic tools often require a method to "ensure safety". The trigger valve 50 of the present invention combines the "ensure safety" energy release function as described below and the trigger "firing" function as described above into a single movable body or valve assembly which can move in one direction to effect the trigger and in the opposite direction to effect the ensure safety.

[0335] As Figure 12 shown, the trigger valve 50 has a third position to ensure the device 1 is safe. When the trigger valve 50 is placed in the ensure safety position, there is a path to the ambient environment 14 as described below, however this is not part of the normal trigger operation to fire the device, but is part of the ensure safety of the device, albeit operated by the trigger valve.

[0336] Again, the path for the working fluid 6 to flow out to the ensure safety position relies on the interaction of the trigger valve and the valve core seal 62, the valve core passage 64 and the shim 61. In particular, as Figure 12 shown, the valve core seals 62D, 62C and 62B all seal on the inner diameter of the valve core bore 65 and the outer diameter of the valve core 63. Therefore, any working fluid trapped between them cannot escape. This means that the source 72 of high pressure fluid is sealed as it is between seals 62B and 62C just as the dump passage 56 is between seals 62C and 62D. However, the port 58 can freely vent using the shim 61 using the valve core passage 64 to bypass the valve core seal 62A. From there, the dumped fluid 71 can pass into the low pressure or ambient environment 14. In this way, the working fluid 6 from the follower chamber 49 and the dose chamber 52 can be removed from the device. This prevents the device from being actuated or fired and therefore ensures the device is safe.

[0337] The trigger valve 50 is a three position pneumatic trigger - for example when used in a fastening tool such as a nail gun, pushing to the right (as seen in Figure 12 ) dumps the working fluid 6 from the dose chamber 52 via the port 58 to a lower pressure safe position, for example, the ambient environment 14 as shown, to ensure the device is safe. In this way, the working fluid "charge" is removed from the dose chamber 52 as highly compressed air so that even if the dose valve 48 is opened, there is no charge to drive the working load 4 and therefore the device incorporating the present invention is safe.

[0338] However, actuating or pulling the trigger valve 50 to the left (as seen in Figure 10The work fluid will be dumped from the dump chamber 47 to then fire the device 1. The trigger valve 50 can have a leak path 60 to the left as shown which acts on the trigger valve 50 to increase the speed of the action of the trigger valve opening.

[0339] For the exhaust valve 2 in Figure 4 The baffle 26 is shown, as is the baffle port 27 in the return chamber 10. These are used to adjust the rate of pressure build up on the working face 28 of the exhaust valve 2. Under dynamic loading, the pressure on the baffle second end 8 side will build up much faster than the pressure on the baffle first end 5 side due to the reduction in size of the baffle port 27. The smaller the baffle port 27, the slower the pressure build up on the working face 28 by the return fluid 42.

[0340] In this embodiment, the working face 28 of the exhaust valve 2 is formed in part by the valve member 37, in this case an O-ring 34. However, the valve member 37 can be any other suitable sealing arrangement capable of sealing and unsealing, such as, but not limited to, an x-ring, a lip seal or other continuous or variable cross-section sealing element. When the pressure differential in the return chamber 10 is high, the return fluid is pushed into the working chamber 20 by the working load travelling down the working chamber towards the second end 8, the return fluid acts on the valve member 37, in this case the O-ring 34, to move the valve member to seal off from the port 40 between the chambers as Figure 8 is seen. In this way, the pressure differential between the return chamber 10 and the pressure existing between the exhaust chamber 21 to the outlet 30 will cause the exhaust valve 2 to translate and move to or towards the open position 12 (i.e. to the left as drawn in the figures). The exhaust chamber 21 is formed between the body of the exhaust valve 2 and the surrounding housing 36 as described above when the exhaust valve 2 is open.

[0341] The size of the working face 28 and the relative internal face within the exhaust chamber 21 of the exhaust valve 2 is adjusted so that the exhaust valve 2 will remain open due to the pressure differential between the exhaust chamber 21 and the return chamber 10. This adjustment can be achieved by the seals used front and back and the seals on the internal and external diameters of the exhaust valve to create different sized areas for the pressure to work on, creating different sized forces to operate the exhaust valve 2.

[0342] The exhaust valve 2 is again normally biased closed by the biasing member 29, in this case a spring. The biasing member is selected based on the pressure experienced in the return chamber 10 and the pressure experienced in the exhaust chamber 21 so that the exhaust valve 2 opens, remains open and then closes as required by the timing of the device.

[0343] As shown, the exhaust valve 2 is sealed on its outer and inner periphery by seals 38, in this case O-rings as shown, but can be any suitable sealing member and material.

[0344] The supply of highly pressurized working fluid 6 is supplied briefly from the first end 5 to the back surface 9 of the working load 4, for example by the opening of a dosing valve 48. This sends the working load 4 down towards the second end 8 of the working chamber, as indicated by the arrow in Figure 4

[0345] In this variant, the exhaust valve 2 is also annular and has at least one, and preferably several openings from its inner to outer circumference, to form exhaust valve ports 33.

[0346] As seen in Figure 9 , the exhaust valve 2 also has an exhaust valve chamber face 39. Normally, when the pressure difference over the working face 28 is not enough to overcome the biasing member 29, then the exhaust valve will be closed. However, the pressure difference acting on the exhaust chamber 21 and the exhaust valve chamber face 39, and the fluid flowing into and out of the exhaust chamber 21, limited by the leakage paths, will keep the exhaust valve 2 in the open position 12. Thus, any pressure difference over the back surface 9 of the working load 4 will continue to be allowed to vent when the working load 4 is moved to a pre-positioned location towards the first end 5.

[0347] As the working load 4 continues to move up the working chamber 3 towards the first end 5, the pressure in the return chamber 10 has the ability to drop below the pressure over the back surface 9 of the working load 4. This is very evident at the end of the stroke of the working load 4 towards the first end 5, possibly because the exhaust valve 2 moves towards the closed condition 11. In this situation, there will be a pressure difference between the exhaust ports 33 (for example, the atmosphere 14) and the return chamber 10. In this situation, the valve member 37 will open to allow fluid to pass into the return chamber 10 via the inter-chamber port 40 shown by the arrow in Figure 11 . Thus, this will further assist the working load 4 to return to the pre-positioned location.

[0348] To provide a lower level of friction, the valve member 37, for example when being an O-ring 34 or other suitable shape, will only seal when the flow of fluid pushes it into place and compresses it to close the passage, at rest with no pressure difference or flow, the valve member 37 will not seal and thus provide little or no friction.

[0349] The method of operation will now be further explained.

[0350] The embodiment of Figures 4 to 12 triggered valve actuation by Figures 1 to 3 the exhaust valve operates in the same way, including the exhaust valve, adding the recirculation using the chamber port 35 and the check valve 23 as Figure 3 A to Figure 3 D's reed valve 24. Figures 4 to 11 Operating on the same principle, the recirculation is provided within the exhaust valve itself. The direction of movement in each figure is shown as an arrow over the working load 4.​

[0351] Upon triggering by an external mechanism, the spool 63 moves to the left to dump pressure from the dump chamber 47 and drive the hammer 46 into the dose valve 48. The dose valve cracks open and unseals the dose chamber 52 from the working chamber 3. As shown, a high pressure working fluid 6 charge, such as but not limited to a gas such as air, is then supplied to the rear face 9 of the working load 4 in the working chamber 3. As the working load is forced against the second end 8 by the working fluid 6, a portion of the supplied working fluid 6 expands into the rapidly forming volume created by the working cylinder 3 and the working load 4. Figures 1 to 12

[0352] Once the required working fluid charge has been supplied from the dose chamber 52 to the working chamber 3 by the dose valve 48, the dose valve 48 closes again, sealing the dose chamber 52 from the working chamber 3. The spool 63 has also returned to the position in Figure 8

[0353] As the working load 4 moves down the working chamber 3, fluid such as air in front of the front face 7 is forced down the working chamber. This fluid, for convenience referred to herein as return fluid 42, therefore enters the return chamber 10 through either the first fluid connection 17 or the second fluid connection 18.

[0354] When the working load 4 is captive, as shown in the example, the volume defined by the front face 7 and the working chamber 3 is a closed volume. However, if the working load is to be ejected, the principles will still apply, as there is a pressure wave of fluid in front of the piston as it moves down the working chamber 3. In this case, the differently shaped fluid connections 17 and / or 18 at least partially trap some of this return fluid 42.

[0355] As the return fluid enters the return chamber, it acts on the working face 28 of the exhaust valve 2. Once the biasing force is overcome by the pressure of the return fluid 42 acting on the working face 28, the exhaust valve 2, normally biased closed 11 by the biasing member 29, is forced open. This is the same for Figures 1 to 12

[0356] The exhaust valve 2 then moves to or towards the open state 12. The pressurised fluid accumulated in the unseen volume of the return chamber 10 then returns to the working chamber 3 and acts to push the working load 4 back up the working chamber and return it from the second end 8 to the first end 5.​​​

[0357] Workload 4 can now start to move freely back up the working chamber 3 towards the first end 5. Otherwise the volume defined by the working chamber 3, the back surface 9 and the first end 5 would cause pressure to build up, resisting the movement of the workload 4 as it moves to the first end 5, the exhaust valve is now open 12 and there is a path for pressure to be vented to a lower pressure (e.g. atmosphere 14). However, any low pressure can be suitable.

[0358] The exhaust valve 2 as described previously provides a flow path to a low pressure, as Figure 2 、 Figure 5 、 Figure 6 、 Figure 9 and Figure 10 illustrated, as exhaust fluid 41. It is explicitly stated that the exhaust fluid is not combustion gas, but simply the working fluid 6 which has expanded from its high pressure into the volume of the working chamber 3 and has done work on the workload 4.

[0359] In Figure 1 and Figure 2 , this open exhaust path for exhaust fluid 41 can be sufficient to allow the workload 4 to return to the ready position at the first end 5.

[0360] However, in some situations, a low pressure can occur in the return chamber 10, preventing the workload 4 from returning fully to the first end 5.

[0361] In this case, the recirculation enabled variants of Figure 3 A to Figure 3 D and Figures 4 to 11 may be used.

[0362] In Figure 3 A to Figure 3 D, if a low pressure occurs in the volume of the return chamber 10, as well as a low pressure defined by the working chamber 3, the second end 8 and the front face 7, there is a chamber port 35 and its check valve 23, illustrated as a reed valve 24. This check valve will open at the design pressure difference between outside the return chamber 10 (e.g. a low pressure area, such as atmosphere 14) and allow recirculation to reduce the pressure difference on the back surface 9, allowing the workload to move to the first end 5 consistently and fully.

[0363] Figures 4 to 11 Variants in

[0364] Figures 4 to 11A variation of this again opens 12 the exhaust valve 2 by the return fluid pressure 42 acting on the working face 28 of the exhaust valve 2 in the return chamber 10. The working face 28 is partially defined by a moving valve member 37, in this case an O-ring 34, which can move to seal and unseal the working face 28 (as described below). When sealing the working face 28, the O-ring 34 then also provides pressure on the exhaust valve 2 to move to the open position 12 or to assist in remaining in the open position 12.

[0365] As the exhaust valve 2 moves to the open position 12, it defines an exhaust chamber 21 between its exhaust valve chamber face 39 and the interior of the housing. When open 12, working fluid can pass through the outlet 30, through the exhaust valve port 33 into the exhaust chamber 21, and then via a restricted or leakage path to the exhaust port 32. The flow rate of the restricted or leakage path out of the exhaust chamber 21 is lower than the flow rate into the exhaust chamber 21, creating a pressure that assists in keeping the exhaust valve 2 open 12.

[0366] The flow path from the sidewall outlet 30 to the exhaust chamber 21, and then from the exhaust chamber 21 to the exhaust port 32, can be throttled, for example by a leakage path or other restriction, to have different flow rates into and out of the exhaust chamber. This impediment or restriction allows pressure to build up in the exhaust chamber 21 and also slows its release to assist in regulating the time the exhaust valve 2 remains open.

[0367] Then, as previously described, the working load 4 is able to move up the working chamber 3 back to the first end 5 under the action of the return fluid 42.

[0368] To increase the open time of the exhaust valve 2 and allow further options for opening and closing, the pressure built up in the exhaust chamber 21 and more specifically acting on the exhaust valve chamber face 39 and its opposite face continues to keep the exhaust valve open even after the pressure in the return chamber has reduced such that the exhaust valve 2 would otherwise close 11. This increases the exhaust valve open time and thus the ability of the working load 4 to return to the first end consistently.

[0369] Additionally, the exhaust valve has an inter-chamber port 40 between the exhaust chamber 21 and the return chamber 10 and preferably between the exhaust port 32 and the return chamber 10. In the preferred embodiment, this inter-chamber port 40 is valved by a valve member 37. Thus, when there is a pressure differential between the exhaust chamber 21 or the exhaust port 32 and the return chamber 10, the valve member 37 will open and allow recirculation into the return chamber to effectively act as the return fluid 42, as Figure 7 and 11 Thus, even after the exhaust valve 2 has closed, this will further allow the working load 4 to return to the first end 5 consistently and be ready to work again.

[0370] Moving or towards the first end the exhaust valve 2 provides for ease of assembly and reduces the number of parts. Furthermore, providing the exhaust port as a side exhaust port provides for reduced complexity when compared to an axial port that must pass parallel to the longitudinal axis 15 at the first end. The result is also a more compact construction with fewer parts, lower manufacturing costs, and ease of assembly and maintenance.

[0371] In the present invention, the introduction of the hammer in conjunction with the inflow shut-off function of the trigger system (from a high pressure source) allows for a very short duration pulse of flow into the working chamber. This allows for very high thermodynamic efficiency and cycle rate.

[0372] The short duration pulse of high pressure working fluid means that the volume of working fluid that enters the working chamber is low, but then is allowed to expand by a large factor, which is closely related to the thermodynamic efficiency of a compression fluid-mechanical system.

[0373] In the present invention, having the required pneumatic trigger components perform both the trigger and "safety assurance" functions can maintain all of the performance metrics mentioned above while meeting regulatory and good safety design requirements.

[0374] The foregoing description of the present invention includes preferred forms thereof. Modifications can be made thereto without departing from the scope of the present invention.

Claims

1. An actuation trigger for a device, comprising or including: Dosing chamber, which is used to contain the high-pressure working fluid packing material received from the high-pressure source. A dosing valve, biased to close, seals and isolates the dosing chamber from the working chamber and retains the high-pressure working fluid packing within the dosing chamber. The hammer is operated by a piston having a driven chamber on a first side of the piston and a trigger chamber on a second side of the piston that is sealed and isolated from the first side. The driven chamber receives high-pressure working fluid directly or indirectly from the high-pressure source. A trigger valve for selectively supplying or releasing high-pressure working fluid into or from the trigger chamber. This arrangement ensures that when the hammer contains high-pressure working fluid in both the driven chamber and the trigger chamber, the hammer is held in a first position by force imbalance, and when the high-pressure working fluid is released from the trigger chamber, the hammer is driven to or toward a second position, toward the trigger chamber. When the hammer is driven to or toward the second position, it strikes the dosage valve, disengaging the dosage valve to unblock the dosage chamber and the working chamber, thereby allowing the high-pressure working fluid packing material to enter the working chamber and perform work therein.

2. The actuation trigger according to claim 1, wherein, The force imbalance is caused by the fact that the working area of ​​the high-pressure working fluid on the trigger chamber side of the piston is larger than the working area of ​​the high-pressure working fluid on the driven chamber side of the piston.

3. The actuation trigger according to claim 1 or 2, wherein, The trigger valve is a slide valve.

4. The actuation trigger according to claim 1, wherein, When the dosage valve opens from the dosage chamber to the working chamber, there is no supply from the high-pressure source to the dosage chamber.

5. The actuation trigger according to claim 1, wherein, The trigger valve actuates to selectively release the high-pressure working fluid from any one of the operating chambers, including the dose chamber, the driven chamber, or the trigger chamber, into the surrounding environment, or directly or indirectly supply the high-pressure working fluid from the high-pressure source to any one of the operating chambers, including the dose chamber, the driven chamber, or the trigger chamber, in order to trigger the device. The trigger valve has at least two positions: a. A first valve position, used to supply the operating chamber to a pre-operational state directly or indirectly from the high-pressure source, wherein the trigger valve: i. Open the supply to the dosing chamber and close any discharge paths therefrom, and ii. Open the supply to the dose chamber and the trigger chamber to prepare for, but not actuate, the opening of the dose valve. b. A second valve position for actuating the device and shutting off the supply from the high-pressure source, wherein the trigger valve: i. Shut down the supply to the device and the supply to the dose chamber and the trigger chamber, and ii. Discharge the trigger chamber into the surrounding environment.

6. The actuation trigger according to claim 1, wherein, The trigger valve has a third valve position to ensure the safety of the device, wherein the trigger valve: a. Block the supply into the dosing chamber, b. Discharge the dose chamber into the surrounding environment, and c. Discharge one or more of the remaining operating chambers.

7. The actuation trigger according to claim 1, wherein, When the trigger valve shuts off the supply to the device, the high-pressure working fluid is prevented from leaving the high-pressure source.

8. The actuation trigger according to claim 1, wherein, The trigger chamber is filled before the dose chamber when it is supplied.

9. The actuation trigger according to claim 1, wherein, The hammer slides along a first sliding axis, and the dosage valve slides along a second sliding axis.

10. The actuation trigger according to claim 9, wherein, The first sliding axis and the second sliding axis are at least parallel.

11. The actuation trigger according to claim 10, wherein, The first sliding axis and the second sliding axis are concentric.

12. The actuation trigger according to claim 1, wherein, The dosage valve is an annular ring, which has an annular sealing surface that seals and isolates the dosage chamber from the working chamber.

13. The actuation trigger according to claim 1, wherein, The dosage valve is closed by spring bias.

14. The actuation trigger according to claim 1, wherein, The hammer has elastic elements on a first side and / or a second side to assist or mitigate the force imbalance.

15. The actuation trigger according to claim 1, wherein, The hammer returns to or toward the first position at least in part via the return of the dosage valve or the high-pressure working fluid to the trigger chamber.

16. The actuation trigger according to claim 1, wherein, The hammer is acted upon by pressure in the working chamber to slow its continued movement in the direction of the dosage valve.

17. The actuation trigger according to claim 1, wherein, The workload is: The capture type, or Non-capture type and expelled from the working chamber, or Pressure waves that perform work in other ways within the working chamber.

18. The actuation trigger according to claim 1, wherein, The high-pressure working fluid can be a compressible or incompressible fluid.

19. The actuation trigger according to claim 1, wherein, The high-pressure working fluid is in the range of 15 bar to 100 bar.

20. The actuation trigger according to claim 1, wherein, The high-pressure working fluid is a gas.

21. A high-pressure fluid operating system, comprising or including: A dosing chamber for containing a high-pressure working fluid packing, the dosing chamber being operably connected to a piston on a first side of the hammer in fluid communication, and selectively in fluid communication with a second side of the piston. When high-pressure working fluid is supplied to both the first and second sides, the piston is in a force imbalance position in the first position, and When the high-pressure working fluid is selectively removed from the second side of the piston and urged to move toward or towards the second position to do work, the piston is in a state of force imbalance.

22. The operating system according to claim 21, wherein, The hammer is held in the first position by a force imbalance from equal pressures between the trigger chamber and the driven chamber, the pressure regions in the trigger chamber and the driven chamber being different, resulting in a greater net force toward the first position.

23. The operating system according to claim 21 or 22, wherein, An elastic element is present on either or both sides of the first side or the second side.

24. The operating system according to claim 21, wherein, The high-pressure working fluid is a compressible fluid.

25. The operating system according to claim 21, wherein, The high-pressure working fluid is in the range of 15 bar to 90 bar.

26. The operating system according to claim 21, wherein, The high-pressure working fluid is a gas.

27. The operating system according to claim 21, wherein, When the dosing valve opens from the dosing chamber to the working chamber, there is no supply from the high-pressure source to the dosing chamber.

28. The operating system according to claim 21, wherein, The operating system includes an exhaust valve, which includes or comprises: A workload, which is located within or operable by a working chamber, the working chamber being capable of selectively receiving some or all of the high-pressure working fluid packing from the dosing chamber, using the high-pressure working fluid on the rear surface of the workload, the workload being driven from a first end of the working chamber to or toward an opposite second end of the working chamber. Fluid pressure, received from the front surface of the workload and returned to the chamber, is generated at least in part by the downward movement of the workload along the working chamber toward the second end. The vent valve is adapted to open due to the fluid pressure in the return chamber acting on its working surface. When open, the vent valve allows high-pressure working fluid present on the rear surface of the working chamber to be discharged from the working chamber to a lower pressure position. The high-pressure working fluid exits via the side wall of the working chamber to the vent valve. This creates a pressure difference from the front surface to the rear surface, thereby returning the workload from the second end to or toward the first end.

29. An actuation trigger for a device, comprising or including: Dosing chamber, which is used to contain the high-pressure working fluid packing material received from the high-pressure source. A dosing valve, biased to close, seals and isolates the dosing chamber from the working chamber, and houses the high-pressure working fluid packing within the dosing chamber, which can be opened under controlled action to allow the high-pressure working fluid packing into the working chamber. A trigger valve selectively supplies high-pressure working fluid from the high-pressure source to the dosing chamber and controls the opening and closing of the dosing valve, whether directly or indirectly. in, When the dosage valve opens from the dosage chamber to the working chamber, there is no supply from the high-pressure source to the dosage chamber.

30. The actuation trigger according to claim 29, wherein, The trigger valve includes a slide valve, the slide valve having: a. A first valve position, used to supply the dose chamber to a pre-operational state directly or indirectly from the high-pressure source, wherein the trigger valve: i. Open the supply to the dosing chamber and close any discharge paths therefrom, and ii. Open the supply to any other operating chamber in preparation for, but without actuating, the opening of the dosage valve. b. A second valve position for actuating the device and shutting off the supply from the high-pressure source, wherein the trigger valve: i. Shutting off the supply to the device and the supply to the dosing chamber, and ii. Allow other operating chambers to actuate the opening of the dosage valve.

31. The actuation trigger according to claim 29 or 30, wherein, The trigger valve has a third valve position to ensure the safety of the device, wherein the trigger valve: a. Blocking the supply into the dose chamber, and b. Drain other operating chambers.

32. The actuation trigger of claim 29, comprising: an exhaust valve, the exhaust valve comprising or including: A workload, which is located within the working chamber, utilizes pressurized fluid on its rear surface, the workload being driven from a first end of the working chamber to or toward an opposite second end of the working chamber. Fluid pressure, received from the front surface of the workload and returned to the chamber, is formed at least in part by the downward movement of the workload along the working chamber toward the second end. The vent valve is adapted to open due to the fluid pressure in the return chamber acting on its working surface. When open, the vent valve allows high-pressure working fluid present on the rear surface of the working chamber to be discharged from the working chamber to a lower pressure position. The high-pressure working fluid exits via the side wall of the working chamber to the vent valve. This creates a pressure difference from the front surface to the rear surface, thereby returning the workload from the second end to or toward the first end.

33. An actuation trigger for a device, comprising or including: A trigger valve is used to selectively control the supply of high-pressure working fluid from a high-pressure source to one or more operating chambers, thereby controlling the operating chambers, which use high-pressure working fluid-filled packing to act on a working load, wherein... The trigger valve has: a. A first valve position, used to supply the one or more operating chambers with a pre-operational state directly or indirectly from the high-pressure source, wherein the trigger valve: i. To open the supply to the one or more operating chambers, and ii. Close any discharge paths to ambient pressure to prepare for, but not for, performing work in, the working chamber. b. Second valve position, which actuates the device, wherein the trigger valve: i. Shutting off or opening the supply to the one or more operating chambers, thereby allowing the working chambers to be filled and perform work. c. The third valve position, which is used to ensure the safety of the device, wherein the trigger valve: i. Shut down the supply from the high-voltage source to the one or more operating chambers, or ii. Discharge one or more operating chambers into ambient pressure, thereby rendering the device unactable or inert.

34. The actuation trigger according to claim 33, wherein, The trigger valve is any one or more of a rotary valve, spool valve, dual-way or multi-way directional control valve, or any combination thereof.

35. The actuation trigger according to claim 33 or 34, wherein, The one or more operating chambers control the packing valve to deliver the high-pressure working fluid packing into the operating chamber.

36. The actuation trigger according to claim 33, comprising: an exhaust valve, wherein, High-pressure working fluid is used on the rear surface or area of ​​the working load, which is driven from or within the working chamber, from a first end of the working chamber to or toward a opposite second end of the working chamber. Fluid pressure is received from the front surface or region of the workload and returned to the chamber, the fluid pressure being at least in part due to the workload moving downwards along the working chamber toward the second end. The vent valve is adapted to open due to the fluid pressure in the return chamber acting on its working surface. When open, the vent valve allows high-pressure working fluid present on the rear surface of the working chamber to be discharged from the working chamber to a lower pressure position. The high-pressure working fluid exits via the side wall of the working chamber to the vent valve. This creates a pressure difference from the front surface to the rear surface, thereby returning the workload from the second end to or toward the first end.

37. The actuation trigger according to claim 36, wherein, There is no direct path from the high-pressure source to the working chamber, regardless of the position of the trigger valve.

38. An apparatus comprising or including: Dosing chamber, which is used to contain the high-pressure working fluid packing material received from the high-pressure source. A dosing valve, biased to close, seals and isolates the dosing chamber from the working chamber and retains the high-pressure working fluid packing within the dosing chamber. The hammer is operated by a piston having a driven chamber on a first side of the piston and a trigger chamber on a second side of the piston that is sealed and isolated from the first side. The driven chamber receives high-pressure working fluid directly or indirectly from the high-pressure source. A trigger valve for selectively supplying or releasing high-pressure working fluid into or from the trigger chamber. This arrangement ensures that when the hammer contains high-pressure working fluid in both the driven chamber and the trigger chamber, the hammer remains unbalanced in a first position, and when the high-pressure working fluid is released from the trigger chamber, the hammer is driven to or toward a second position, toward the trigger chamber. When the hammer is driven to or toward the second position, it strikes the dosage valve, disengaging the dosage valve to unblock the dosage chamber and the working chamber, thereby allowing the high-pressure working fluid packing material to enter the working chamber and perform work therein.

39. The apparatus according to claim 38, wherein, The force imbalance is caused by the fact that the working area of ​​the high-pressure working fluid on the trigger chamber side of the piston is larger than the working area of ​​the high-pressure working fluid on the driven chamber side of the piston.

40. The apparatus according to claim 38 or 39, wherein, The trigger valve is a slide valve.

41. The apparatus according to claim 38, wherein, The trigger valve actuates to selectively discharge the high-pressure working fluid from any one of the operating chambers, including the dose chamber, the driven chamber, or the trigger chamber, into the surrounding environment, or directly or indirectly supply the high-pressure working fluid from the high-pressure source to any one of the operating chambers, including the dose chamber, the driven chamber, or the trigger chamber, in order to trigger the device. The trigger valve has at least two positions: a. A first valve position for supplying the operating chamber directly or indirectly from the high-pressure source to a pre-operational state, wherein the trigger valve opens to supply the following: i. Slave chamber and trigger chamber, ii. Dose chamber, and close any discharge path from it, and b. A second valve position for actuating the device and shutting off the supply from the high-pressure source, wherein the trigger valve: i. Shut down the supply to the device and the supply to the dose chamber and the trigger chamber, and ii. Discharge the trigger chamber into the surrounding environment.

42. The apparatus according to claim 38, wherein, The trigger valve has a third valve position to ensure the safety of the device, wherein the trigger valve: a. Block or shut off the supply to the dose chamber and the trigger chamber. b. Discharge the dose chamber, and c. Discharge the trigger chamber.

43. The apparatus according to claim 42, wherein, When the trigger valve shuts off the supply to the device, the high-pressure working fluid is prevented from leaving the high-pressure source.

44. The apparatus according to claim 38, wherein, The trigger chamber is filled before the dose chamber when it is supplied.

45. The apparatus according to claim 38, wherein, The hammer slides along a first sliding axis, and the dosage valve slides along a second sliding axis.

46. ​​The apparatus according to claim 45, wherein, The first sliding axis and the second sliding axis are at least parallel.

47. The apparatus according to claim 46, wherein, The first sliding axis and the second sliding axis are concentric.

48. The apparatus according to claim 38, wherein, The dosage valve is an annular ring, which has an annular sealing surface that seals and isolates the dosage chamber from the working chamber.

49. The apparatus according to claim 38, wherein, The dosage valve is closed by spring bias.

50. The apparatus according to claim 38, wherein, The hammer has elastic elements on the first side and / or the second side that assist or mitigate the force imbalance.

51. The apparatus according to claim 38, wherein, The hammer returns to or toward the first position at least in part via the return of the dosage valve or the high-pressure working fluid to the trigger chamber.

52. The apparatus according to claim 38, wherein, The work is a load or an action on a load, and the load is: The capture type, or Non-capture type and expelled from the working chamber, or Pressure waves that perform work in other ways within the working chamber.

53. The apparatus according to claim 38, wherein, The high-pressure working fluid is a compressible fluid.

54. The apparatus according to claim 38, wherein, The high-pressure working fluid is in the range of 15 bar to 90 bar.

55. The apparatus according to claim 38, wherein, The high-pressure working fluid is a gas.

56. The apparatus of claim 38, comprising or including: an exhaust valve, the exhaust valve comprising or including: A workload that performs work on, within, or from the working chamber, using a high-pressure working fluid on the rear surface of the working chamber, the workload being driven from a first end of the working chamber to or toward an opposite second end of the working chamber. Fluid pressure, received from the front surface of the workload and returned to the chamber, is generated at least in part by the downward movement of the workload along the working chamber toward the second end. The vent valve is adapted to open due to the fluid pressure in the return chamber acting on its working surface. When open, the vent valve allows high-pressure working fluid present on the rear surface of the working chamber to be discharged from the working chamber to a lower pressure position. The high-pressure working fluid exits via the side wall of the working chamber to the vent valve. This creates a pressure difference from the front surface to the rear surface, thereby returning the workload from the second end to or toward the first end.

57. A method for an actuating device, comprising or including the steps of: The dosing chamber is filled with packing material using high-pressure working fluid. The driven chamber on the first side of the hammer is filled with high-pressure working fluid. The trigger chamber on the second side of the hammer is filled with high-pressure working fluid. The first and second sides are separated by a piston operably connected to the hammer, such that the hammer remains in a force imbalance in a first position. The high-pressure working fluid is released from the trigger chamber to drive the hammer toward or towards the second position. When the dosing valve is in or toward the second position, the dosing valve is actuated by the hammer striking the dosing valve to disengage it from the sealed position to the unsealed position, allowing the high-pressure working fluid filling material to enter the working chamber and perform work therein. In the sealed position, the dosing valve seals and isolates the dosing chamber from the working chamber.

58. The method according to claim 57, wherein, The force imbalance is at least partially provided or mitigated by the biasing element.

59. The method according to any one of claims 57 or 58, comprising the step of: returning the hammer to or toward the first position at least in part by the return of the dosage valve or high-pressure working fluid acting on a portion of the hammer to the trigger chamber.

60. The method of claim 57, wherein, The high-pressure working fluid is supplied directly or indirectly by a high-pressure source.

61. The method of claim 60, comprising the step of: directly or indirectly filling the driven chamber from the high-voltage source.

62. The method of claim 60, further comprising the steps of: selectively filling the trigger chamber and the dose chamber via a trigger valve, or releasing the trigger chamber and / or the dose chamber.

63. The method according to claim 62, wherein, The trigger valve is a slide valve.

64. The method according to claim 62 or 63, wherein, The trigger valve actuates to selectively release the high-pressure working fluid from any one of the operating chambers, including the dose chamber, the driven chamber, or the trigger chamber, into the surrounding environment, or directly or indirectly supply the high-pressure working fluid from the high-pressure source to any one of the operating chambers, including the dose chamber, the driven chamber, or the trigger chamber, in order to trigger the device. The trigger valve has at least two positions: a. A first valve position, used to supply the operating chamber to a pre-operational state directly or indirectly from the high-pressure source, wherein the trigger valve: i. Open the supply to the dosing chamber and close any discharge paths therein, and ii. Open the supply to any other chamber in preparation for, but without actuating, the opening of the dosage valve. b. A second valve position for actuating the device and shutting off the supply from the high-pressure source, wherein the trigger valve: i. Shut down the supply to the device and the supply to the dose chamber and the trigger chamber, and ii. Allow the operating chamber to actuate the opening of the dosage valve.

65. The method according to claim 62, wherein, The trigger valve has a third valve position to ensure the safety of the device, wherein the trigger valve: a. Blocking the supply into the dose chamber, and b. Drain the other chambers.

66. The method of claim 60, further comprising the step of: when the dosing valve is opened from the dosing chamber to the working chamber, there is no supply from the high-pressure source to the dosing chamber.

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