Improvements in or relating to actuation systems

Abstract

An apparatus and method for operating and controlling high pressure fluids is disclosed. The apparatus has a discharge chamber for receiving high pressure fluid from a source of high pressure fluid and a dose chamber for receiving a flow of high pressure fluid from the discharge chamber through a flow path from the discharge chamber to the dose chamber, the discharge chamber having an outlet. There is also a working chamber having an inlet end at one end thereof and a dose valve member having an annular sealing face around the inlet end. When the dose valve member is in a closed condition, the sealing face is in contact with an annular seat to seal the outlet; and when the dose valve member is in an open condition, there is a gap between the annular sealing face and the seat to allow high pressure fluid to move from the outlet to the inlet. The high pressure fluid in the discharge chamber at least partially holds the dose valve member in the closed condition until the pressure of the high pressure fluid in the discharge chamber is reduced, whereby the high pressure fluid in the dose chamber unseals the dose valve member to the open position.

Description

TECHNICAL FIELD

[0001] The present invention relates to actuation systems for high pressure fluid power devices.

[0002] In particular, but not exclusively, the present invention relates to valves and methods of actuating them to release or transfer energy. BACKGROUND

[0003] There is a need to control and release energy, particularly energy delivered, provided or released by high pressure fluids.

[0004] In one embodiment, high pressure fluids, such as compressed gases, such as air, or carbon dioxide, can be used to do work. In one such embodiment, compressed air can be used to drive a piston or the like in a work chamber through a valve to do work, such as drive fasteners, for example in a tool such as, but not limited to, a nail gun.

[0005] In this case, energy is extracted from the high pressure fluid source by expansion. Expansion of a gas is always associated with a decrease in pressure, unless the system is heated, extra work (compression) is done or extra gas is added.

[0006] There are pneumatic nail guns, usually tethered to a pneumatic compressor, which use pressurized gas to drive a reciprocating piston which in turn drives nails or fasteners into the material to be fastened. In these compressor supply systems, air is supplied continuously through a valve to keep the pressure behind the piston high enough to perform the required driving function. This valve or another valve then allows the piston to return to the ready to work position.

[0007] Keeping the intake cold is important to maintain the efficient use of compressed gas, which is difficult or impossible after multiple combustion cycles. This is important for the function of the tool, as if the pressure is not kept at a high level, the lower pressure can not be enough to drive the nails in. This of course depends on the specific substrate, nail type, chamber volume and piston diameter implemented in the specific design.

[0008] These tools, especially the frame variants, are inefficient in their use of compressed gas. They use a lot of air to drive each nail and return the drive piston. As a result, they cannot operate without a compressor, which is the source of compressed air, for any meaningful commercial use. Therefore, efficiency is not usually a primary performance indicator for these tools, as the compressor is simply running a little longer, while the cost or hassle to the user is little. Instead, power, reliability, ruggedness, compactness and other biological comfort take precedence over efficiency, some of which are directly or indirectly achieved through the effective unlimited air supply of the tethered compressor.

[0009] To at least address the tethering issue, several different systems have been developed.

[0010] One such system utilizes a combustible gas, such as butane, to provide the explosion that drives the operation of the tool. Given that the tool typically includes a storage device for the combustible gas and a combustion source in close proximity to one another, such combustion systems have their own safety issues. The gas and the canister tend to be expensive and available only from select suppliers. Furthermore, when finished, the canister is a waste stream that can not always be recycled. Additionally, they often require a battery as an ignition source. Likewise, when these are exhausted, even if they are rechargeable, they can not be recycled. Furthermore, the heat and shock of the explosion tends to wear out the tool severely, causing them to require frequent maintenance. If the tool is exposed to moisture, such as rain, the electrical components are prone to failure. All of these factors add additional costs, waste streams, and factors that inconvenience the user. Furthermore, their performance can be affected in rapid fire situations because they must vent the combustion gases and charge with fresh gas and air and mix properly before firing. Additionally, they can be inefficient since they do not use the full pressure of the combustion charge. Furthermore, they produce gases that can be harmful to the health of the user, especially in an enclosed space.

[0011] Recently, portable pressure sources have been developed through which a container containing pressurized fluid, such as carbon dioxide, can be connected to a tool that is traditionally powered by an air compressor through a regulator. These systems allow the use of the tool in a more portable manner without the restrictions of the hoses required by traditional setups. However, the pneumatic tools available are designed for pneumatic devices, and the supply of compressed air or gas is virtually unlimited. Thus, the transfer and use of the energy of the compressed gas is again relatively inefficient, especially in the drive mechanism.

[0012] Typically, such compressed gas driven tools are inefficient at least because, in order to simplify their manufacture and assembly, they have an architecture in which a valve that supplies compressed gas to a drive piston that performs work has two functions. Thus, at least for a short time, there is a flow path between the main pressurized fluid supply and the atmosphere that passes through a chamber in which the drive piston reciprocates. While the pressure zone is typically designed to quickly stop this flow path, it can be an important cause of inefficiency in certain designs, even if for a short time, there is a direct path from the high pressure source to the atmosphere, thus wasting the energy that exists in such high pressure fluid. In these established designs, even if this temporary leak is effectively minimized, the mechanism still operates in a manner that discharges a significant amount of full pressure gas to the atmosphere that has not done any work and thus is wasted. Thermodynamically, this is very inefficient.

[0013] Thus, it would be advantageous for the drive mechanism of a pneumatic tool to be more efficient in the consumption of compressed gas or high pressure fluid.

[0014] One solution to avoid the issues with remote supply of high pressure fluid systems, the use of combustion or inefficient use of high pressure fluid is the valve and actuation system disclosed in our own patent NZ573990. This valve and actuation system can be used in many applications including impact nail guns for timber, concrete and related building materials. However, the same actuation and valve system can find use in many other applications including but not limited to pest control, pneumatic motors or anywhere where efficient valve control is required.

[0015] In NZ573990, the valve that releases high pressure fluid into the working chamber is opened by a striking hammer that impacts it to allow fluid into the working bay to do work. This is a very efficient system and there is little wastage of high pressure fluid.

[0016] In this specification, where a document, act or other item of information is referred to, it is generally referred to for the purpose of providing background information regarding the present invention. Unless otherwise specifically indicated, reference to such a document, act or item of information is not to be understood as an admission that such document, act or item of information is prior art or forms part of the common general knowledge in the art. In the claims, means-plus-function clauses, if used, are intended to cover the structures described herein as performing the recited function and not only structural equivalents. Structure described in means-plus-function clauses are deemed to be passive unless expressly recited otherwise.

[0017] It is an object of the present invention to provide an improved actuation and / or valve system for high pressure fluid, or to provide an improved actuation and / or valve system for high pressure fluid that is more efficient and is actuated primarily or solely by high pressure fluid or gas, or to overcome the above disadvantages or to provide a useful alternative to the public, or at least to provide the public with a useful choice. SUMMARY

[0018] In a first aspect, the invention consists in an apparatus comprising or including,

[0019] a discharge bay for receiving high pressure fluid from a source of high pressure fluid,

[0020] a dose bay for receiving a flow of high pressure fluid from the discharge bay through a flow path from the discharge bay to the dose bay, having an outlet,

[0021] a working bay having an inlet end at one end thereof,

[0022] a dose valve member having an annular sealing face about the inlet end,

[0023] wherein, when the dose valve member is in a closed condition, the sealing face is in contact with the annular seat to seal the outlet; and in the case where the dose valve member is in an open condition, there is a gap between the annular sealing face and the seat to allow high pressure fluid to move from the outlet to the inlet,

[0024] Wherein the high pressure fluid in the venting chamber at least partially holds the dosing valve member in a closed state until the high pressure fluid pressure in the venting chamber is reduced, whereby the high pressure fluid in the dosing chamber unseals the dosing valve member to an open position.

[0025] Preferably, the high pressure fluid flow is prevented from entering the dosing chamber or the venting chamber when the dosing valve member is open.

[0026] Preferably, the high pressure fluid flow is prevented from entering the venting chamber when the dosing valve member is open.

[0027] Preferably, the high pressure fluid flowing into the working chamber then does work on a working load therein to expel it from or move it towards the opposite end of the working chamber.

[0028] Preferably, no fluid connection from any high pressure fluid source to the working load drive assembly or chamber body is available when the working load is driven from the first (or inlet) end to the second (or opposite) end.

[0029] Preferably, the dosing valve member slides linearly.

[0030] Preferably, the dosing valve member slides along a linear axis parallel to the device main axis.

[0031] Preferably, the working load, whether fixed, such as a piston, or expelled, such as a projectile, slides linearly along the working chamber from the inlet end to or towards the opposite, distal end, parallel to the main axis.

[0032] Preferably, the venting chamber, the dosing chamber and the working chamber are concentric or parallel to the main axis.

[0033] Preferably, the venting valve is biased open at or towards the inlet end and closes the venting port under actuation of the high pressure fluid leaving the dosing chamber.

[0034] Preferably, the venting port opens under the action of the bias when the working load is at or near the opposite end.

[0035] Preferably, the venting valve is a piston or a diaphragm, at least partially surrounded by the dosing valve.

[0036] Preferably, the dosing valve is at least partially biased in the closed state.

[0037] Preferably, the dosing chamber is a hollow volume radially outward or inward from the working chamber.

[0038] Preferably, the flow path is through the dosing valve.

[0039] Preferably, the flow path is in a skirt of the dosing valve.

[0040] Preferably, there is a restriction in the flow path from the discharge chamber to the dose chamber such that the discharge chamber increases the closing pressure of the dose valve even when filling the dose chamber.

[0041] Preferably, there is a one-way valve in the flow path from the discharge chamber to the dose chamber.

[0042] Preferably, the discharge chamber is a hollow cylindrical volume, such as an annular chamber.

[0043] Preferably, the pressure in the discharge chamber is reduced by a trigger mechanism or similar.

[0044] Preferably, the trigger mechanism vents the pressure in the discharge chamber to atmosphere.

[0045] Preferably, the working load is returned to the inlet port by a fluid cushion behind its back side, a spring behind or in front of its back side, or a tension member connected to or towards the inlet port from the front side.

[0046] Preferably, the bias on the exhaust valve is a spring.

[0047] Preferably, wherein or in addition, the bias on the exhaust valve is a tension member connected between the working load and the exhaust gate.

[0048] Preferably, there is a safety valve to selectively vent pressure from the dose chamber to prevent the device from operating.

[0049] Preferably, a slow leak safety valve releases fluid pressure from the dose chamber if the high pressure fluid supply pressure drops below the pressure of the dose chamber.

[0050] In another aspect, the invention comprises a method of operating a high pressure fluid device, comprising the steps of,

[0051] filling a discharge chamber with high pressure fluid,

[0052] increasing the sealing pressure of a valve member by high pressure fluid acting on its back side to hold the valve member in a closed state, the valve member having an annular sealing face between an outlet of a dose chamber and an inlet of a working chamber,

[0053] passing high pressure fluid from the discharge chamber to the dose chamber through a flow path,

[0054] reducing the pressure of the discharge chamber such that the high pressure fluid in the dose chamber acts on a front side of the valve member, forcing the valve member into an open state with a gap between the inlet and the outlet,

[0055] the high pressure fluid then enters the working chamber from the dose chamber to do work on a working load within the working chamber.

[0056] Preferably, the discharge chamber and the dose chamber are at nearly the same pressure when filled prior to pressure reduction.

[0057] Preferably, the vent valve moves to a position closing the vent port from the work chamber until the work on the work load is complete, at which point the vent port opens, for example under bias.

[0058] Preferably, the method includes the step of allowing the work load to return to the entry end of the work chamber, any fluid between the work load and the entry end exiting through the vent port.

[0059] Preferably, the vent port is biased open, unless high pressure fluid exits the dose chamber, such that the bias is overcome, and the vent valve moves to a closed position of the vent port.

[0060] Preferably, the dose valve member moves to a closed position once the work load moves to or towards the opposite end.

[0061] Preferably, the trigger mechanism reduces the pressure in the discharge chamber.

[0062] Preferably, the work load returns to the entry end by bias, for example but not limited to a fluid cushion / pressure bias, or a compression member on the back, non-working side of the work load, and / or a stretch member on the working side in front of the work load.

[0063] Preferably, once the dose valve member is in a closed position, the discharge chamber and the dose chamber can be filled freely again.

[0064] Preferably, wherein or additionally, filling of the discharge chamber assists in closing the dose valve member.

[0065] Preferably, the method includes the step of optionally venting the high pressure fluid in the dose chamber to atmosphere to prevent the device from operating.

[0066] In another aspect, the invention includes a device as described herein with reference to any one or more of the drawings.

[0067] In another aspect, the invention includes a method of operating a high pressure fluid device as described herein with reference to any one or more of the drawings.

[0068] As used herein, the term "and / or" means "and" or "or", or both.

[0069] As used herein, "(one or more)" following a term means the plural and / or singular form of the term.

[0070] As used in this specification, the term "comprises" means "consists at least partially of". When interpreting statements in this specification that include the term "comprises", the features that follow the term in each statement are required for the feature that precedes the term. Related terms such as "comprises" and "comprised of" are construed in the same manner.

[0071] It is contemplated that a recitation of a numerical range, for example 1 to 10, herein disclosed also incorporates by reference a recitation of all rational numbers within the stated range (e.g., 1, 1.1, 2, 3, 3.9, 4, 5, 6, 6.5, 7, 8, 9, and 10) and any rational number range also within the stated range (e.g., 2 to 8, 1.5 to 5.5, and 3.1 to 4.7).

[0072] The entire disclosure of all applications, patents and publications, to the extent any are cited in the above description, is hereby incorporated by reference.

[0073] Broadly speaking, the present application can also be in 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 or features, and where specific integers are mentioned in this specification and you have the art to which this application pertains, such known equivalents are deemed to be incorporated in the description of the application, as if individually stated.

[0074] 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

[0075] The preferred form of the present application will now be described with reference to the drawings, wherein:

[0076] Figure 1 shows a vertical cross-section through the device according to the application in a rest state without application of high pressure fluid,

[0077] Figure 2 shows a similar view to Figure 1 showing the position of the pressure safety release valve and the supply and discharge ports of the discharge chamber,

[0078] Figure 3 shows a similar view to Figure 1 showing that the discharge chamber is full and from there flows to the dose chamber and fills,

[0079] Figure 4 shows the next stage of Figure 3 when the dose chamber is also full,

[0080] Figure 5 shows the next stage of Figure 4 when the discharge chamber has been discharged,

[0081] Figure 6 shows the next stage of Figure 5 after which the dose valve opens to allow flow from the outlet of the dose chamber to the inlet of the work chamber,

[0082] Figure 7 showsFigure 6 In the next stage, the exhaust valve closes, and the working load (in this case, the piston) is driven towards the opposite end of the working chamber.

[0083] Figure 8 Showing Figure 7 The next phase involves the working loads at the opposite ends of the working modules.

[0084] Figure 9 Showing Figure 8 In the next stage, where the working load (in this case, the piston) begins to return to the working chamber, the exhaust valves now open.

[0085] Figure 10 Showing Figure 9 In the next stage, the working load returns to the valve end of the working chamber.

[0086] Figure 11 Showing with Figure 1 A similar view, with the addition of a tension member to assist the piston or working load return, and / or at least partially act as an exhaust valve, shows the piston in the ready-to-work position at point A and the tension member substantially unstretched; at point B, the piston has moved to the position where it has completed its work, with the tension member extending between the piston and the exhaust valve and in an extended state; and at point C, the piston is moving towards the rear of the working chamber with at least partial assistance from the tension member.

[0087] Figure 12 Schematic diagrams of several embodiments of the present invention are shown. Detailed Implementation

[0088] Now refer to Figures 1 to 12 The preferred embodiment will be described below. The view shown is a vertical cross-section along the main axis, therefore the illustrated embodiment and its components are largely radially symmetrical.

[0089] A novel pneumatically actuated valve design utilizes a pressure venting device of a trigger-force actuated valve to generate efficient energy extraction from high-pressure fluids, such as compressed gases, including but not limited to air or carbon dioxide. A novel pressure-based piston return and exhaust flow control system is also proposed to allow pressure venting behind the workload. This system is tightly integrated with a force-actuated valve suitable for high-circulation-rate systems and also for efficient use of high-pressure fluids.

[0090] refer to Figures 1 to 10 The components and features of the device are described.

[0091] The device 1 has a supply of high pressure fluid 3 from a fluid source 4. In one preferred form, the fluid source 4 is connected to and integral with a similar tool to which the device 1 or tool belongs, such as a hand held nail or fastening gun, a pest trap, a rescue flotation device launcher or a gas pulse cleaner, or other assembly requiring the valve arrangement of the present invention. In this case, the high pressure fluid source 4 is a pressurised vessel or tank containing the high pressure fluid. In other embodiments, the fluid source 4 can be located remotely and fluidly connected, such as in a valve system or the like.

[0092] The high pressure fluid 3 is supplied to the discharge chamber 2 either directly or through a regulator, a relief valve or the like. A regulator is generally required, in addition to its safety aspects and any relief valve, to ensure a constant working pressure is supplied to any trigger system and discharge chamber. Typically, the high pressure fluid is in a tank or vessel and maintains the high pressure fluid at 4500 psi or more and regulates it to a working pressure, such as about 400 to 600 psi. The pressure in the high pressure fluid source can of course be higher as required, such as the capacity required when the device is a tetherless device. The regulator or a valve downstream thereof will prevent the supply of too low a pressure to the discharge chamber to ensure proper operation of the device.

[0093] As shown, the discharge chamber 2 is an annular volume, which has several advantages. It provides a more compact system. Furthermore, given the annular nature of the dosing valve member 11 and that it slides linearly along the main longitudinal axis of the device, then the discharge chamber 2 is at least partially formed by the annular space into which the dosing valve member 11 slides on firing and out of which it slides on moving to the closed position 13. Furthermore, having the discharge chamber 2 as an annular volume then allows the independent vent valve 20 and vent port 21 (described later) to be located internally, preferably concentrically internally (although can be offset from the axis of the dosing valve member 11 if necessary). This provides simplified and optimised venting timing and control.

[0094] Downstream of the discharge chamber 2 is the dosing chamber 5. The two are separated by the dosing valve member 11. The dosing chamber 5 is also an annular chamber, which can also be described as a hollow cylindrical volume or void. Between the two is the dosing valve member 11, briefly described. Between the discharge chamber 2 and the dosing chamber 5 is a flow path 6. The flow path 6 can be through the body of the dosing valve member 11, or can be through a separate flow path to the dosing chamber 5, such as through one or more ports in the wall of each of the chamber bodies, fluidly connecting the chamber bodies. When the discharge chamber 2 is full of working fluid 3, typically at high pressure, then the dosing chamber 5 can be filled through the flow path 6. In a preferred form, the flow path is at least partially provided by the dosing valve member 11, as shown. Alternatively, it can be provided by a leak path around the dosing valve member 11. In one form, the flow path 6 is open between the discharge chamber 2 and the dosing chamber 5 at all times. However, in other forms, it can only be open when the dosing valve member 11 is in the closed position sealing the dosing chamber 5. Figure 3 Downstream of the discharge chamber 2 is the dosing chamber 5. The two are separated by the dosing valve member 11. The dosing chamber 5 is also an annular chamber, which can also be described as a hollow cylindrical volume or void. Between the two is the dosing valve member 11, briefly described. Between the discharge chamber 2 and the dosing chamber 5 is a flow path 6. The flow path 6 can be through the body of the dosing valve member 11, or can be through a separate flow path to the dosing chamber 5, such as through one or more ports in the wall of each of the chamber bodies, fluidly connecting the chamber bodies. When the discharge chamber 2 is full of working fluid 3, typically at high pressure, then the dosing chamber 5 can be filled through the flow path 6. In a preferred form, the flow path is at least partially provided by the dosing valve member 11, as shown. Alternatively, it can be provided by a leak path around the dosing valve member 11. In one form, the flow path 6 is open between the discharge chamber 2 and the dosing chamber 5 at all times. However, in other forms, it can only be open when the dosing valve member 11 is in the closed position sealing the dosing chamber 5.

[0095] In a preferred form there is a restriction 25 in the flow path 6 between the vent chamber 2 and the dose chamber 5. In other forms there can be a check or one-way valve 26 between the dose and vent chambers. In some applications this is not necessary but in high cycle rate applications this would be very beneficial. For example, when the vent chamber pressure is reduced, if there is no one-way valve 26, pressure can flow back from the dose chamber 5 to the vent chamber 2 and then possibly to atmosphere. The check valve can be formed by an O-ring in a groove on the periphery of the dose valve member 2 over a single or series of holes in the groove. Air can flow out of the holes by moving the O-ring but is prevented from returning by the O-ring, for example from the vent chamber to the dose chamber. The check valve can be formed in any other way, for example a poppet or ball check valve. These alternative check valve options can be more suitable in designs where the flow path 6 connecting the vent chamber 2 and the dose chamber 5 does not pass through the dose valve member 11.

[0096] Providing such a check valve has the following advantages,

[0097] a.) Rapid filling of the dose chamber in applications where this is beneficial, for example in high cycle rate (<1 s cycle) applications such as power tools,

[0098] b.) When the pressure in the trigger and dump vent chamber is released, dose chamber gas is not allowed to flow back to the vent chamber and then to atmosphere. This improves the reliability of the actuation mechanism by maximising the opening force bias and improves efficiency as less air is vented to atmosphere.

[0099] c.) The check valve provides additional safety functionality in certain applications (additional check valve mentioned below)

[0100] d.) In the absence of a check valve, there can be a flow restriction through the dose valve member or a separate flow path connecting the vent and dose chambers where the trigger vent flow exceeds the flow through the vent to dose flow path 6.

[0101] In a preferred form the dose chamber 5 is also an annular chamber which can also be described as a hollow cylindrical volume, similar to the vent chamber 2. In the preferred form as shown in Figure 1 it is concentric with the vent chamber 2. Figure 1

[0102] One safety feature is the ability to independently vent pressure from the dose chamber 5 and possibly also from the vent chamber 2. In this way the valve and actuation system 1 can be brought into a safe or non-operational mode. Venting pressure from at least the dose chamber 5 will prevent the dose valve member 11 from firing and hence the work load 17 from firing in the absence of any other locking system for the dose valve member 11.

[0103] ​In preferred forms, the pressure of the discharge dose capsule 5 will also discharge the pressure of the discharge capsule 2 as this is connected by flow paths, but this is done sequentially, first the dose capsule, then the discharge capsule, or in any other controlled manner where the pressure in the dose capsule cannot exceed the pressure in the discharge capsule, so the dose valve member remains closed and so the device cannot fire.

[0104] For example, when the structure of the invention is used in a nail gun, the discharge of the pressure of the dose capsule 5 will disarm the nail gun and prevent it from firing. Even if the trigger is pulled, there can be a further lock preventing the high pressure fluid from flowing into the dump capsule body 2 (and thus into the dose capsule body) or at least into the dose capsule body until the operator is ready to use the tool again and re-activate the tool, thus closing any safety valve from the dose capsule 5 and allowing working fluid into the discharge capsule 2, thus the dose capsule 5 - the tool or at least the device 1 is ready to operate again. Simply discharging the discharge capsule 2 and not allowing further working fluid into it is also an option, but this is not safe as the dose capsule 5 is then ready and will fire the work capsule 8 and any working load 17 therein. For this reason, the "shut down" or "safety assurance" function must be discharged from the discharge capsule 2, not the other way around, it must at least be discharged or released from the dose capsule 5 first or only.

[0105] In preferred forms, the central axis of the discharge capsule 2 and the central axis of the dose capsule 5 are parallel to the main axis 18 of the device, and in preferred forms they are both concentric. However, in certain forms, they can also be independent of each other, although parallel.

[0106] To improve safety, there can be accidental pressure loss safety check valves 29A and 29B, which are a function needed in fastening applications.

[0107] Where the first is a catastrophic supply failure check valve 29A. In the extreme event of a large leak flow path upstream of the trigger, this can cause the discharge capsule 2 to lose pressure. A straight check valve, where the supply from the discharge capsule into the discharge capsule 2, prevents the discharge capsule 2 from backfilling through the leak and triggering a fire event. Depending on the housing type and integrity of the system and the flow of other components, it can be decided that this safety function is not needed, although this must be a well thought out decision.

[0108] Where the second is a slow leak safety check valve 29B. In the event of an accidental slow leak or normal pressure loss through pressure supply venting, the dose capsule 5 must not be allowed to be at a higher pressure than the discharge capsule 2, as this will cause a fire event. The check valve upstream of the catastrophic supply failure check valve achieves this. As the supply pressure drops below the dose capsule pressure, air flows from the dose capsule out of the leak safety check valve and eventually out of the failure leak point to atmosphere.

[0109] The triggering mechanism can use a slide valve that releases the pressure in the discharge chamber 2. Alternatively, a slide valve can be used to interrupt the flow of working fluid 3 to the discharge chamber 2 and connect the discharge chamber 2 to the atmosphere. The slide valve can then return to the first position, in which it closes the vent and reconnects the supply to the discharge chamber 2. This would allow for the supply of high-pressure fluid to both the discharge chamber and the dosing chamber in the first position, and then, when moved to the second position, the supply of high-pressure fluid to be completely cut off, connecting the discharge chamber to the atmosphere or a reference or lower pressure. This then allows the discharge chamber to release its pressure, thereby opening the dosing valve in the dosing chamber and charging the working chamber or working load 31, which then performs work.

[0110] A dose valve assembly 11 is located between the discharge chamber 2 and the dose chamber 5. The dose valve assembly 11 has the following characteristics: Figure 2 The closed position 13 shown and as Figure 7 The open position 15 is shown. In one embodiment, the dosing valve member 11 is biased closed. The dosing valve member 11 has an annular sealing surface 12, which in a preferred embodiment is or substantially a blunt or rounded blade, as shown. This annular sealing surface 12 seals sequentially onto the sealing member 34 in the closed position 13. In a preferred embodiment, the sealing member 34 is an O-ring, a square-section ring, an X (or "quadrilateral") ring, or an integrated co-molded sealing element, or a rubber or rubber-like material with a similar cross-section, as shown, although other forms are also acceptable as long as they can be sealed onto the sealing surface 12 as needed, and the opposite arrangement can also be used, as described below. The sealing member 34 is, for example, on the wall of the dosing chamber or near its proximal end, such as Figure 2 As shown. Alternatively, the sealing member 34 may be on the dosage valve member 11, and the sealing surface 12 may be on the wall of the dosage chamber or its proximal end.

[0111] When the dosage valve component is in the open position 15, such as Figure 6 and 7 As shown, a gap 16 appears, is created, or is formed between the annular sealing surface 12 and the sealing member 34. This forms an outlet 7 from the dosing chamber 5 to the working chamber 8. This allows pressurized working fluid to enter the working chamber 8.

[0112] In a preferred embodiment, the dosage valve component 11 is biased closed, for example by means of the dosage spring 35.

[0113] As shown, the dosage valve member 11 has an elongated skirt 23 extending along and parallel to its linear axis 18. When in the open position 15, this elongated skirt 23 is received into the discharge chamber 2. In a preferred embodiment, the elongated skirt 23 fills the entire discharge chamber 2. When in the closed position 13, the elongated skirt partially forms the wall of the annular gap, i.e., the discharge chamber 2. Fluid pressure in the discharge chamber acts on the rear surface 36 of the dosage valve member 11 to partially maintain its closed position. Therefore, this fluid pressure further forces the discharge valve member 11 into the closed position 13, thereby increasing the seal between the annular sealing surface 12 and the sealing member 34. This is combined with or replaces the dosage spring 35.

[0114] The front surface 37 of the dosing valve component 11 is also subjected to pressure from the working fluid 3 in the dosing chamber. However, the dosing valve component is held in the closed position by the pressure difference and / or area difference with the discharge chamber. The dosing valve component 11 only opens when the pressure in the discharge chamber decreases. Due to the high pressure, this opening is very rapid, occurring within 0.01 to 2 seconds, preferably less than 0.5 seconds.

[0115] Under steady-state conditions, the pressure between the dosing chamber 5 and the discharge chamber 2 will be substantially the same, and this is generally true for most rapid ignition scenarios. However, the discharge chamber 2 has a larger area for pressure action on its rear surface 36 than the front side presented to the dosing chamber 5, thus keeping the dosing valve assembly 11 closed. The dosing chamber 5 will only have sufficient force to open the dosing valve assembly 11 when the pressure in the discharge chamber 2 decreases, is discharged, vented, or released, for example, by means of a triggering system as described above.

[0116] Downstream of the dosing chamber 5 and its outlet 7 is the working chamber 8. It has an inlet 9 at the inlet end 10, which receives working fluid 3 from the dosing chamber 5 when the dosing valve component 11 moves to the open position 15.

[0117] The working chamber 8 contains a working load 17. This can be a fixed working load, such as, but not limited to, a piston reciprocating within a piston, or it can be a non-fixed working load, such as a projectile or the like ejected from the working chamber 8. Alternatively, there may be no physical object in the working chamber, such as a piston or projectile; it could be a pressure wave that is then released into or from the chamber to do work.

[0118] In a preferred embodiment, the working load is located at the inlet end 10, and there is preferably no gap or volume behind it before the dosing valve component 11 is opened.

[0119] Also present downstream of the dosing chamber 5 and the dosing valve assembly 11 is the exhaust valve 20. This can be upstream of the working chamber 8, or at the same flow location as the working chamber 8, i.e., the working fluid 3 will operate on both at the same or similar time.

[0120] The exhaust valve 20 also has the following features: Figure 3 The opening position shown and as Figure 7 The closed position is shown. When in the open position, it exposes one or more vents 21, and when closed, it closes these vents. In a preferred embodiment, the vent valve 20 is biased to the open position, for example by a vent spring 38, or additionally or alternatively, by a tension member 28 as described below.

[0121] When the dosing valve component 11 is opened, the exhaust valve 20 moves to the closed position through the working fluid 3, thereby closing the exhaust port 21 and providing a closed volume for the working chamber 8.

[0122] When the working chamber 8 is exposed to the pressurized working fluid 3, the working load therein receives energy from the working fluid and is acted upon, for example, it moves to the opposite end 22 of the working chamber 8. It can then be discharged from there, for example, as a projectile, or it can then return, for example, as a piston.

[0123] As described above, one method of returning the payload to the launch position (i.e., near the dose valve end or inlet end) is to use an air cushion on the front side 31 of the payload, for example, on the front side 31 of the piston. This is formed by the return capsule 39. A spring or similar device can also be used on the rear side.

[0124] Another method, as an alternative or supplement, is to use a tension member 28, such as a piston, on the rear side 32 of the working load. Figure 11 As shown in AC. The tension member 28 can be, for example, an elastic element, such as, but not limited to, silicone or similar materials, which holds the working load near or against the inlet end of the working chamber in its relaxed or near-relaxed state.

[0125] When the actuation system 1 is activated and the working load moves downwards into the working chamber 8, the tensioning element 28 extends. Upon completion of the ignition stroke, the working load needs to return to the valve end or inlet end 10 of the working chamber 8, and the pressure on the working side or rear side of the working load decreases. The tensioning element itself, or in combination with energy stored in the air cushion or other energy on the front side 31 of the working load, then contracts again. In this way, it pulls the working load back to the inlet end 10 of the working chamber 8 while the air cushion pushes it forward.

[0126] The tension member 28 can be connected to the interior of the working chamber 8 or can extend through the wall of the working chamber and be connected or constrained by an outer surface, body, fixing or fastening method.

[0127] In other forms, the tension member can be connected to the exhaust valve 20, such as a seat, piston, or moving element, like Figure 11As shown in AC. As described above, the exhaust valve 20 closes the exhaust port 21 when the working load travels downward along the working chamber 8 during ignition. When the working stroke is completed or nearly completed, the exhaust valve 20 opens the exhaust port 21 at regular intervals to reduce the pressure at the front of the working load, thereby facilitating its return to the starting position at the inlet end 10 of the working chamber 8.

[0128] When tension member 28 is connected to exhaust valve 20, tension member 28 is adjusted to at least partially or fully assist in controlling the movement of exhaust valve 20 and opening exhaust port 21. This is an additional method of adjusting and timing the opening of exhaust port 21 by applying force to the exhaust element based on the position of the working load. This can provide an advantage because it can be used to completely remove piston return chamber 39 (thus reducing the number of parts, the possibility of seal failure, and / or complexity), or remove some of its components, such as the one-way check valve, or at least allow for a reduction in the size of piston return chamber 39 or will allow piston return chamber to operate effectively at lower pressures.

[0129] Furthermore, if the tensile member 28 is an elastic material, at least for the extension it will undergo, then it will generally decrease its cross-sectional area as it extends and increase its cross-sectional area as it expands. This is clearly shown in... Figure 11 In AC.

[0130] like Figure 11 The tension member 28 shown can be connected at least partially via the vent valve 20. Therefore, as the tension member 28 extends, it will reduce its cross-sectional area, such as... Figure 11 As shown in B, the portion connecting to the exhaust valve 20 is opened, typically when the working load is at the limit of its stroke, thus the high-pressure fluid has finished its work and the working load is ready to return. The exhaust valve 20 will then open under the aforementioned action, and optionally also due to the tension and thinning of the tension member 20, and will move to the open position, away from port 21. The thinning of the tension member 28 then allows for further exhaust through the body of the exhaust valve 20, in this case centered.

[0131] This feature can be further used to time the opening of the exhaust valve 20 and the exhaust port 21. This reduces the linear movement required for the exhaust valve 20 to open and close the port 21.

[0132] The device is at least partially contained within it and forms some structures as described by the housing 33. The device has a main axis 18 that runs its main length.

[0133] Now refer to Figures 1 to 10 The operation method of the valve and actuation system consistent with the present invention is described. The direction of movement of the valve, working load, and working fluid 3 is indicated by arrows, and the position of the working fluid is indicated by cross-hatching.

[0134] exist Figure 3 In this process, the discharge chamber 2 fills faster than the dosing chamber 5, thereby creating or increasing the bias in the closing and sealing force of the dosing valve component 11. This difference in filling rate is unavoidable because the dosing chamber 5 is supplied by the discharge chamber 2 via flow path 6, and any restriction 25 of valve 26 in this flow path results in a pressure difference that depends on the flow rate in and out of the discharge chamber 2. The dosing chamber 5 can also be filled via a check valve. Figure 4 In the middle, dosing chamber 5 shows that it has been filled.

[0135] exist Figure 5 When trigger mechanism 27 is actuated, discharge chamber 2 is discharged or released, in this case to a lower pressure, such as atmospheric pressure or reference pressure. Due to the pressure zones of the inner seal, outer seal, and face seal, the force balance on the dosing valve component 11 is exchanged. In other forms, the discharge chamber can vent to the working chamber 8 (which would slightly improve efficiency and partially alleviate the need for extremely low efficiency in the dosing chamber 5).

[0136] Then dose valve 5 is in Figure 6 The valve opens, and pressurized gas flows to fill the small space behind the working load 17, in this case, as shown in the figure, which is the piston.

[0137] a. Further increase the opening force bias on the dosing valve component 11 to fully open it and expel any remaining gas from the discharge chamber 2.

[0138] b. Start energizing the exhaust valve to begin moving it to the closed position.

[0139] c. Begin moving the working load down into the working chamber.

[0140] like Figure 7 As shown, the working fluid 3 in the dosing chamber 5 expands, the pressure drops, and the working load 17 is pushed down into the working chamber 8. As shown, a piston-shaped exhaust valve 20 is sealed on its face seal to seal the exhaust port 21, thereby sealing the working chamber behind the working load.

[0141] The working load, in this case, is the piston, which moves through... Figure 8 The return capsule check valve 40 allows the working capsule pressure on the front side 31 of the working load to expand into the piston return capsule 39. If the dosing valve assembly 11 is fitted with a force bias spring 35 (not shown), it will close the dosing valve assembly 11 now, slightly earlier, or slightly later depending on the adjustment.

[0142] like Figure 9As shown, the exhaust pressure is reached, causing the exhaust spring 38 to overcome the pressure and open the exhaust valve 20, thereby opening the exhaust port 21. This allows the working load to return or be loaded, driven by the working fluid 3 in the piston return chamber 39 and / or the tension member 28. If a dose spring 35 is included, the dose valve member 11 moves to the closed position 13 at this stage—but if not, the dose valve member 11 will be in the open state, and the dose chamber 5 will be fully vented into the working chamber and then discharged into the atmosphere after the exhaust port opens.

[0143] The remaining working fluid 3 following the working load 17 is discharged into the atmosphere through port 21, and the working load 17, as Figure 10 As shown, return to entry point 10.

[0144] When the trigger is pulled or otherwise activated, the supply of working fluid to the ignition mechanism, i.e., to the discharge chamber 2, is cut off. Then, when the trigger mechanism 27 is released, the discharge chamber 2 and the dosing chamber 5 are rapidly refilled. In other configurations, activating the trigger mechanism 27 will temporarily shut off the supply, but will subsequently refill the discharge chamber 2 even if the trigger mechanism is not released.

[0145] The release of trigger 27 can be automatic, locked, or popped up in some way to allow refilling while the trigger is still pressed, meaning the trigger is only effective for a short time, or it can rely on another triggering element, such as the safety element used in a nail gun, which ensures that the tool is close to the workpiece as part of the triggering action.

[0146] Exhaust can also occur independently of the position of the dosage valve component 11.

[0147] This invention has potential applications in penetrating fastening tools, pneumatic motors, projectile launchers, rapid pulse air or fluid valves, etc. The working fluid can be a compressed gas, and preferably highly compressed, using 4500 PSI or higher as a source, although this can be reduced, for example, to air, carbon dioxide, nitrogen, or the like. Alternatively, the working fluid can be a hydraulic fluid, a supercritical fluid, or a similar fluid.

[0148] Compared with the prior art, the present invention offers many advantages:

[0149] The valve is highly efficient and can extract a high percentage of usable energy from high-pressure fluids. This allows for more repetitions from the high-pressure fluid source, thereby reducing costs associated with replenishment sources and increasing the ease of using motion transmission devices.

[0150] • Due to the system's closed-loop design and the significant reduction in fluid pressure from the start to the end of the cycle, the noise pollution generated by the device is greatly reduced and its availability is improved.

[0151] • The less pressurized fluid required per cycle, the more repetitions can be safely achieved.

[0152] • The smaller volume of pressurized fluid discharged during the exhaust of the actuation system reduces exhaust requirements and potential safety hazards associated with this process. For example, when the pressurized fluid is carbon dioxide, the risk of dry ice formation in the exhaust is reduced.

[0153] The valve opening area is relatively large compared to the volume of the dosing chamber, allowing for rapid valve opening. Therefore, the fully charged high-pressure gas exits the dosing chamber very quickly, and the valve can return to the closed state shortly after opening. This allows the mechanism to operate efficiently at a very high cycle rate, and the dosing and discharge chambers can be filled and ready for restarting even as the working load moves downwards along the chamber body.

[0154] • Allows for high power density and extremely efficient aerodynamic actuation using reliable pressure venting, force bias seals, and triggers.

[0155] The above description of the present invention includes its preferred form. Modifications may be made thereto without departing from the scope of the invention.

Claims

1. An apparatus for controlling high-pressure fluid, comprising: The discharge chamber, being an annular volume, is used to receive high-pressure fluid from a high-pressure fluid source. A dosing chamber, downstream of the discharge chamber, is used to receive a flow of the high-pressure fluid from the discharge chamber via a flow path from the discharge chamber to the dosing chamber, the dosing chamber having an outlet. A working chamber, having an inlet at one end, is located downstream of the dosing chamber and its outlet. A dosage valve component having an annular sealing surface around the inlet end, wherein the discharge chamber and the dosage chamber are separated by the dosage valve component. in, When the dosage valve component is in the closed state, the annular sealing surface contacts the annular seat to seal the outlet; and when the dosage valve component is in the open state, a gap exists between the annular sealing surface and the annular seat to allow the high-pressure fluid to move from the outlet to the inlet end, and to prevent the flow of high-pressure fluid from the high-pressure fluid source into the dosage chamber or the discharge chamber. The high-pressure fluid in the discharge chamber at least partially keeps the dosage valve component in the closed position until the pressure of the high-pressure fluid in the discharge chamber decreases, thereby releasing the dosage valve component to the open position.

2. The apparatus according to claim 1, wherein, The high-pressure fluid flowing into the working chamber does work on the working load to discharge it from or move it to the opposite end of the working chamber.

3. The apparatus according to claim 2, wherein, When the working load is driven from the inlet end to the opposite end of the working chamber, no high-pressure fluid source is available for the fluid connection of the working chamber.

4. The apparatus according to claim 1, wherein, The dosage valve component slides linearly.

5. The apparatus according to claim 2, wherein, The dosage valve component slides along a linear axis parallel to the main axis of the device.

6. The apparatus according to claim 5, wherein, The working load slides linearly from the inlet end along the working chamber to or toward a relatively distant end parallel to the main axis of the device.

7. The apparatus according to claim 6, wherein, The working load is either a stationary piston or a ejected ejector.

8. The apparatus according to claim 1, wherein, The emission chamber, the dosing chamber, and the working chamber are concentric or parallel to the main axis of the device.

9. The apparatus according to claim 2, wherein, An exhaust valve is present, which is biased to an open position at or toward the inlet end and closes the exhaust port of the working chamber upon actuation of the high-pressure fluid exiting the dosing chamber.

10. The apparatus according to claim 9, wherein, When the working load is at or near the opposite end of the working compartment, the exhaust port opens under the effect of offset.

11. The apparatus according to claim 9, wherein, The exhaust valve is a piston or diaphragm that is at least partially surrounded by the dosing valve component.

12. The apparatus according to claim 1, wherein, The dosage valve component is at least partially biased in the closed state.

13. The apparatus according to claim 1, wherein, The dosing chamber is a hollow volume that extends radially outward or inward from the working chamber.

14. The apparatus according to claim 1, wherein, The flow path passes through the dosage valve component.

15. The apparatus according to claim 14, wherein, The flow path is located in the skirt of the dosage valve component.

16. The apparatus according to claim 1, wherein, There are restrictions in the flow path from the discharge chamber to the dosing chamber, such that even when the dosing chamber is being filled, the discharge chamber increases the closing pressure of the dosing valve component.

17. The apparatus according to claim 1, wherein, A one-way valve is present in the flow path from the discharge chamber to the dosing chamber.

18. The apparatus of claim 1, further comprising a check valve in the flow path from the discharge chamber to the dosing chamber, wherein, The check valve is configured to prevent the flow of high-pressure fluid from the dosing chamber to the discharge chamber in response to the device being triggered.

19. The apparatus according to claim 1, wherein, The pressure in the discharge chamber is reduced by a triggering mechanism.

20. The apparatus according to claim 19, wherein, The triggering mechanism releases the pressure in the discharge chamber into the atmosphere.

21. The apparatus according to claim 2, wherein, The working load is returned to the inlet end via a fluid pad on its back, a spring on the rear or front side, or a tension member connected to the inlet end from the front or toward the inlet end.

22. The apparatus according to claim 9, wherein, The exhaust valve is spring-biased.

23. The apparatus according to claim 9, wherein, The exhaust valve is biased by a tension member connected between the working load and the exhaust valve.

24. The apparatus according to claim 1, wherein, A safety valve is provided to release pressure from the dosing chamber to prevent the device from operating.

25. The apparatus according to claim 1, wherein, A slow-leak safety valve is provided to release fluid pressure from the dosing chamber if the pressure supplied by the high-pressure fluid drops below the pressure in the dosing chamber.

26. A method of operating a high-pressure fluid device, comprising the following steps: The discharge chamber, which is annular in volume, is filled with high-pressure fluid. The high-pressure fluid acting on the rear side of the dose valve component increases the sealing pressure of the dose valve component to keep it in a closed state. The dose valve component has an annular sealing surface between the outlet of the dose chamber and the inlet of the working chamber. The dose chamber is downstream of the discharge chamber, and the working chamber is downstream of the dose chamber and its outlet. The discharge chamber and the dose chamber are separated by the dose valve component. High-pressure fluid is transferred from the discharge chamber to the dosing chamber via a flow path. The pressure in the discharge chamber is reduced, causing the high-pressure fluid in the dosing chamber to act on the front side of the dosing valve component, forcing the dosing valve component to be in an open state, with a gap between the inlet and the outlet. When the dosing valve component is open, it prevents the flow of high-pressure fluid from the high-pressure fluid source into the dosing chamber or the discharge chamber. High-pressure fluid then enters the working chamber from the dosing chamber to work the working load inside the working chamber.

27. The method according to claim 26, wherein, The discharge chamber and the dosing chamber are at nearly the same pressure when they are filled before decompression.

28. The method according to claim 26, wherein, The exhaust valve moves to a position where it closes the exhaust port from the work chamber until the work is completed on the work load, at which point the exhaust port opens.

29. The method according to claim 28, wherein, The method includes the step of allowing the working load to return to the inlet end of the working chamber, and any fluid between the working load and the inlet end is discharged through the vent.

30. The method according to claim 28, wherein, The vent is biased to the open position unless the high-pressure fluid leaves the dosing chamber to overcome the bias and the vent valve moves to the closed position of the vent.

31. The method according to claim 26, wherein, Once the working load is moved to or toward the opposite end of the working chamber, the dosing valve component moves to the closed position.

32. The method according to claim 26, wherein, The trigger mechanism reduces the pressure in the emission chamber.

33. The method according to claim 26, wherein, The working load is returned to the inlet via a bias, the bias being selected from any of the following: a) Fluid pad / pressure bias. b) or compression members on the back side, working loads on the non-working side, and / or c) The tension member on the front working side of the working load.

34. The method according to claim 26, wherein, Once the dosing valve component is in the closed position, the discharge chamber and the dosing chamber are freely refilled.

35. The method according to claim 26, wherein, The filling of the discharge chamber helps to close the dosing valve component.

36. The method according to claim 26, wherein, The method includes venting the high-pressure fluid in the dosing chamber into the atmosphere to prevent the device from operating.

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