Hydraulic fuse with pressure regulator

Abstract: A hydraulic fuse monitors the quantity of fluid passing through it and blocks such flow when a selected quantity has passed, the fuse including a body structure (13) containing a cavity (14), a primary piston (22) in the cavity movable endwise to control fluid flow through a first port (23); a sleeve (17) and a slider (18) in the cavity (14) and in the path of fluid flow to the primary piston (22); a regulator spring (19) to urge the sleeve (17) in one axial direction; and fluid flow control slots (33 to 36) formed by the sleeve (17) and slider (18) to control flow both to the piston (22) and to the first port (23); characterised in that the piston (22) begins its movement toward the port (23) as the flow rate through the fuse reaches a threshold, and beyond that threshold, relative axial movement between the sleeve (17) and slider (18) acts to maintain nearly constant the fluid pressure drop across primary slot means of the control slots and controllably meters fluid flow to the piston (22) via metering slot means of the control slots.

Description: Technical Field This invention relates generally to hydraulic "fuse" devices; and more particularly, it concerns an in-line hydraulic fuse, or sensor, that monitors the quantity of hydraulic fluid that passes through the device, and then blocks the flow when a pre-selected quantity of fluid has passed through. Devices to accomplish the above functions have employed buoyant pistons and vane motors. Testing of a buoyant piston device showed it to be undesirably and inherently sensitive to changes in attitude of the device; and it was also undesirably critical with respect to fit and clearances. Vane motors, on the other hand, are undesirably expensive. There is need for a simple, effective device having few manufactured parts, relatively high force levels of sensing mechanism, and with flow/volume characteristics which can be readily tailored, i.e. fitted, to many different design requirements. US Patent No. 4655245 describes a fuse that overcomes many of the deficiencies and problems of such prior devices. This fuse employs an accurate pressure regulator which senses flow through the fuse and regulates a proportional but smaller flow when the desired fluid quantity has passed through the fuse. The pressure regulator consists of a sleeve that is axially movable on an inner hollow sleeve guide and is spring loaded axially in one direction, and fluid flow control slots formed on the sleeve and sleeve guide that control flow through the fuse and also to the movable piston dependent upon the relative positions of the sleeve and sleeve guide. As the flow rate through the fuse reaches a threshold, the piston begins its movement towards a shut-off port. As the flow rate increases above the threshold, the sleeve moves against the spring loading on the sleeve guide and controls opening of the control slots such that the fluid pressure drop across a primary slot is maintained constant, and the fluid flow to the piston is metered via a metering slot. Disclosure of the invention It is an object of the invention to provide an improved fuse compared with the above prior art fuses. According to the present invention, a hydraulic fuse comprises a body structure containing a cavity; a primary piston in the cavity and moveable endwise to control fluid flow through a first port; a sleeve and a slider in the cavity and in the path of fluid flow toward the primary piston, the sleeve and slider being coaxially relatively axially moveable; a regulator spring acting to urge the sleeve in one axial direction; and fluid flow control slots formed by the sleeve and slider to control flow both to said primary piston for controllably displacing the same, and to said first port; the primary piston being such that it begins its movement toward said first port as the forward flow rate through the fuse reaches a threshold, and above that threshold, relative axial movement between the sleeve and slider acts to maintain substantially constant the fluid pressure drop across primary slot means of said control slots, and controllably meters fluid flow to the primary piston via metering slot means of said control slots, for displacing said primary piston as aforesaid, whereby the primary piston is displaced to close the first port after a required quantity of fluid has passed through the fuse; characterised in that the slider is guided within the sleeve, and is hollow to pass flow via said primary slot means from the slider interior to the slider exterior, and via said primary slot means toward said first port. The arrangement of the hollow slider within the sleeve allows the use of smaller diameter components for a given amount of fluid flow compared with the known arrangement of a moveable sleeve on a hollow inner sleeve guide. This in turn makes it easier to manufacture components with a tight fit, and also produces a more compact fuse device. Preferably, the control slot means communicates with an annular cavity within which the sleeve is axially moveable; and the control slots may typically include primary slot means extending radially through the sleeve to pass the flow to the first port in full flow axial position of the sleeve. The control slots may also include threshold slot means associated with the primary slot means to initiate flow through the sleeve to the first port when the sleeve is in, or approximately in, no-flow position. These and other objects and advantages of the invention, as well as the details of an illustrative embodiment, will be more fully understood from the following specification and drawings, in which: Description of the Drawings Fig. 1 is an external elevation; Fig. 2 is a section taken in elevation through the fuse; Fig. 3 is an enlarged fragmentary section showing elements of the fuse; and Figs. 4 - 6 are schematic views showing three different modes of fuse operation. Best Mode of Carrying Out the Invention The illustrated hydraulic fuse 10 is adapted to monitor the quantity of hydraulic fluid passing through it, for example in direction of arrows 11 and 12, and then block such flow when a selected quantity of fluid has passed through the device. The fuse includes cylindrical body structure 13 containing cavity structure 14. Located within the latter is a tubular housing 15 that extends coaxially within the cylinder 13. The housing includes a rearwardmost enlarged section 15 a serving as a tubular plug telescopically fitting the cylinder bore 13 a intermediate sections 15 b and 15 c , and a forward reduced section 15 d . The latter threadably interfits a threaded bore 16 a of a plug 16, closing same. Plug 16 is tubular and is received in the forward end of the cylinder. Section 15 c is reduced relative to section 15 b . Housing 15 is fixed to body 13, via end flanges 15 a ′ and 16 b . A sleeve 17 and a slider or slide 18 are coaxially located in the cavity structure, as for example within section 15 b of the housing. These elements are coaxially relatively movable, and a regulator spring, such as coil spring 19, acts to urge the sleeve in one axial direction, i.e. rightwardly, in the drawings. Note in Fig. 3 and Fig. 4 that spring 19 engages leftward facing shoulder 17 a of the sleeve, urging the rightward facing end shoulder 17 b of the sleeve against leftward facing shoulder 20 of the housing 15. The cylindrical outer surfaces 18 a of the slider 18 may be guided for axial movement by the sleeve bore 17 c , as seen in Fig. 3. The leftward end of the spring engages an annular axially slidable cup or seat 21. The slider is also axially movable, as between leftward (reverse flow position) as seen in Figs. 3 and 6, and rightward (forward position) as seen in Fig. 5, and an annular "reset" spring washer 26 resists rightward movement of the slider. That washer is captivated between seat 21 and flange 18 b of the slider retained by retaining ring 90. A primary piston 22 is located in the cavity structure within the cylinder, to move axially endwise for controlling fluid flow through first radial ports 23 formed through the wall of 15 c . As shown, the piston 22 is annular and its bore 22 c is slidable along the tubular section 15 c of the housing. As the piston moves rightwardly, its head 22 a ultimately closes the four exit ports 23 in section 15 c to block forward flow of fluid via such ports (such forward flow seen in Fig. 4) and to exit ports 24 in the plug 16. A compression spring 25 in cavity 14 yieldably resists forward movement of the piston, the spring leftward end engaging piston flange 22 b . Seals 27 and 28 respectively seal off between the piston bore 22 c and the guide section 15 c , and between the piston flange outer surface 22 d and the bore 13 a of cylinder 13. The tapered forward end 15 g of the piston head seats against a tapered seal 30 on plug 16, in extreme rightward position of the piston, the piston then closing exit ports 23. When the piston is retracted to the left, as seen in Fig. 4, fluid may flow forwardly via threshold orifice 18 e to the interior 31 of the housing section 15 c , then out ports 23, and through angled ports 24, to the hollow interior 32 of the plug 16, and then rightwardly. This is the forward flow mode, as seen in Fig. 4. Central orifice 18 e through the right end wall of the slide is used for threshold flow. Threshold flow is that flow rate below which the fuse will not function. This is to allow normal leakage downstream of the fuse to occur without limit. At this time, flow control slots 33 formed by the slider are closed by the sleeve, as best seen in Fig. 3. Slot 33 is formed through the wall 18 d of the slide. Fluid flow control slots are also indicated at 35 (a metering slot through the sleeve wall) and at 36 (a slot through the wall 18 d of the slide). As the slide is urged forwardly (rightwardly) by pressure application on leftward facing surfaces 37 and 38, and relative to the sleeve, as best seen in Fig. 5, slot 36 ultimately communicates with slot 35, (shoulder 18 g registers with slot 35) passing fluid to the piston chamber 39 via slots 22 f for driving the piston rightwardly when leftward force exerted by piston spring 25 is overcome. Slots 35 and 36 may be regarded as primary slot means. Note that regulator spring 19 resists slider movement to the right, so that such rightward movement of the piston cannot take place until the leftward force of spring 19 is overcome by rightward fluid pressure on the slider, and until the fluid pressure in the chamber 39 and exerted rightwardly on piston face 40 overcomes the leftward force of spring 25. Fused Forward Flow This mode of operation begins when the forward flow rate through the fuse approaches the upper threshold point as determined by orifice 18 e . See Fig. 4. (The threshold point for the fuse may for example be between 0.025/0.04 l/s (.40/.60 GPM)). The upper threshold is set by the orifices, piston area and spring force, and is exemplified by pressure level in zone 51. At flow rates near the upper threshold, the slide will begin to move due to pressure exerted on 18 a , opening and closing the area between it and the sleeve, in order to maintain a nearly constant pressure drop, the value of which is set by the regulator spring force and the area of the slide. Since the pressure drop across the slide is nearly constant, due to overlap of ports 33 and 34, flow through the fuse can be related to the position of the slide. The position of the slide also dictates the opening of the metering slot 35 leading to the piston, and therefore the flow rate delivered to the piston cavity or chamber 39. This, in turn, determines the closing time of the fuse. Therefore, at any flow rate, the amount of fluid which has flowed through the fuse is related by the orifice coefficients of the slide opening 36 and the metering slot 35 and their respective flow areas that come into registration. Testing has shown that the relationship between these two orifices is nearly parallel, so that a rectangular metering slot 34 can be used. Therefore, the quantity of fluid which has flowed through the fuse is directly related to the position of the slide. As inlet flow increases, a point is reached that provides a sufficient differential pressure across the piston to fully compress the piston spring, so that the piston moves rightwardly. After the required amount of fluid volume has been reached, flow is shut off by sealing at the interface of the piston end 15 g and the fusing seal 30. This type of seal is virtually leak-free. In order to reduce the impact on the seal at shut-off, the exit holes 23 are located leftwardly of the seal. When these holes are closed off by the piston, the fluid flow is greatly reduced, thereby reducing the tendency to unseat the fusing seal. With the reduced flow rate, the pressure differential across the piston rises rapidly and moves the piston taper 15 g to the seal 30 quickly. The built-in threshold feature is accomplished by having the pressure required to move the piston to the fusing position greater than the differential pressure across the pressure regulator at the threshold flow. Reverse Flow In this mode, as seen in Fig. 6, the piston 22 is to be displaced to the left, to seat at 50. Fluid flows leftwardly via ports 24 and then 23 to interior 31, and then reversely through ports 34 and 33 to interior 51 of the slide. It then exits to the left of the unit. Fluid pressure acting on the sleeve, displaces it leftwardly to overcome the regulator spring 19, and the left end 17 h of the sleeve seats on the seat 21, at which time the reverse flow path is open. Reset Mode Fig 2 shows the device in reset mode, which occurs when the differential pressure across the fuse i.e, acting in chamber 39 on the area of the piston falls to a level that can be overcome by the piston spring 25. For example, this point may be approximately 0.827 bar (12 psi). In the reset mode the slide is seated on the retaining ring 21 by the reset spring 26 which is a thin wave spring. In this position, a flow path is opened from the piston chamber 39 via slots 35 and 36 to interior 51, and then forwardly via slots 33 and 34, whereby fluid in the piston cavity is forced or exhausted through and out the inlet ports 33 and 34. In order, for example, to achieve a total reset of the fuse in under 2.0 seconds a 0.345 bar (5 psi) pressure differential is required. See Fig 2. Since the pressure drop across the slide will never exceed a set limit, such as 18 psi (1.241 bar) even at extreme flow rate, the diametral clearance between the sleeve and slide can be quite large. In one design, this clearance is 0.0015/0.0025 cm (.0006/.0010 inches) which allows the components to be interchangeable with no matched sets. The spring seat cup 21 rests on the retaining ring 90 when in the non-active condition. The purpose of the spring washer 26 is to position the slide 18 in the bottomed position against the retaining ring. In this position the reset ports in the sleeve are open so that the fluid in the fusing ports in the sleeve are open whereby the fluid in the fusing cavity can flow out, thereby allowing the fuse piston to return to its normal position. O-ring or packing seals are indicated at 65, 28, 27 and 66.

Claims: A hydraulic fuse which monitors the quantity of hydraulic fluid passing through it and blocks such flow when a selected quantity of fluid has passed, the hydraulic fuse comprising a body structure (13) containing a cavity (14); a primary piston (22) in the cavity (14) and movable endwise to control fluid flow through a first port (23); a sleeve (17) and a slider (18) in the cavity (14) and in the path of fluid flow toward the primary piston (22), the sleeve (17) and slider (18) being placed coaxially with respect to each other relatively and axially movable; a regulator spring (19) acting to urge the sleeve (17) in one axial direction; and fluid flow control slots (33 to 36) formed by the sleeve (17) and slider (18) to control flow both to said primary piston (22) for controllably displacing the same, and to said first port (23); the primary piston (22) being such that it begins its movement toward said first port (23) as the forward flow rate through the fuse reaches a threshold, and above that threshold, relative axial movement between the sleeve (17) and slider (18) acts to maintain substantially constant the fluid pressure drop across primary slot means of said control slots, and controllably meters fluid flow to the primary piston (22) via metering slot means of said control slots, for displacing said primary piston (22) as aforesaid, whereby the primary piston (22) is displaced to close the first port (23) after a required quantity of fluid has passed through the fuse; characterised in that the slider (18) is guided within the sleeve (17) and is hollow to pass flow via said primary slot means from the slider interior to the slider exterior, and via said primary slot means toward said first port (23). A fuse as claimed in claim 1 wherein the regulator spring (19) urges the sleeve (17) in a direction acting to reduce fluid flow through said primary slot means located in the sleeve (17) and slider (18). A fuse as claimed in either one of the preceding claims wherein said control slots include metering slot means communicating with an annular cavity (15 b ) within which the sleeve (17) is axially movable. A fuse as claimed in any one of the preceding claims wherein said primary slot means extends radially through the sleeve (17) to pass the flow to said first port (23) in a full flow axial position of the sleeve. A fuse as claimed in any one of the preceding claims wherein said primary slot means includes slot means to initiate flow through the sleeve (17) to said first port (23) when the sleeve is in, or substantially in, a no flow position. A fuse as claimed in any one of the preceding claims wherein said control slots include metering slot means in the sleeve (17) and axially spaced from primary slot means in the slider to meter said flow to the primary piston. A fuse as claimed in any one of the preceding claims in which the primary piston (22), the sleeve (17) and the slider (18) are all tubular and are relatively axially movable. A fuse as claimed in any one of the preceding claims in which a main spring (25) urges the piston (22) in an axial direction opposite to the said one axial direction in which the regulator spring (19) acts on the sleeve (17). A fuse as claimed in claim 8 which has a forward flow mode in which flow is passed via the slider (18) and sleeve (17) and is metered and reduced as the slider (18) moves forwardly to provide constant pressure drop; and also in which fluid pressure passes via the slider (18) and via the sleeve (17) to the primary piston (22) and acts to displace the piston (22) forwardly, overcoming the main spring (25) to shut off forward flow when a required volume of fluid is reached. A fuse as claimed in claim 8 or 9 which has a reset mode in which the main spring (25) urges the primary piston (22) leftwardly when fluid pressure across the fuse drops to a pre-set level, and in which the slider (18) is seated in leftward position, and in which a flow path is opened via the sleeve (17) to release fluid as the primary piston moves leftwardly. A fuse as claimed in claim 8, 9 or 10 which has a reverse flow position in which fluid passes reversely via exit slots (24) in the housing (13) into the interior of the sleeve (17), and pressure displaces the sleeve (17) against the regulator spring (19), whereby flow then exits to inside of the housing (13) and out the inlet port (11).

Inventors: GELLERSON WALTER G, GELLERSON, WALTER G.
Applicants: DOWTY DECOTO INC, DOWTY DECOTO INC.
Application year: 1990
Main classification: F16K21
IPC codes: F16K21