Pressure oil supply/discharge circuit and valve device for use in said circuit

Abstract: In a pressure oil supply/discharge passage (3) connected in communication to a hydraulic actuation chamber (2) there are provided a check valve (14) with a forcibly valve opening function and a bypass opening/closing valve (17) in parallel. The opening/closing valve (17) is adapted to be held at a valve opened position (Y) against a residual pressure holding spring (19) under such a condition that a pressure on the check valve inlet (14a) side is normal and to be changed over to a valve closed condition (X) by means of the spring (19) when the pressure has lowered to a predetermined value. The pressure oil supply/discharge passage (3) and a pressure discharge passage (7) are connected in communication to each other through a pressure compensation valve (12). Incidentally, the opening/closing valve (17) is composed of a piston valve member (38) resiliently urged to a bypass valve seat (40) by means of the spring (19).

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pressure oil supply/discharge circuit with a residual pressure holding function and a residual pressure holding valve device for use in the pressure oil supply/discharge circuit, which are adapted to leave a predetermined pressure remaining within a hydraulic actuation chamber even in the case that a breakage of a hydraulic hose and the like cause an oil leak in a pressure oil supply/discharge passage connected to the hydraulic actuation chamber of a hydraulic cylinder. 2. Description of the Prior Art As such a pressure oil supply/discharge circuit with a residual pressure holding function has been conventionally known the one disclosed in JP-B-54 108 156. As shown in a circuit diagram of Fig. 17, this publication discloses a hydraulic cylinder applied to a clamping device. That is, a clamping hydraulic actuation chamber 203 is formed in the one side of a piston 202 of a double-acting type hydraulic cylinder 201, a check valve 205 with a forcibly valve-opening function is disposed in a clamping pressure oil supply/discharge passage 204 connected to the hydraulic actuation chamber 203, and an unclamping pressure oil supply/discharge passage 207 is connected to an unclamping actuation chamber 206 formed in the other side of the piston 202. At the time of clamping, a pressure oil is discharged from the unclamping hydraulic actuation chamber 206 as well as the pressure oil is supplied to the clamping hydraulic actuation chamber 203, so that the hydraulic cylinder 201 is operatively contracted to press and fix a fixed object 210 by means of a clamping member 209. Under this clamped condition, when a pressure on the inlet side of the check valve 205 abnormally lowers due to a breakage of a hydraulic hose and the like, the check valve 205 serves to prevent a counter flow so as to leave a pressure remaining within the clamping hydraulic actuation chamber 203 and thus to prevent a shift and/or a fall of the fixed object 210. Incidentally, a very little leakage of a pressure from the check valve 205 is supplemented by means of an accumulator 211. On one hand, at the time of unclamping, when the pressure oil is supplied from the unclamping pressure oil supply/discharge passage 207 to the unclamping hydraulic actuation chamber 206, the check valve 205 is opened by means of a hydraulic pressure of a pilot oil passage 213, so that a discharge of a pressure oil from the clamping hydraulic actuation chamber 203 is allowed and the hydraulic cylinder 201 is operatively extended. The above-mentioned prior art has such an advantage that the clamping condition can be held by means of a checking function of the check valve 205 even though a pressure oil leakage is caused on the inlet side of the check valve 205, but there is the following problem associated therewith. For example, like in a hydraulic clamping device for a metal mould of an injection moulding machine, when the hydraulic cylinder is subjected to a raised temperature under the clamping condition, a pressure within the clamping hydraulic actuation chamber 203 gradually increases due to a cubical expansion of the pressure oil. Thereby, a clamping force of the hydraulic cylinder 201 excessively increases and resultantly it is apprehended that the fixed object 210 might be damaged. SUMMARY OF THE INVENTION It is an object of the present invention to make leaving a pressure remaining within a hydraulic actuation chamber by means of a check valve compatible with preventing an excessive pressure increase within the hydraulic actuation chamber. (The Circuit of the Invention) For accomplishing the above- mentioned object, for example as shown in Figs. 1 and 2, the pressure oil- supply/discharge circuit is improved as follows. A bypass passage 16 is connected to a pressure oil supply/discharge passage 3 in parallel with a check valve 14. A bypass opening/closing valve 17 is disposed in the bypass passage 16 and adapted to be changed over to a valve closed position X by means of a residual pressure holding spring 19 so as to hold a pressure within a hydraulic actuation chamber 2 within a second pressure range R₂ lower than a first pressure range R₁ under an abnormal pressure condition in which a pressure on the side of the check valve inlet 14 a abnormally lowers in comparison with a pressure on the side of the check valve outlet 14b and to a a valve opened position Y against the spring 19 under a normal pressure condition in which that pressure doesn't lower abnormally. A pressure compensation valve 12 is arranged along the pressure oil supply/discharge passage 3 and a pressure oil discharge passage 7 in parallel with a pressure oil supply/discharge changeover means 4 and is adapted to hold the pressure of the hydraulic actuation chamber 2 within the first pressure range R₁ by discharging only a very slow increased portion of the hydraulic pressure within the hydraulic actuation chamber 2. This first invention functions as follows. Under the normal pressure condition in which a pressure of the pressure port P is within the first pressure range R₁, the bypass opening/closing valve 17 is changed over to the valve opened position Y by that pressure against the spring 19 so that the hydraulic actuation chamber 2 of the hydraulic cylinder 1 is connected in communication to the pressure compensation valve 12 through the bypass opening/closing valve 17. Thereby, though the pressure within the hydraulic actuation chamber 2 increases very slowly due to a cubical expansion of the pressure oil caused by a heat reception of the hydraulic cylinder 1, an increased portion of the hydraulic pressure is released to the pressure oil discharge passage 7 through the pressure compensation valve 12. Resultantly, the pressure of the hydraulic actuation chamber 2 is prevented from excessively increasing. Further, under the normal condition in which the pressure of the pressure port P is within the first range R₁, when a breakage of the hydraulic hose 10 and an oil leakage from the piping are caused, the pressure oil within the hydraulic actuation chamber 2 is discharged from the bypass opening/closing valve 17 at the valve opened position Y to the pressure port P. But, since the bypass opening/ closing valve 17 is changed over rapidly to the valve closed position X by means of the spring 19 at the time of lowering of the pressure on the side of the check valve inlet 14a to the second pressure range R₂, the pressure lowering lower than that range pressure is prevented so as to hold the pressure of the hydraulic actuation chamber 2 within the second pressure range R₂. Accordingly, this first invention provides the following advantages. Though the pressure of the check valve inlet side might have abnormally decreased, it is possible to make a leaving of a pressure remaining within the hydraulic actuation chamber compatible with a prevention of an excessive pressure increase within the hydraulic actuation chamber. Further, since the prevention of the pressure increase within the hydraulic actuation chamber can be attained by making use of the conventional pressure oil supply/discharge circuit, it becomes possible to omit such a piping dedicated to a releasing of the pressure oil so that the construction of the circuit can be made simple. Since at least two kinds of pressure ranges, namely the first pressure range and the second pressure range lower than that first pressure range are provided as the pressure of the hydraulic actuation chamber of the hydraulic cylinder, the following advantages can be provided. That is, in the case that the hydraulic cylinder is applied to a hydraulic clamp for a metal mould of an injection moulding machine and a hydraulic clamp for a metal mould of a press machine, since it is adapted to be changed over to a high-pressure clamping condition after completion of the mould fitting under a low-pressure clamping, the mould fitting work becomes easy. Further, in the case that the hydraulic cylinder is applied to a hydraulic clamp for a work of a cutting machine, since it makes possible to perform a finishing process under a low-pressure clamping condition after completion of a powerful rough cutting process under a high-pressure clamping condition, a machining time can be shortened as well as also a machining accuracy can be improved. (The Valve of the Invention) A residual pressure holding valve device for use in the above-mentioned pressure oil supply/discharge circuit is constructed as follows, for example as shown in Figs. 7 and 8. A pressure port P is connected in communication to a working port A through a check valve seat 28 and a check valve chamber 29 in order within a valve casing 27. A check valve member 30 inserted into the check valve chamber 29 is resiliently urged for valve closing toward the check valve seat 28 by means of a checking spring 31. A forcibly valve-opening means 15 of said check valve 14 is disposed outside the check valve seat 28 and a valve opening member 35 of said forcibly valve-opening means 15 is opposed to the check valve member 30 from the side of the pressure port P. The check valve member 30 is adapted to be brought into contact with the check valve seat 28 for valve closing so as to block a counter flow from the side of the check valve outlet 14b to the side of the check valve inlet 14a under a checking condition in which the forcibly valve-opening means 15 has not been operated, and the check valve member 30 is adapted to be separated from the check valve seat 28 by means of the valve opening member 35 so as to allow the pressure oil to be discharged from the working port A to the pressure port P under a checking cancelled condition in which the forcibly valve-opening means 15 has been operated. A bypass passage 16 is arranged in such a portion as extending from the pressure port P to the working port A, in parallel with the check valve seat 28 and the check valve chamber 29. A bypass opening/closing valve 17 is disposed in the bypass passage 16. The bypass opening/closing valve 17 comprises a piston valve member 38 resiliently urged against a bypass valve seat 40 by means of a residual pressure holding spring 19. The piston valve member 38 is adapted to be separated from the bypass valve seat 40 toward the residual pressure holding spring 19 by means of a pressure within the pressure port P under a normal pressure condition in which the pressure within the pressure port P is kept within a first pressure range R₁ and to be brought into contact with the bypass valve seat 40 for valve closing by means of the residual pressure holding spring 19 under an abnormal pressure condition in which the pressure within the pressure port P abnormally lowers to a second pressure range R₂. When the pressure of the pressure port P lowers from the first pressure range R₁ to the second pressure range R₂, the piston valve member 38 is brought into contact with the bypass valve seat 40 for valve closing by means of a resilient force of the residual pressure holding spring 19. Thereby, the bypass opening/closing valve 17 is changed over to the valve closed position X. Therefore, the bypass opening/closing valve 17 can be simplified in construction by omitting an opening/closing operation device. Accordingly, when the pressure oil supply/discharge circuit with the residual pressure holding function, is put into practice, the residual pressure holding valve device used for that circuit can be manufactured small in construction and inexpensively. BRIEF DESCRIPTION OF THE DRAWINGS The above and other important features of the present invention will be better understood from the following detailed description of a preferred embodiment of the invention, made with reference to the accompanying drawings, in which: Figure 1 through Figure 16 show embodiments of the present invention; Figure 1 through Figure 8 show a first embodiment; Figure 1 is a circuit diagram of a pressure oil supply/discharge circuit; Figure 2 is a view showing a change of a pressure within a hydraulic actuation chamber of a hydraulic cylinder with the lapse of time; Figure 3 is a schematic view of a residual pressure holding valve device; Figure 4 is a circuit diagram of a hydraulic clamping device to which the present invention is applied; Figure 5 is a sectional view taken along the V - V directed line in Figure 4; Figure 6 is a plan view of Figure 5; Figure 7 is an enlarged sectional view taken along the VII - VII directed line in Figure 5 and a cross-sectional view of the residual pressure holding valve device; Figure 8 is a schematic view for operational explanation, Figure 8(a) is a view showing a clamping condition, Figure 8(b) is a view showing a residual pressure holding condition, and Figure 8(c) is a view showing an unclamping condition; Figure 9 shows a first variant of the aforementioned embodiment and is a partial view corresponding to Figure 7; Figure 10 shows a second variant and is a schematic view corresponding to Figure 7; Figure 11 shows a second embodiment and is a view corresponding to Figure 7; Figure 12 shows a third embodiment and is a view corresponding to Figure 7; Figure 13 shows a fourth embodiment and is a partial view corresponding to Figure 1; Figure 14 shows a fifth embodiment and is a partial view corresponding to Figure 1; Figure 15 shows a sixth embodiment and is a partial view corresponding to Figure 4; Figure 16 shows a seventh embodiment and is a partial view corresponding to Figure 4; and Figure 17 shows a conventional embodiment and is a partial view corresponding to Figure 1; DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be explained with reference to the accompanying drawings hereinafter. (First Embodiment) Fig. 1 through Fig. 8 show a first embodiment. Firstly, both a construction and an operation of a pressure oil supply/discharge circuit with a residual pressure holding function will be explained with reference to Fig. 1 and Fig. 2. A circuit diagram of Fig. 1 shows a device for operatively extending and contracting a single-acting type spring-returned hydraulic cylinder 1. A hydraulic actuation chamber 2 of a hydraulic cylinder 1 is adapted to be selectively connected to a hydraulic pressure source 6 at a starting end portion of a pressure oil supply passage 5 and to an oil tank 8 at an ending end portion of a pressure oil discharge passage 7 through a pressure oil supply/discharge passage 3 and a pressure oil supply/discharge changeover means 4. The pressure oil supply/discharge changeover means 4 is composed of one changeover valve and adapted to be changed over to a supply position M and to a discharge position N. A residual pressure holding valve device 11 is disposed between the hydraulic actuation chamber 2 and a hydraulic hose 10 of the pressure oil supply/discharge passage 3. A pressure compensation valve 12 is arranged along the pressure oil supply/discharge passage 3 and the pressure oil discharge passage 7 in parallel with the pressure oil supply/discharge changeover means 4. The residual pressure holding valve device 11 is provided with a check valve 14 with a forcibly valve-opening function, a forcibly valve-opening means 15 of the fluid-pressure operating type, a bypass passage 16 connected in parallel with the check valve 14 and a bypass opening/ closing valve 17 disposed in the bypass passage 16. The bypass opening/closing valve 17 is adapted to be changed over to a valve closed position X by means of a residual pressure holding spring 19 under such a condition that a pressure is not acting on the side of the check valve inlet 14a and to a valve opened position Y by means of a pressure on the side of the check valve inlet 14a against the residual pressure holding spring 19. A flow resistance application means 21 composed of a throttling passage is disposed in a valve passage 17a of the bypass opening/closing valve 17. The pressure compensation valve 12 comprises a throttling valve 23 and a relief valve 24 connected in series to each other. The operation of the aforementioned pressure oil supply/discharge circuit will be explained with reference to Fig. 1 and Fig. 2. At the time of extending operation of the hydraulic cylinder 1, the changeover means 4 is changed over to the supply position M as well as the forcibly valve-opening means 15 is changed over to a fluid discharge position. Thereupon, a pressure oil of the hydraulic pressure source 6 flows into the hydraulic actuation chamber 2 through the pressure port P, the check valve inlet 14a, its outlet 14b and a working port A of the valve device 11 so as to operatively extend the hydraulic cylinder 1. The pressure of the hydraulic actuation chamber 2 increases gradually as the extension resistance increases, and when it has reached the pressure (herein, 250 Kgf/cm²) of the first pressure range R₁ of substantially the same pressure as that of the hydraulic pressure source 6, the extension of the hydraulic cylinder 1 is completed (time t₁). In the midway course of increasing of the pressure on the side of the check valve inlet 14a, the bypass opening/closing valve 17 is changed over to the valve opened position Y so that the hydraulic actuation chamber 2 is connected in communication to the pressure compensation valve 12 through the bypass opening/closing valve 17. Under the extension completed condition, when the hydraulic cylinder 1 receives a heat from outside, the pressure of the hydraulic actuation chamber 2 starts to increase very slowly due to a cubical expansion of the pressure oil (time t₂). When the pressure has increased to a set pressure (herein, around 255 ∼ 270 Kgf/cm²) of the relief valve 24 (time t₃),the pressure compensation valve 12 serves to discharge only a very slow increased portion of the hydraulic pressure from the pressure oil discharge passage 7 to the oil tank 8. Thereby, the pressure of the hydraulic actuation chamber 2 is held within the first pressure range R₁. Under the extended condition of the hydraulic cylinder 1, when the pressure of the pressure port P starts to rapidly abnormally lower due to a breakage of the hydraulic hose 10 and the like (time t₄), the pressure of the hydraulic actuation chamber 2 lowers (refer to the figure indicated by the alternate long and short dash - line) because the check valve 14 serves to block a counter flow from the side of the check valve outlet 14b to the side of the check valve inlet 14a and on the other hand, the bypass opening/closing valve 17 at the valve opened position Y serves to allow the pressure oil to discharge from the working port A to the pressure port P. When the pressure of the pressure port P lowers to the pressure (herein, 140 Kgf/cm²) within the second pressure range R₂ (time t₅), the bypass opening/closing valve 17 is changed over to the valve closed position X by means of the residual pressure holding spring 19. Thereby, the pressure of the hydraulic actuation chamber 2 is held within the second pressure range R₂. Further, in the case that the pressure of the pressure port P starts to abnormally lower very slowly due to a little leak from the piping and the like at the time of t₄, also the pressure of the hydraulic actuation chamber 2 lowers very slowly (refer to the figure indicated by the alternate long and two short dashes line). Thereupon, similarly to the aforementioned one, when the pressure of the pressure port P lowers to the pressure within the second pressure range R₂ (time t₆), the bypass opening/ closing valve 17 is changed over to the valve closed position X so that the pressure of the hydraulic actuation chamber 2 can be held within the second pressure range R₂. On one hand, under such a condition that the pressure of the hydraulic actuation chamber 2 is held within the first pressure range R₁, when the hydraulic cylinder 1 is operatively contracted, the pressure oil supply/discharge changeover means 4 is changed over to the discharge position N as well as the forcibly valve opening means 15 of the fluid pressure type is changed over to the supply position ( time t₇). Thereupon, the checking condition of the check valve 14 is cancelled so that the pressure oil within the hydraulic actuation chamber 2 is discharged to the oil tank 8 through the working port A, the check valve outlet 14b, the check valve inlet 14a, the pressure port P and the changeover means 4 at the discharge position N in order. Accompanying therewith, the pressure of the hydraulic actuation chamber 2 lowers rapidly, the contraction of the hydraulic cylinder 1 is completed (time t₉). Incidentally, the contracting operation of the hydraulic cylinder 1 may be performed according to the following procedure. Under such a condition that the pressure of the hydraulic actuation chamber 2 is held within the first pressure range R₁, firstly only the changeover means 4 is changed over to the discharge position N at the time of t₄. Thereupon, the pressure oil within the hydraulic actuation chamber 2 is discharged from the bypass opening/closing valve 17 at the valve opened position Y so that the pressure of the hydraulic actuation chamber 2 lowers to the second pressure range R₂ (time t₅). Under this condition, the check valve 14 is opened (time t₈) by operating the forcibly valve opening means 15 to the supply position. Thereby, the pressure of the hydraulic actuation chamber 2 lowers, so that the contraction of the hydraulic cylinder 1 is completed (time t₉). Next, the construction of the aforementioned residual pressure holding valve device 11 will be schematically explained. As shown in Fig. 3, the pressure port P is connected in communication to the working port A through the check valve seat 28 and the check valve chamber 29 in order within the valve casing 27. The check valve member 30 inserted into the check valve chamber 29 is resiliently urged for valve closing toward the check value seat 28 by means of the checking spring 31. The forcibly valve-opening means 15 is disposed outside (above, in Figure 3) both the pressure port P and the check valve seat 28 and provided with a fluid pressure piston 33 inserted into the valve casing 27. Above the fluid pressure piston 33 there are provided a fluid pressure actuation chamber 34 and a pilot port F. A valve opening member 35 disposed below the piston 33 is opposed to a check valve member 30 from the side of the pressure port P. Further, a bypass passage 16 is arranged along a portion from the pressure port P to the working port A in parallel with the check valve seat 28 and the check valve chamber 29. Incidentally, the bypass passage 16 may be formed in a wall of the valve casing 27 or outside the valve casing 27 instead of within the check valve member 30 in this embodiment. The bypass opening/closing valve 17 disposed in a midway portion of the bypass passage 16 is provided with a piston valve member 38 and a valve seat tube 39 having a bypass valve seat 40. These piston valve member 38 and valve seat tube 39 are inserted into the check valve member 30 so as to be oil-tightly movable within a certain extent and are resiliently urged for valve closing by means of the residual pressure holding spring 19 and a return spring 41. A flow resistance application means 21 arranged in the bypass passage 16 is constructed by an annular fitting gap formed between a tube port 39a of the valve seat tube 39 and a throttling valve member 44 inserted into the tube port 39a. Under the normal pressure condition in which the pressure of the pressure port P is within the first pressure range R₁, the aforementioned piston valve member 38 is separated from the bypass valve seat 40 by means of that range pressure against the residual pressure holding spring 19. Thereby the working port A is connected in communication to the pressure port P so that a very slow increased portion of the hydraulic pressure of the working port A is released to the pressure port P. To the contrary, under the abnormal pressure condition in which the pressure of the pressure port P has lowered abnormally the the second pressure range R₂, the piston valve member 38 is brought into contact with the bypass valve seat 40 for valve closing by means of the residual pressure holding spring 19. Thereby, the pressure of the working port A can be held within the second pressure range R₂. When a pressure fluid is supplied from the pilot port F to the fluid pressure actuation chamber 34, the fluid pressure piston 33 serves to separate the check valve member 30 from the check valve seat 28 through the valve opening member 35 so that the pressure oil of the working port A is discharged to the pressure port A through a peripheral groove 30a of the check valve member 30. The concrete constructions of the aforementioned pressure oil supply/discharge circuit and the residual pressure holding valve device 11 will be explained with reference to Fig. 4 through Fig. 8 hereinafter. Fig. 4 shows a hydraulic clamping device 50 for fixing a metal mould to an injection moulding machine of the rotary table type. A first metal mould 52 and a second metal mould 53 are fixedly secured to a circular rotary table 51 of an injection moulding machine by means of two hydraulic clamps 54, 54 respectively. Each hydraulic clamp 54 is fixedly secured at opposite side walls of its housing 55 to a rotary table frame 51 by means of bolts 57, 57. Respective clamping members 62 extended from the housings 55 are adapted to press upper and lower fixed portions 52a, 53a of the respective metal moulds 52, 53. These hydraulic clamps 54 are adapted to actuate the clamping members 62 forward and backward in the inclined direction with respect to the metal moulds 52, 53 in order to enable to be mounted within an outer peripheral surface 51a of the rotary table frame 51. That is, as shown in a vertical sectional view of Fig. 5 and in a plan view of Fig. 6, a cylinder bore 58 of a hydraulic cylinder 1 is formed within the housing 55 of the hydraulic clamp 54 in the forwardly downwardly inclined manner. An inclination angle ϑ of the cylinder bore 58 is preferably defined at ab. 35 degree for providing a compact construction of the housing 55. A hydraulic piston 59 is inserted into the cylinder bore 58 through a packing 60 so as to be oil-tightly movable forwardly and backwardly. The hydraulic actuation chamber 2 is formed within the cylinder bore 58 so as to face the back surface of the piston 59. The clamping member 62 is protruded directly from the upper portion of the piston 59 to the advancing side thereof. A spring accommodation bore 66 is formed in the piston 59 so as to extend backwardly from its front surface. An axis K of the spring accommodation bore 66 is offset to the lower side relative to an axis J of the piston 59. An unclamping spring 67 composed of a compression spring is accommodated within the spring accommodation bore 66. This unclamping spring 67 is mounted between the piston 59 and a spring retaining pin 69 inserted into a pin insertion hole 68 of the housing 55. A pair of left and right free travel grooves 71, 71 are formed in the opposite lateral side portions of the clamping member 62 in such a manner as to open their front surfaces in order to avoid an interference with the spring retaining pin 69. When the hydraulic clamp 54 is changed over to the illustrated clamping condition, the pressure oil is supplied to the hydraulic actuation chamber 2. Thereupon, the piston 59 is forwardly actuated by means of the hydraulic pressure, so that the clamping member 62 is advanced to the clamping position outside the front surface 55a of the housing 55. Thereby, the clamping member 62 serves to press and fix the fixed portion 52a of the metal mould 52 onto the rotary table frame 51. In the housing 55 of the aforementioned hydraulic clamp 54 there is provided the residual pressure holding valve device 11. As shown in Fig. 7, the casing 27 of the valve device 11 comprises a wall portion 73 and a cover bolt 74 of the housing 55. The pressure port P of the valve device 11 is formed in the housing wall portion 73, the working port A is connected in communication to the hydraulic actuation chamber 2, and the pilot port F is formed in the cover bolt 74. The check valve seat 28 of the check valve 14 is formed in the leading end portion (in the lower end portion in Figure) of the cover bolt 74. The check valve chamber 29 is formed in the space below the cover bolt 74. The check valve member 30 is guided within the leading end portion of the cover bolt 74. The valve surface of the check valve member 30 is made of a resilient material such as fluororesin and the like. The valve seat tube 39 of the bypass opening/closing valve 17 is inserted oil-tightly and movably into the check valve member 30. A bypass valve seat 40 is formed in the upper portion of the valve seat tube 39. Also the bypass valve seat 40 is made of a resilient material such as fluororesin and the like. The fluid pressure piston 33 of the forcibly valve-opening means 15 is inserted into the midway portion of the cover bolt 74 coaxially with the check valve member 30. The fluid pressure piston 33 has a piston pressure receiving sectional area defined at a smaller value than a pressure non-receiving sectional area within the check valve seat 28 by defining its external dimension D smaller than a cut-off diameter dimension E of the check valve seat 28. A piston valve member accommodation bore 75, a spring chamber 76 and communication ports 77 are formed in order within the fluid pressure piston 33. The piston valve member 38 oil-tightly and movably inserted into the accommodation bore 75 is resiliently urged for valve closing toward the bypass valve seat 40 by means of the residual pressure holding spring 19 mounted within the spring chamber 76. Its valve closing movement further than a predetermined distance is blocked by the contact between a shoulder portion 38a of the piston valve member 38 and a reduced diameter stopper portion 33b of the fluid pressure piston 33. An annular filter chamber 78 is formed between the pressure port P and the bypass opening/closing valve 17 as well as the check valve 14. An annular primary filter 79 is mounted within the filter chamber 78. The operation of the aforementioned valve device 11 will be explained with reference to Fig. 8. Fig. 8(a) shows the clamping condition. At the time of clamping operation, the pressure oil supplied from the pressure port P serves to push and open the check valve member 30 and flows into the hydraulic actuation chamber 2 through the working port A. After the pressure within the hydraulic actuation chamber 2 has increased, the check valve member 30 is brought into contact with the check valve seat 28 for valve closing by means of the checking spring 31. The valve seat tube 39 urged by means of the return spring 41 is received by the fluid pressure piston 33. The piston valve member 38 is kept separated from the bypass valve seat 40 against the residual pressure holding spring 19 by means of such a pressure as acting in the bypass passage 16. Thereby, the working port A is connected in communication to the pressure port P through the flow resistance application means 21 composed of the fitting gap, the valve passage 17a and the communication groove 33a of the fluid pressure piston 33 in order. Fig. 8(b) shows the residual pressure holding condition. In case that the pressure within the pressure port P abnormally lowers, the check valve member 30 is held in such a condition as being kept in contact with the check valve seat 28 for valve closing as well as the residual pressure holding spring 19 brings the piston valve member 38 into contact with the bypass valve seat 40 so that the pressure within the hydraulic actuation chamber 2 can be prevented from further lowering. Fig. 8(c) shows the unclamping condition. By supplying the pressure fluid to the pilot port F, the fluid pressure piston 33 serves to separate the check valve member 30 from the check valve seat 28 through the valve opening member 35. Thereby, the pressure oil within the hydraulic actuation chamber 2 is discharged from the pressure port P. In this case, a resultant force composed of the resilient force of the residual pressure holding spring 19 and the received pressure from the pilot port F acts on the piston valve member 38 while the piston valve member 38 is received by the check valve member 30 through the stopper portion 33b of the fluid pressure piston 33. Thereby, a valve-closing contact force for the piston valve member 38 and the valve seat tube 39 is sufficiently provided by only a resilient force of the return spring 41. As a result, the bypass valve seat 40 made of a resilient material becomes hardly damaged and can have a long service life. Further, since the valve surface of the check valve member 30 and the bypass valve seat 40 are made of a resilient material, an oil leakage can be prevented more surely. As a result, the accumulator 211 employed in the conventional embodiment (refer to Fig. 17) can be omitted, so that the whole of the valve device 11 can be made small. Incidentally, the location where a sealing resilient member is arranged may be the check valve seat 28 and the valve surface of the piston valve member 38. As shown in Fig. 4, the pressure port P of each aforementioned valve devices 11 is selectively connected to the booster pump (the hydraulic pressure source) 6 at the starting end portion of the pressure oil supply passage 5 and to the oil tank 8 at the ending end portion of the pressure oil discharge passage 7 through the pressure oil supply/discharge passage 3 and the pressure oil supply/discharge changeover means 4. The booster pump 6 is adapted to operatively deliver an oil from the oil tank 8 when a compressed air is supplied from a pneumatic source 80 thereto through a pressure reduction valve 81. In the midway portion of the pressure oil supply/discharge passage 3 there are provided two flexible hydraulic hoses 10, 10, and the pressure compensation valve 12 is disposed along the pressure oil supply/discharge passage 3 and the pressure oil discharge passage 7 in parallel with the pressure oil supply/discharge changeover means 4. The pilot port F of each valve device 11 is selectively connected to a pressure fluid supply passage 84 and to a pressure fluid discharge passage 85 through a pressure fluid supply/discharge passage 82 and a pressure fluid supply/discharge changeover means 83. The pressure fluid supply/discharge changeover means 83 employs a hydraulic changeover valve having the same construction as that of the pressure oil supply/discharge changeover means 4. The pressure fluid supply passage 84 is connected to the pressure oil supply passage 5, and the pressure fluid discharge passage 85 is connected to the pressure oil discharge passage 7. Also in the midway portion of the pressure fluid supply/discharge passage 82 there are provided two flexible hoses 87, 87. The aforementioned two changeover means 4, 83 are changed over to the supply position M and to the discharge position N by means of an electromagnetic pneumatic changeover valve 89. When the pneumatic changeover valve 89 is changed over to the clamping position C, the pressure oil supply/discharge changeover means 4 is changed over to the supply position M as well as the pressure fluid supply/discharge changeover means 83 is changed over to the discharge position N. Thereby, the pressure oil of the booster pump 6 is supplied to the pressure port P of the valve device 11 so that four hydraulic clamps 54 are actuated for clamping. This clamping operational condition is detected by means of a pressure switch 91. To the contrary, when the pneumatic changeover valve 89 is changed over to the unclamping position U, the pressure oil supply/discharge changeover means 4 is changed over to the discharge position N as well as the pressure fluid supply/discharge changeover means 83 is changed over to the supply position M. Thereby, the pressure oil of the booster pump 6 is supplied to the pilot port F of the valve device 11. As a result, the pressure oil within the hydraulic actuation chamber 2 is discharged from the pressure port P to the oil tank 8 through the changeover means 4 so that the respective hydraulic clamps 54 are actuated for unclamping. This unclamping operational condition is detected by means of a pressure switch 92. As described above, since the forcibly valve-opening means 15 of the check valve 14 is constructed as the fluid pressure actuating type, the automation of the changeover of the pressure oil supply/discharge circuit 3 becomes easy. By constructing the forcibly valve-opening means 15 as the hydraulic actuating type one, the fluid pressure piston 33 for valve opening operation can be made small in dimension and the whole of the device can be made small. Further, since the flow resistance application means 21 is arranged in series with respect to the valve passage 17a of the bypass opening/closing valve 17, though the lowering speed of the pressure on the side of check valve inlet 14a is abrupt, the lowering speed of the pressure of the hydraulic actuation chamber 2 can be made slow by means of the flow resistance application means 21 so that the residual pressure of the hydraulic actuation chamber 2 can be made at a high level. Fig. 9 through Fig. 16 show variants and other embodiments respectively. Incidentally, in the respective variants and embodiments, component parts having the same constructions as those of the first embodiment are designated by the same symbols in principle. (First Variant) Fig. 9 shows a first variant of the above-mentioned first embodiment. Onto a portion facing the working port A within the housing 55, a second filter 97 is pressed and fixed oil-tightly by means of the resilient forces of the checking spring 31 and the return spring 41. (Second Variant) Fig. 10 shows a second variant of the first embodiment. A flow resistance application means 101 is composed of an annular fitting gap formed between the check valve member 30 and the fluid pressure piston 33. A secondary filter 102 is fixedly secured to the lower portion of a cylindrical port of the valve seat tube 39. (Second Embodiment) Fig. 11 show a second embodiment. A hydraulic piston 105 and a valve seat tube 106 are integrally formed, and a bypass valve seat 107 is disposed in the midway portion of the cylindrical port of this integrated tube. The working port A is adapted to be connected in communication to the pressure port P through the flow resistance application means 21 and a communication port 108 above the bypass valve seat 107 in order. (Third Embodiment) Fig. 12 show a third embodiment. A fluid pressure piston 111 inserted into a cover bolt 110 has its external dimension D defined at a larger value than a cut-off diameter E of a check valve seat 112. The fluid pressure piston 111 is adapted to be received by means of a press bolt 113 within the cover bolt 110. According to this construction, since a pressure received by the fluid pressure piston 111 can be made large at the time of unclamping operation, the check valve member 30 can be opened powerfully. (Fourth Embodiment) Fig. 13 shows a fourth embodiment. A flow resistance application means 117 of a residual pressure holding valve device 116 is disposed in a bypass passage 119 outside a bypass opening/closing valve 118. (Fifth Embodiment) Fig. 14 shows a fifth embodiment. A pressure oil supply/discharge changeover means 121 comprises two valves, namely a supply opening/closing valve 122 and a discharge opening/closing valve 123. When a pressure oil is supplied to the pressure oil supply/discharge passage 3, the supply opening/closing valve 122 is opened as well as the discharge opening/closing valve 123 is closed. When the pressure oil is discharged from the pressure oil supply/discharge passage 3, the supply opening/closing valve 122 is closed as well as the discharge opening/closing valve 123 is opened. (Sixth Embodiment) Fig. 15 shows a sixth embodiment. Residual pressure holding valve devices 130 are fixedly secured to respective hydraulic actuation chambers 128 of hydraulic clamps 126, 126 on one side of two pairs of hydraulic clamps, and a pressure oil supply/discharge passage 132 and a pressure fluid supply/discharge passage 133 are connected to each valve device 130. Respective hydraulic actuation chambers 129 of hydraulic clamps 127, 127 on the other side are connected in communication to the respective hydraulic actuation chambers 128 on one side through communication pipes 134 respectively. (Seventh Embodiment) Fig. 16 shows a seventh embodiment. Respective hydraulic actuation chambers 139 of four hydraulic clamps 138 are connected to one residual pressure holding valve device 140. This valve device 140 is provided with one pressure port P, one pilot port F and two working ports A. Incidentally, besides the above-mentioned variants and embodiments, the present invention may be modified as follows. (a) The hydraulic clamp is not limited to such a type that the clamping member is actuated in the inclined direction, but also may be employed in other kinds of devices such as a press machine and the like. (b) The forcibly valve- opening means 15 of the check valve 14 may be of the pneumatically or manually operated type instead of the hydraulically operated type. (c) The hydraulic cylinder may be of the double-acting type instead of the single acting type. (d) The flow resistance application means 21 interposed in the bypass passage 16 may be composed of a port having a small diameter instead of the annular fitting gap. Further, the flow resistance application means 21 may be omitted by increasing a speed of a valve closing operation of the bypass opening/closing valve 17. (e) The pressure compensation valve may be such a one as to release a very slowly increasing portion of a pressure which might be caused by a cubical expansion of the pressure oil and may be of the another type having such function instead of the combination of the throttle valve and the relief valve. As many different embodiments of the invention will be obvious to those skilled in the art, some of which have been disclosed or referred to herein, it is to be understood that the specific embodiments of the present invention as presented herein are intended to be by way of illustration only and are not limiting on the invention, and it is to be understood that such embodiments, changes, or modifications may be made without departing from the scope of the claims appended hereto.

Claims: A pressure oil supply/discharge circuit including: a hydraulic actuation chamber (2) of a hydraulic cylinder (1), said hydraulic actuation chamber (2) being adapted to be selectively connected to a pressure oil supply passage (3) and to a pressure oil discharge passage (7) through a pressure oil supply/discharge passage (3) and a pressure oil supply/discharge changeover means (4); and a check valve (14) with a forcibly valve-opening function disposed in said pressure oil supply/discharge passage (3); said check valve (14) being adapted to block a counter flow from a check valve outlet (14b) side to a check valve inlet (14a) side under a checking condition in which a forcibly valve- opening means (15) is not operated and to allow the pressure oil to be discharged from the hydraulic actuation chamber (2) under a checking cancelled condition in which the forcibly valve-opening means (15) has been operated, characterized in that: a bypass passage (16) is connected to said pressure oil supply/discharge passage (3) in parallel with said check valve (14); a bypass opening/closing valve (17) is disposed in said bypass passage (16) and adapted to be changed over to a valve closed position (X) by means of a residual pressure holding spring (19) so as to hold a pressure of said hydraulic actuation chamber (2) within a second pressure range (R₂) lower than a first pressure range (R₁) under an abnormal pressure condition in which a pressure on the side of the check valve inlet (14a) abnormally lowers in comparison with a pressure on the side of the check valve outlet (14b) and to a valve opened position (Y) against said spring (19) under a normal pressure condition in which said pressure doesn't lower abnormally; a pressure compensation valve (12) is arranged along said pressure oil supply/discharge passage (3) and said pressure oil discharge passage (7) in parallel with said pressure oil supply/discharge changeover means (4); and said pressure compensation valve (12) is adapted to hold the pressure within the hydraulic actuation chamber (2) within the first pressure range (R₁) by discharging only a very slow increased portion of the hydraulic pressure within the hydraulic actuation chamber (2). A pressure oil supply/discharge circuit as set forth in claim 1, wherein said forcibly valve-opening means (15) is constructed as a fluid pressure actuation type one, and a pilot port (F) of the forcibly valve-opening means (15) is selectively connected to a pressure fluid supply passage (84) and to a pressure fluid discharge passage (85) through a pressure fluid supply/discharge passage (82) and a pressure fluid supply/discharge changeover means (83). A pressure oil supply/discharge circuit as set forth in claim 2, wherein said forcibly valve-opening means (15) is constructed as a hydraulic actuation type one, and said pressure fluid supply passage (84) is connected to the pressure oil supply passage (5) as well as said pressure fluid discharge passage (85) is connected to the pressure oil discharge passage (7). A pressure oil supply/discharge circuit as set forth in any one of claims 1 through 3, wherein a flow resistance application means (21) is disposed in said bypass passage (16) of the pressure oil supply/discharge passage (3) in series with respect to a valve passage (17a) of said bypass opening/closing valve (17). A residual pressure holding valve device including: a pressure port (P) connected to a working port (A) through a check valve seat (28) and a check valve chamber (29) in order within a valve casing (27); a check valve member (30) inserted into the check valve chamber (29) and resiliently urged for valve closing toward the check valve seat (28) by means of a checking spring (31); a forcibly valve-opening means (15) of said check valve (14) disposed outside the check valve seat (28), and a valve opening member (35) of said forcibly valve-opening means (15) being opposed to said check valve member (30) from the side of said pressure port (P); said check valve member (30) being adapted to be brought into contact with the check valve seat (28) for valve closing so as to block a counter flow from the side of the check valve outlet (14b) to the side of the check valve inlet (14a) under a checking condition in which the forcibly valve-opening means (15) is not operated; and said check valve member (30) being adapted to be separated from the check valve seat (28) by means of the valve opening member (35) so as to allow the pressure oil to be discharged from the working port (A) to the pressure port (P) under a checking cancelled condition in which the forcibly valve-opening means (15) has been operated, characterized in that: a bypass passage (16) is arranged in a portion from said pressure port (P) to said working port (A), in parallel with said check valve seat (28) and said check valve chamber (29); a bypass opening/closing valve (17) is disposed in said bypass passage (16); said bypass opening/closing valve (17) comprises a piston valve member (38) resiliently urged toward a bypass valve seat (40) by means of a residual pressure holding spring (19); and said piston valve member (38) is adapted to be separated from the bypass valve seat (40) against the residual pressure holding spring (19) by means of a pressure within the pressure port (P) under a normal pressure condition in which the pressure within the pressure port (P) is kept within a first pressure range (R₁) and to be brought into contact with the bypass valve seat (40) for valve closing by means of the residual pressure holding spring (19) under an abnormal pressure condition in which the pressure within the pressure port (P) has abnormally lowered to a second pressure range (R₂). A valve device as set forth in claim 5, wherein at least a portion of said bypass passage (16) is disposed within said check valve member (30) as well as said bypass valve seat (40) is disposed within the check valve member (30). A valve device as set forth in claim 6, wherein said forcibly valve-opening means (15) of the check valve (14) has a fluid pressure piston (33) so disposed as to face the check valve member (30) from the side of the pressure port (P); a fluid pressure actuation chamber (34) is formed in one side of said fluid pressure piston (33), and the pressure port (P) is connected in communication to the other side of the fluid pressure piston (33) as well as a valve opening member (35) is disposed in said other side; and within said fluid pressure piston (33) there are installed said piston valve member (38) of the bypass opening/closing valve (17) and the residual pressure holding spring (19). A valve device as set forth in claims 6 or 7, wherein a valve seat tube (39) is so inserted into said check valve member (30) as to be oil-tightly movable therein, and the bypass valve seat (40) formed in said valve seat tube (39) is resiliently urged to the valve surface of the piston valve member (38) by means of a return spring (41). A valve device as set forth in any one of claims 5 through 8, wherein a flow resistance application means (21) is arranged in said bypass passage (16) in series with respect to a valve passage (17a) of said bypass opening/closing valve (17). A valve device as set forth in claim 8, wherein a throttling valve member (44) is inserted into a tube port (39a) of said valve seat tube (39), so that said flow resistance application means (21) is constructed by an annular gap formed between said tube port (39a) and said throttling valve member (44). A valve device as set forth in any one of claims 5 through 10, wherein the valve casing (27) is fixedly secured to a cylinder body (1a) of a hydraulic cylinder (1).

Inventors: YONEZAWA KEITARO C O KABUSHIKI, YONEZAWA, KEITARO, C/O KABUSHIKI KAISHA KOSMEK
Applicants: KOSMEK KK, KABUSHIKI KAISHA KOSMEK
Application year: 1991
Main classification: F15B13
IPC codes: F15B11, B23Q3, F15B13, B25B5