• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    In the shutoff valve according to the invention, the stop noise that occurs when a piston of an air cylinder strikes in the stroke end position is reduced by utilizing the mode of action of an air cushion. An air cylinder pair (7A, 7B) consisting of air cylinder (7A) and air cylinder (7B), which cause a valve plate (3) to make an opening / closing movement and each of which is equipped with a head-side air damping mechanism and a rod-side air damping mechanism. Each head-side air damper mechanism includes a head-side communication path and a head-side throttling flow path (68) that connect a head-side pressure chamber (61) and a head-side main flow path (24) in parallel, as well as a locking mechanism that blocks the head-side communication path (67) when a piston locks (23) approaches the end position of a reverse stroke, and each rod-side air damping mechanism comprises a rod-side connecting path (78) and a rod-side throttling flow path (80) which connect a rod-side pressure chamber (62) and a rod-side main flow path (25) in parallel, as well as a locking mechanism, which blocks the rod-side connection path (78) when the piston (23) approaches the end position of a forward stroke.
    公开号:CH715704A2
    申请号:CH01577/19
    申请日:2019-12-09
    公开日:2020-06-30
    发明作者:Shimoda Hiromi；Ogawa Hiroshi；Udagawa Hiroshi；Nagao Takashi
    申请人:Smc Corp；
    IPC主号:
    专利说明:

    The present invention relates to a check valve which is attached to a vacuum chamber in a semiconductor manufacturing device and which serves to open and close a lock opening that communicates with the vacuum chamber, in particular a low-noise check valve that when opening and Closing the lock opening causes little noise.
    In a semiconductor manufacturing device, a check valve, such as the check valve disclosed in Patent Literature 1, is used when opening and closing a check opening that communicates with a vacuum chamber. The check valve includes a valve disk that opens and closes the shutoff opening, a valve stem that is connected to the valve disk, and a pair of air cylinders that cause the valve disk to perform opening / closing movements over the valve stem. The check valve opens and closes the opening with the valve plate by moving the valve plate up and down over the valve stem from the pair of air cylinders.
    More specifically, by moving the pistons of the air cylinder pair back and forth, the valve plate is moved over the valve stem to a fully open position, an intermediate position and an absolutely tight position. The fully open position is given when the valve plate has moved downwards and the locking opening is fully open. The intermediate position is given when the valve plate has moved upwards and the blocking opening is not closed, although the valve plate faces the blocking opening. The absolutely tight position is given when the valve plate has moved to the side of a blocking opening and the blocking opening is closed.
    In the generally known shut-off valve, it is the case that when the valve plate is in the fully open position, each piston has reached the end position of the forward stroke and touches one of the end faces of a cylinder housing, and when the valve plate is in the absolute position tight position, each piston has reached the end position of the reverse stroke and touches the other end of the cylinder housing. As a result, each time the valve disk repeats the opening / closing movements, the pistons collide with one end face when the forward stroke end position is reached and with one end face when the reverse stroke end position is reached, which has the problem of causing an impact noise is produced.
    Thus, in order to be able to create an operating environment that produces little noise as a result of reducing the impact noise generated by each piston, there is a desire for a novel check valve that is designed to be unlikely to produce this impact noise becomes.
    [Patent Literature 1] Unexamined Japanese Patent Application Publication No. 2015-215009.
    A purpose of the present invention is to offer a check valve with an appropriately designed structure in which when opening and closing a check opening through a valve plate, an impact noise generated by the impact of the pistons of the air cylinders at the stroke ends by utilizing the effect of air damping can be effectively reduced.
    To this end, a low-noise shut-off valve according to this invention comprises a valve plate that opens and closes a shut-off opening, a valve stem whose distal end is connected to the valve plate, and an actuating mechanism that causes the valve plate via the valve stem, an opening valve. / Execute closing movement.
    The actuating mechanism comprises a cover through which the valve stem slidably extends, a pair of air cylinders consisting of a left and a right air cylinder, which are attached to the cover in parallel with each other with an intermediate valve stem, and a head-side opening and a rod-side opening, through the air can be supplied to the pair of air cylinders and air can be removed from the pair of air cylinders; and each air cylinder includes a cylinder housing attached to the cover, a piston housed in the cylinder housing so that it can freely advance and retract, a drive rod having its proximal end connected to the piston and its distal end out emerges from the cylinder housing, and a head-side pressure chamber and a rod-side pressure chamber, which are formed on one end face and the other end face of the piston.
    The head-side pressure chambers are connected to the head-side opening via head-side main flow paths which are formed on the cylinder housings and the cover, and the rod-side pressure chambers are connected to the rod-side opening via rod-side main flow paths which are formed on the cylinder housings and the cover; and a proximal end portion of the valve stem is supported by the actuator rods of the air cylinder pair via a stem support, the valve plate moves to a position in which the locking opening is opened due to a forward stroke of the pistons and the drive rods, and the valve plate moves to a position, in which closes the blocking opening due to a reverse stroke of the pistons and the drive rods.
    Each air cylinder comprises a head-side air damping mechanism and a rod-side air damping mechanism, both of which have a shock-absorbing effect when the blocking opening is opened and closed by the valve plate; each head-side air damper mechanism includes a head-side communication path and a head-side throttling flow path that connect the head-side pressure chamber and the head-side main flow path in parallel, and a locking mechanism that blocks the head-side communication path when the retracting piston approaches the reverse stroke end position; and each rod side air damper mechanism includes a rod side communication path and a rod side throttling flow path that connect the rod side pressure chamber and the rod side main flow path in parallel, and a lock mechanism that blocks the rod side communication path when the extending piston approaches the forward stroke end position.
    In the present invention, the locking mechanism of each head-side air damper mechanism may have a head-side damper shaft which protrudes into the head-side pressure chamber from an end face of the head-side pressure chamber, a concave-shaped head-side damper hole which is machined in the piston such that the head-side damper shaft inserted therein when the piston reaches the end position on the backward stroke and a head-side damper packing that seals a portion between an inner boundary surface of the head-side damper hole and an outer boundary surface of the head-side damper shaft, and the head-side connecting path is formed in the head-side damper shaft; and the locking mechanism of each rod-side air damping mechanism can have a concave-shaped rod-side damper hole which is machined in an end face of the rod-side pressure chamber, a rod-side damper shaft which fits into the rod-side damper hole when the piston approaches the end position during the forward stroke, and a rod-side damper pack, which seals a portion between an inner boundary surface of the rod-side damper hole and an outer boundary surface of the rod-side damper shaft; and the rod side connection path may be formed from the rod side damper hole.
    In this case, it is desirable that each head-side damper pack is designed such that an air flow flowing from the head-side pressure chamber to the head-side damper hole is blocked and an air flow flowing from the head-side damper hole to the head-side pressure chamber is let through, and that each rod-side damper pack is designed in this way is that an air flow flowing from the rod-side pressure chamber to the rod-side damper hole is blocked and an air flow flowing from the rod-side damper hole to the rod-side pressure chamber is let through.
    In the present invention, all of the head-side communication paths and all of the head-side throttling flow paths of the head-side air damping mechanisms of the air cylinder pair are connected to the head-side main flow paths, and all of the rod-side connecting paths and all of the rod-side throttling flow paths of the rod-side air damping mechanisms of the air cylinder pair are connected to the head-side main flow so that the head paths Air damping mechanisms and the rod-side air damping mechanisms of the pair of air cylinders work synchronously with one another.
    Furthermore, in this invention, it is desirable that each piston and the valve plate have a fully open position in which the valve plate opens the blocking opening completely, an intermediate position in which the valve plate does not close the blocking opening although it faces the blocking opening, and can assume an absolutely tight position in which the valve disk hermetically seals the blocking opening; during the reverse stroke, in which each piston moves from the fully open position to the absolutely tight position through the intermediate position, the locking mechanism of each head-side air damping mechanism blocks the head-side communication path before the piston reaches the intermediate position; and during the forward stroke in which each piston moves from the absolutely tight position to the fully open position through the intermediate position, the locking mechanism of each rod-side air damper mechanism blocks the rod-side communication path after the piston has passed the intermediate position.
    In this case, it is desirable that the lid is equipped with an air damper with which the shaft support comes into contact and which dampens the shock when the valve disk moves upwards from the fully open position into the intermediate position; that the air damper has a damper chamber formed on the lid, a buffer that is fixedly housed in the damper chamber, a damper rod that is housed in the damper chamber so that it is slidable, the proximal end facing the buffer, and that the distal end protrudes from the lid and includes a damper pressure chamber formed between the damper rod and the buffer; and that the damper pressure chamber is connected to the main flow paths on the rod side.
    Each air cylinder can be provided with a first locking mechanism for locking the valve plate in the fully open position and a second locking mechanism for locking the valve plate in the absolutely tight position.
    In the check valve of the present invention, both during the forward stroke and during the reverse stroke, the air damping mechanism causes the speeds of the pistons of the pair of air cylinders to be reduced when the check opening is opened and closed by the valve plate, so that the pistons in hit the stroke end positions slowly and the shock is dampened and the pistons come to a standstill. The development of impact noises is therefore inhibited.
    [Fig. 1] Figure 1 shows the front view of a check valve according to this invention, in a state in which a valve disk is in a fully open position with a part of the valve housing cut off.
    [Fig. 2] Figure 2 shows a sectional view along the line II-II in Figure 1.
    [Fig. 3] Figure 3 shows a front view of the check valve in a state in which the valve plate has moved from the state in Figure 1 to an intermediate position.
    [Fig. 4] Figure 4 shows a sectional view along the line IV-IV in Figure 3.
    [Fig. 5] Figure 5 shows a front view of the check valve in a state in which the valve plate has moved from the state in Figure 3 to an absolutely tight position.
    [Fig. 6] Figure 6 shows a sectional view along the line VI-VI in Figure 5.
    [Fig. 7] Figure 7 shows a sectional view, partially schematically showing the structure of an air cylinder pair and the arrangement of air flow paths in relation to the air cylinders.
    [Fig. 8] Figure 8 shows an enlarged sectional view of one of the paired air cylinders from Figure 7 and shows an operating position of the air cylinder when the valve disk is in the fully open position.
    [Fig. 9] FIG. 9 shows an enlarged sectional view of a concrete structure of a throttling section which is formed in the head-side throttling flow path in FIG. 8.
    [Fig. 10] Figure 10 shows a sectional view of an operating position of the air cylinder when the valve plate has moved from the state shown in Figure 7 to the intermediate position.
    [Fig. 11] Figure 11 shows a sectional view of an operating position of the air cylinder when the valve disk has moved from the state shown in Figure 10 to the absolutely tight position.
    [Fig. 12] Figure 12 is an enlarged view of an essential part and shows an enlarged view of part of the air damper section from Figure 7.
    [Fig. 13] Figure 13 shows an enlarged sectional view along the line XIII-XIII in Figure 2.
    [Fig. 14] Figure 14 shows an enlarged sectional view along the line XIV-XIV in Figure 6.
    [Fig. 15] Figure 15 is a diagram showing the interrelationship of the noises generated by opening / closing the valve plate with one stroke during the extension of each piston and with one stroke during the insertion of each piston in the check valve according to this invention .
    [Fig. 16] Figure 16 is a diagram showing the interrelationship of the noises generated by opening / closing the valve disc with one stroke while each piston is extended and with one stroke during the piston retraction in a well-known check valve.
    As shown in Figures 1 to 6, a check valve according to this invention comprises a hollow valve housing 1, which has a lock opening 2, which is connected to a vacuum process chamber (not shown), a valve plate 3, which is housed in the valve housing 1 and which opens and closes the blocking opening 2, a columnar valve stem 4, on the distal end of which the valve plate 3 is fixedly mounted, and an actuating mechanism 5 which causes the valve plate 3 to perform an opening / closing movement via the valve stem 4.
    The actuating mechanism 5 comprises a cover 6 through which the valve stem 4 slidably extends, a pair of cylinders consisting of a right air cylinder 7A and a left air cylinder 7B, both of which are arranged parallel to one another with the valve stem 4 placed in between on the cover 6, Drive rods 8 extending downward from both air cylinders 7A and 7B and a shaft support 9 attached to distal end portions of the drive rods 8.
    The shaft support 9 comprises a first block 11, which is fixed to the distal end portions of the drive rods 8, and a second block 12, which is connected to the first block 11 by a connecting member 13, which consists of an elastic body to be relatively displaceable. A proximal end portion of valve stem 4 is attached to second block 12.
    The check valve is one in which, by causing the drive rods 8 of the pair of air cylinders 7A and 7B to extend (move down) and retract (move up), the stem support 9 Valve stem 4 is caused to move down and up, so that valve disc 3 is in a fully open position P1 as shown in Figures 1 and 2, in an intermediate position P2 as shown in Figures 3 and 4 and in an absolutely tight position P3, as shown in Figures 5 and 6, is moved. The fully open position P1 is the position in which the valve plate 3 is in a downward position and the blocking opening 2 is fully open. The intermediate position P2 is the position in which the valve plate 3 has moved upwards and is separated from the blocking opening 2, although it faces the blocking opening 2. The absolutely tight position P3 is the position in which the valve plate 3 has pressed a valve seal 14 against a valve seat 15 around the blocking opening 2 in order to hermetically seal it.
    The valve disk 3 has essentially the shape of a rectangular plate which is elongated in the left-right direction and is provided with an annular sealing groove which is machined in a section of the outer circumference of a surface thereof. The annular valve seal 14, which consists of an elastic material, such as an O-ring, is mounted in the seal groove in such a way that part of the valve seal 14 protrudes from the seal groove.
    The valve housing 1 has a front wall Ia and a rear wall Ib, which are opposite to each other. The blocking opening 2 is machined in the front wall 1a, and an opening 2a for the rear part, which has essentially the same shape and the same size as the blocking opening 2, is machined in the rear wall 1b at the same height as the blocking opening 2.
    The blocking opening 2 is designed similar to the valve plate 3 as a rectangular, stretched in the left-right direction, the blocking opening 2 being smaller than the valve plate 3. In addition, the annular valve seat 15, which is formed from a flat surface, is provided on a portion of the outer circumference of the blocking opening 2 on an inner surface of the front wall 1a so that it encloses the blocking opening 2. Because the valve seal 14 is caused by the movement of the valve plate 3 to contact and separate from the valve seat 15, the blocking opening 2 is closed and opened.
    The cover 6 is attached to a bottom wall of the valve housing 1 in an airtight manner and the valve stem 4 is inserted into a through hole 16 incorporated in the bottom wall and the cover 6 so that it is in the direction of an axial line L1 of the valve stem 4 and in one direction is displaceable perpendicular to the axial line L1 (ie in the vertical direction to the valve seat 15).
    On an outside of the valve housing 1 from the through hole 16, the valve stem 4 is closed by a cylindrical suspension body 17 which expands and contracts due to the movement of the valve stem 4 in the direction of the axial line L1. One end of the suspension body 17 is attached to an outside of the cover 6 so that the through hole 16 is enclosed, and the other end of the suspension body 17 is attached to the second block 12 in an airtight manner.
    The pair of air cylinders 7A and 7B are provided at opposite positions with the valve stem 4 interposed. Each of the two air cylinders 7A and 7B includes a prismatic hollow cylinder housing 20. The inner walls 20a of the cylinder housings 20, which face the cam frames 27 on side surfaces of the first block 11, are fixed perpendicularly along an axial line L2 to a bottom of the cover 6. Therefore, the drive rods 8 move up and down along the axial line L2.
    In the present embodiment, the inner walls 20a of the cylinder housing 20 are also roller cages for receiving the guide rollers 33a, 33b, 33c and 33d, which are described below. Therefore, in the following description, the inner walls 20a can also be referred to as “roller cages 20a”. However, the roller cages 20a only have to be permanently assigned to the cylinder housings 20 of the air cylinders 7A and 7B. For example, the roller cages 20a can also be designed separately from the cylinder housings 20 and attached to the cylinder housings 20.
    As can be clearly seen from Figure 7, a head-side opening 21 and a rod-side opening 22 are provided on an outer side of the cylinder housing 20 of the air cylinder 7A from the air cylinder pair 7A and 7B. By supplying and discharging compressed air to and from the air cylinder pair 7A and 7B through the head-side opening 21 and the rod-side opening 22, the pistons 23 in the cylinder housings 20 extend (downward movement) and in (upward movement), so that the drive rods 8 extend (Downward movement) and retract (upward movement).
    As an example, the structures of the air cylinders 7A and 7B and the arrangement of the air flow paths will be described in more detail later.
    The first block 11 of the shaft support 9 includes a support plate 26 which is provided between a distal end portion of the drive rod 8 of the air cylinder 7A and a distal end portion of the drive rod 8 of the air cylinder 7B, and a pair of left and right cam frames 27, the proximal end portions are attached to the support plate 26 and have plate shapes that extend upward and parallel to the axial line L2. The cam frames 27 are arranged between the second block 12 and the inner wall 20a of the air cylinder 7A and 7B, respectively.
    The carrier plate 26 is in the form of a plate which is stretched to the right and left, and is attached to a side opposite the cover 6, with the second block 12 being connected therebetween, and extends parallel to the cover 6 concave-shaped spring plate 28 is formed on one side of the carrier plate 26, opposite the second block 12, and a compression spring, which represents the connecting element 13, is arranged between the spring plate 28 and the second block 12. Therefore, the connecting element compression spring 13 is referred to in the following description.
    The second block 12 of the stem support 9 is attached to the proximal end portion of the valve stem 4. The second block 12 is substantially H-shaped in the front view and includes a first concave portion 30 formed in the middle of an end face facing the lid 6, a pair of shoulder portions 31 each on the corresponding left one and right side wall are formed, which together define the first concave portion 30, and a second concave portion 32, which is formed in the middle of an end face on the side opposite to the cover 6 in the direction of the axial line LI. The valve stem 4 extends through the center of the first concave portion 30 and the center of the second concave portion 32 and is fixed to the second block 12. Furthermore, the suspension body 17, one end of which is fastened to the cover 6, is fastened with its other end to the first concave section 30 and the compression spring 13, one end of which is fastened to the spring plate 28 of the carrier plate 26, with its other end End attached to the second concave portion 32.
    In this way, by connecting the support plate 26 of the first block 11 and the second block 12 by the compression spring 13, the second block 12 can be moved relative to the first block 11 in the directions in which the compression spring 13 is pulled apart and is compressed (in the directions of the axial line L1 of the valve stem 4 and parallel to the surface of the valve seat 15) and in the directions perpendicular thereto (directions perpendicular to the surface of the valve seat 15).
    In order to move the valve plate 3 into the fully open position P1, the intermediate position P2 and the absolutely tight position P3, the check valve has a mechanism for a parallel movement and a mechanism for a vertical movement.
    The mechanism for the parallel movement moves the valve plate 3 parallel to the valve seat 15 from the fully open position P1 in Figures 1 and 2 to the intermediate position P2 of Figures 3 and 4 and includes the plurality of guide rollers 33a, 33b, 33c and 33d, which are mounted on the roller cages 20a of the cylinder housings 20, and guide grooves 34, which are machined in the cam frame 27 of the first block 11.
    In the embodiment shown there are a total of four guide rollers, namely 33a, 33b, 33c and 33d, and these four guide rollers 33a, 33b, 33c and 33d are arranged in a row and aligned from top to bottom (parallel to the axial line L2 ).
    On the other hand, the guide grooves 34 are incorporated in the side surfaces of the cam frames 27, that is, in side surfaces opposite to one side of the roller cages 20a of the cylinder housings 20, so that they extend from the upper ends of the cam frames 27 parallel to the axial line L2 to extend to points near the lower ends. The guide grooves 34 are formed as concave grooves with a depth which corresponds to approximately 2/3 of the thicknesses of the cam frames 27 without extending through the cam frames 27 in the thickness direction thereof. The bottom walls 34a (see Fig. 13) of the guide grooves 34 are flat surfaces.
    Because of the upward movement of the drive rods 8, the first block 11 and the second block 12 move up together. When the valve plate 3 moves from the fully open position P1 to the intermediate position P2, as shown in Figures 2 and 4, the two lower guide rollers 33a and 33b, which were previously inserted into the guide grooves 34, move in the guide grooves 34 relative to the bottom, and the upper guide roller 33c is inserted into the guide groove 34 to prevent the first block 11 and the second block 12 from tilting with respect to the cylinder housings 20.As a result, the drive rods 8 and the valve plate 3 move parallel to the valve seat 15 from the fully open position P1 up to the intermediate position P2.
    As soon as the first block 11 and the second block 12 reach the intermediate position P2, the contact areas 35 of the two shoulder sections 31 of the second block 12 come into contact with the two air dampers 36, which are arranged on the underside of the cover 6 with the valve stem 4 arranged therebetween are formed, and the second block 12 stops at this position. The contact areas 35 are formed from rollers which are rotatable about a horizontal axis.
    The air dampers 36 are intended to absorb the impact that occurs when the second block 12 contacts the underside of the cover 6 in the intermediate position P2. The air dampers 36 have the function of absorbing shocks by air suspension and the function of absorbing shocks by means of rubber buffers, and they are constructed as follows.
    As shown in Fig. 12, each air damper 36 includes a damper chamber 40 formed on the lid 6. In the lower part of each damper chamber 40, a downward-facing, convex-shaped rubber buffer 41 is fixedly accommodated, and in an opening section of each damper chamber 40, a cap-shaped damping cushion holder 42 is screwed airtightly via a sealing element 43. By having the proximal end face of each damper rod 44 facing the buffer 41 and the distal end portion 44a of each damper rod 44 protruding downward from the cushion pad holder 42, each damper rod 44 is held by the cushion cushion holder 42 so that it extends and expands freely via the sealing member 45 retract (move up and down).
    The damper pressure chambers 46 are formed between the proximal end faces of the damper rods 44 and the buffers 41. The damper pressure chambers 46 are connected to the rod-side opening 22 via damper connection paths 47 and rod-side main flow paths 25 (see FIG. 7), and when the drive rods 8 move upwards, compressed air is supplied from the rod-side opening 22. If the drive rods 8 move downwards because the rod-side opening 22 is in the air discharge state, the damper pressure chambers 46 are also in the air discharge state.
    The air dampers 36 operate as follows. So when the contact areas 35 of the shoulder sections 31 of the second block 12 come into contact with the distal end sections 44a of the damper rods 44 in the intermediate position P2, the damper rods 44 retract as a result of the impact and the air in the damper pressure chambers 46 is compressed. The impact energy is thus absorbed by air damping acting at this point in time. As a result, the damper rods 44 are pushed by the second block 12 and continue to retract and stop at points where they contact the buffers 41. The impact energy is now absorbed by the spring force of each buffer 41. As soon as the damper rods touch and stop the buffers 41, the second block 12 also stops in this position.
    The mechanism for the vertical movement serves to move the valve plate 3 perpendicular to the valve seat 15 from the intermediate position P2 in Figures 3 and 4 to the absolutely tight position P3 in Figures 5 and 6. As shown in Figures 2, 4 and 6, the vertical movement mechanism comprises two cam grooves 50a and 50b, namely the upper and lower cam grooves formed in the cam frame 27 of the first block 11, and two cam rollers 51a and 51b , namely the upper and lower cam roller, which are attached to the second block 12. The upper, first cam roller 51a is fitted into the upper, first cam groove 50a, and the lower, second cam roller 51b is fitted into the lower, second cam groove 50b.
    The first curve groove 50a kinks in its entire orientation from one side of the cover 6 to one side of the carrier plate 26 increasingly towards the surface of the valve seat 15. An end portion of the first cam groove 50 a on the side of the cover 6 opens toward the cover 6. When the valve disk 3 is in the fully open position P1 and the intermediate position P2, as shown in FIGS. 2 and 4, the first cam roller 51a is in the first position CI at the upper end of the first cam groove 50a.
    In contrast, the second cam groove 50b includes an upper portion that is parallel to the first cam groove 50a (an area on the lid 6 side), and a lower portion that is oriented from the lid 6 side to Side of the support plate 26 gradually slopes away from the top of the valve seat 15 (an area on the side of the support plate 26). These two areas are connected to one another and form a concavely curved shape on a surface of the valve seat 15.
    If the valve plate 3 is in the fully open position P1 and in the intermediate position P2, as shown in Figures 2 and 4, then the second cam roller 51b is in a first position CI at an upper end of the second cam groove 50b .
    The mechanism of vertical movement works as follows. So if, after the second block 12 has stopped in the intermediate position P2, as shown in Figures 3 and 4, then the drive rods 8 move further up and the first block 11 moves together with the drive rods 8 and thereby presses Compression spring 13 together. Thus, the cam grooves 50a and 50b formed in the cam frame 27 move upward with respect to the cam rollers 51a and 51b, and as shown in Fig. 6, they move up to the positions C2 at the lower ends of the cam grooves 50a and 50b.
    As a result, because of the mutual effects between the cam rollers 51a and 51b and the cam grooves 50a and 50b, the second block 12 and the valve plate 3 move perpendicular to the valve seat 15 and the valve plate 3 presses the valve seal 14 against the valve seat 15, in order to then take absolutely tight position P3, in which the locking opening 2 is closed.
    At this time, the contact sections 35 are in contact with the damper rods 44 of the air dampers 36 and the second block 12 shifts with respect to the damper rods 44. Since the contact sections 35 are formed from rollers, the second block 12 becomes due to the Rotational movement of the rollers gently shifted.
    However, if the valve plate 3 is to be controlled from the absolutely tight position P3 to the fully open position P1 via the intermediate position P2, then the drive rods 8 of the two air cylinders 7A and 7B are moved downwards in order to carry out operations which perform the aforementioned Operations are opposite.
    Next, for example, the structures of the paired air cylinders 7A and 7B and the arrangement of the air flow paths will be described in detail with reference to FIGS. 7 to 11.
    The two air cylinders 7A and 7B each include an air suspension mechanism that dampens the shock when the lock opening 2 is opened and closed by the valve plate 3, and both have the same internal structure. However, since the head-side opening 21 and the rod-side opening 22 are formed in the one air cylinder 7A, which is located on the right in FIG. 7, the arrangement of the air flow paths differs slightly.
    In the following description, if necessary, the one air cylinder 7A in which the head-side opening 21 and the rod-side opening 22 are incorporated is referred to as the first air cylinder 7A and the other air cylinder 7B is referred to as the second air cylinder 7B. If a distinction between the air cylinders 7A and 7B and their separate designation is not necessary, then they are both simply called “air cylinders 7”. Figures 8, 10 and 11 typically show the first air cylinder 7A.
    As illustrated in Figures 7 and 10, each air cylinder 7 includes the hollow cylinder housing 20 which is attached to one end of the cover 6. One end (the upper end) of each cylinder housing 20 is hermetically sealed by the cover 6, and the other end (the lower end) of each cylinder housing 20 is closed by a cylindrical collar 53 which is inserted into the cylinder housing 20 by means of three O-rings 54a, 54b and 54c is inserted airtight. Each collar 53 is fastened to the cylinder housing 20 with a C-shaped locking ring 55.
    The pistons 23 are fitted in the cylinder housings 20 with piston seals 56 and guide rings 57 in such a way that they can be displaced in the direction of the axial line L2. The proximal ends of the drive rods 8 are connected to the pistons 23 by means of connecting screws 58. The distal ends of the drive rods 8 are slidably inserted into the center holes of the collars 53 via bearing elements 59 and rod seals 60 and extend downward from the cylinder housings 20.
    Each head-side pressure chamber 61, which is delimited by the piston 23 and the cover 6, is formed on a surface side of the piston 23. Each rod-side pressure chamber 62, which is delimited by the piston 23 and the collar 53, is formed on the other surface side of the piston 23. The cover 6 thus forms an end face of each pressure chamber 61 on the head side and the collars 53 are the end faces of the pressure chambers 62 on the rod side. The collars 53 are part of the cylinder housing 20.
    Round columnar head-side damper shafts 63, which protrude from the cover 6 into the head-side pressure chambers 61 along the axial line L2, are provided on the head-side pressure chambers 61. The head-side damper shafts 63 are fastened to the cover 6 in that the screw sections 65a at the distal ends of the fastening bolts 65, which are fitted airtightly in the fastening bores 64 of the cover 6 by means of O-rings 66, into the screw holes 63a at the upper end sections the head-side damper shafts 63 are screwed in. Head-side connecting paths 67, which open into the head-side pressure chambers 61, are formed in the middle of the head-side damper shafts 63 and the center of the fastening bolts 65. The head-side connection paths 67 are connected to the head-side main flow paths 24, which are connected to the head-side opening 21.
    Head-side throttling flow paths 68, each having a throttling section 69 that has a small flow cross-section, are incorporated in the cover 6 to cause the head-side pressure chambers 61 and the head-side main flow paths 24 to communicate with one another. The head-side throttling flow paths 68 and the head-side connection paths 67 are arranged in parallel.
    As shown in Fig. 9, the throttling portion 69 of each head-side throttling flow path 68 is formed by a needle valve 70. The needle valves 70 are accommodated via 0-rings 72 in valve holes 71 which are provided in the cover 6b. The throttling portions 69 are formed by the distal ends of the needles 70a. Each needle valve 70 may have a structure that allows the flow path cross-sectional area of the throttling portion 69 to be regulated by causing the needle valve 70 to freely move back and forth.
    However, each throttling section 69 can be realized through a small opening with a small cross-sectional area and need not be formed by the needle valve 70.
    As shown in Figures 7 and 10, the main flow path 24 includes a first portion 24a which extends from the head opening 21 across a side wall of the cylinder housing 20 of the first air cylinder 7A to an annular flow path 73 which is one encloses outer boundary surface of the collar 53, extends a second section 2b, which extends from the annular flow path 73 to the cover 6 by passing through the side wall of the cylinder housing 20 parallel to the axial line L2, and a pair of third sections 24c and 24c which represent branches of the second section 24b and extend in opposite directions into the cover 6. One of the third sections 24c communicates with the head side communication path 67 and the head side throttling flow path 68 of the first air cylinder 7A, and the other third section 24c communicates with the head side connection path 67 and the head side throttling flow path 68 of the second air cylinder 7B.
    Concave shaped head damper holes 74 opening into the head pressure chambers 61 are machined into the pistons 23 along the axial line L1, and head damper packs 75 are provided at the open ends of the head damper holes 74. When the head-side damper shafts 63 are inserted into the head-side damper holes 74 through the head-side damper packs 75, as soon as the pistons 23 moving upward have passed an intermediate position of an upward stroke and are approaching the end of an upward stroke, the head-side connecting paths 67 are separated from the head-side pressure chambers 61 to provide air cushioning.
    Each damper packing 75 on the head side is a lip-shaped packing, the sealing property of which is direction-dependent. The lips, which are oriented such that an air flow flowing from the head-side pressure chambers 61 in the direction of the head-side damper holes 74 is blocked and an air flow which flows from the head-side damper holes 74 in the direction of the head-side pressure chambers 61, are passed attached to the piston 23.
    Distal end portions 63b of the head-side damper shafts 63 have a conical shape that gradually becomes narrower in order to facilitate the insertion of the distal end portions 63b into the head-side damper packs 75.
    The head-side damper shafts 63, the head-side damper holes 74, the head-side damper packs 75, the head-side connecting paths 67 and the head-side throttling flow paths 68 form the head-side air damping mechanisms.
    The head-side damper shafts 63, the head-side damper holes 74 and the head-side damper packs 75 form locking mechanisms for blocking the head-side connecting paths 67 from the head-side pressure chambers 61.
    In contrast, on one side of the rod-side pressure chamber 62 of each air cylinder 7 in the collar 53 along the axial line L2, a concave-shaped rod-side damper hole 78, which opens into the rod-side pressure chamber 62, is provided. The drive rods 8 extend in the middle of each rod-side damper hole 78. The rod-side damper holes 78 communicate with the rod-side opening 22 via the rod-side main flow paths 25.
    The rod-side main flow path 25 comprises a first section 25a, which extends from the rod-side opening 22 across the side wall of the cylinder housing 20 of the first air cylinder 7A to an annular flow path 79 which surrounds the outer boundary surface of the collar 53, and a second portion 25b that extends from the annular flow path 79 through the inside of the collar 53 to the rod-side damper hole 78. The rod-side main flow path 25 communicates with the rod-side pressure chamber 62 of the first air cylinder 7A via the rod-side damper hole 78. Therefore, the rod-side damper hole 78 can be defined as a rod-side connection path that connects the rod-side main flow path 25 and the rod-side pressure chamber 62.
    In order for the rod-side opening 22 to communicate with the rod-side pressure chamber 62 of the second air cylinder 7B, the rod-side main flow path 25 comprises a third section 25c, which extends from the annular flow path 79 of the first air cylinder 7A to the cover 6, in parallel to the axial line L2 within the side wall of the cylinder housing 20 of the first air cylinder 7A, a fourth section 25d which extends transversely inside the cover 6, a fifth section 25e which extends downward from the fourth section 25d along the axial line L2 within one Side wall of the cylinder housing 20 of the second air cylinder 7B extends and communicates with an annular flow path 79 which surrounds an outer boundary surface of the collar 53, and a sixth section 25f which connects the annular flow path 79 and the rod-side damper hole 78 within the collar 53 with each other. The rod side main flow path 25 communicates with the rod side pressure chamber 62 of the second air cylinder 7B via the rod side damper hole 78. The fourth section 25d also communicates with the damper communication paths 47 of the air damper 36.
    A rod-side throttling flow path 80, which includes a throttling portion 81 having a small flow path cross-sectional area, is provided within the collar 53 of the first air cylinder 7A as well as the second air cylinder 7B. The rod-side throttling flow paths 80 connect the rod-side pressure chambers 62 and the rod-side damper holes 78 to one another. Therefore, the rod side throttling flow paths 80 and the rod side damper holes 78 (the rod side connecting paths) are connected in parallel between the rod side main flow paths 25 and the rod side pressure chambers 62.
    In the illustrated example, the throttling portion 81 of each rod-side throttling flow path 80 is formed by a needle valve 82. The needle valves 82 are arranged in parallel to the axial line L2 through O-rings 84 in valve holes 83 formed in the collars 53, and the throttling portions 81 are formed by distal ends of the needles 82a. The needle valves 82 may also be configured so that when they are caused to move freely back and forth, the flow path cross-sectional areas of the throttling portions 81 are adjustable.
    Nevertheless, the throttling sections 81 need not be formed by the needle valves 82, but can also be designed starting from a small bore with a small cross-sectional area.
    Rod-side damper shafts 85 with a diameter that is larger than the diameter of the drive rods 8 are provided on portions of the pistons 23 of the air cylinders 7A and 7B, to which the drive rods 8 are connected. A rod side damper pack 86 is attached to an open side of each rod side damper hole 78.
    By inserting the rod-side damper shafts 85 into the rod-side damper holes 78 via the rod-side damper packs 86, as soon as the pistons 23 have passed an intermediate position of the downward stroke in the downward movement and are approaching the end position of the downward stroke, the rod-side damper holes 78 become from the rod-side Pressure chambers 62 separated to effect air damping. In order for the insertion to proceed smoothly, each rod-side damper shaft 85 has a distal end portion 85a, which has a conical, gradually narrowing shape.
    Each damper packing 86 on the rod side is a lip-shaped packing, the sealing properties of which depend on the direction. The lips, which are oriented so that an air flow flowing from the rod-side pressure chambers 62 to the rod-side damper holes 78 and a flow of air flowing from the rod-side damper holes 78 to the rod-side pressure chambers 62 are let through, are attached to the rod-side damper holes 78.
    The rod-side damper shafts 85, the rod-side damper holes 78 (the rod-side connecting paths), the rod-side damper packings 86 and the rod-side throttling flow paths 80 form rod-side air damping mechanisms.The rod-side damper shafts 85, the rod-side damper holes 78 and the rod-side damper packs 86 form locking mechanisms for blocking the rod-side connecting paths from the rod-side pressure chambers 62.
    Next, the operations of the paired air cylinders 7A and 7B will be described.
    Figures 8, 10 and 11 show an operating state of the first air cylinder 7A, but its mode of operation is the same as that of the second air cylinder 7B.
    Figures 7 and 8 show the operating states of the air cylinders 7A and 7B when the valve plate 3 is in the fully open position P1 from Figure 1. At this time, the head-side opening 21 is in the state of the air supply and the rod-side opening 22 is in the state of the air discharge. Air from the top opening 21 is thus supplied from the top main flow paths 24 via the top connection paths 67 inside the top damper shafts 63 and the top throttling flow paths 68 to the top pressure chambers 61 of the air cylinders 7A and 7B, and in the rod side pressure chambers 62 of the air cylinders 7A 7B and 7B air is discharged from the rod-side opening 22 through the rod-side damper holes 78 (the rod-side connection paths) and the rod-side throttling flow paths 80 via the rod-side main flow paths 25.
    In order to move the valve plate 3 from this state into the absolutely tight position P3 in FIGS. 5 and 6, when the head-side opening 21 is set up for air discharge and the rod-side opening 22 for air supply, air is caused from the rod-side opening 22 to flow into the rod-side damper holes 78 through the rod-side main flow paths 25, and as a result the rod-side damper packs 86 are pressed open so that the air can flow freely into the rod-side pressure chambers 62; and the air in the head-side pressure chambers 61 is drained from the head-side connection paths 67 in the head-side damper shafts 63 through the head-side main flow paths 24 from the head-side opening 21 so that the pistons 23 move upward without slowing down their driving speed.
    [0100] Although the air from the rod-side damper holes 78 also flows into the rod-side pressure chambers 62 through the rod-side throttling flow paths 80, the amount is very small at this time. In this phase, the air in the head-side pressure chambers 61 is also discharged through the head-side throttling flow paths 68 into the head-side main flow paths 24, but the amount is very small.
    If the pistons 23 move upward, the valve disk 3 moves via the intermediate position P2 shown in FIGS. 3 and 4 into the absolutely tight position P3 shown in FIGS. 5 and 6. Figure 10 shows an operating state of each cylinder 7 after the valve plate 3 has reached the intermediate position P2.
    At this moment, the two pistons 23 are in a position where they pass the intermediate position of the upward stroke and have approached the end of the upward stroke. The head-side damper shafts 63 have already been inserted into the head-side damper holes 74 at this moment. The rod-side damper shafts 85 are fully extended from the rod-side damper holes 78. The connection between the head-side pressure chambers 61 and the head-side connection paths 67 is separated, so that the air in the head-side pressure chambers 61 is discharged, the volume flow being limited by the head-side throttling flow paths 68.
    In the intermediate position P2, however, as described above, the second block 12 of the shaft actuation mechanism 9 comes into contact with the air dampers 36 and stops. Since the air is now supplied from the rod-side opening 22 to the air dampers 36 via the rod-side main flow paths 25, the air-damping effect sets in, so that the shock is cushioned as soon as the second block 12 hits the air dampers 36.
    If immediately before the valve plate 3, i.e. the pistons 23 reach the intermediate position P2, the air in each head-side pressure chamber 61 is discharged with a limited flow speed, the air damping ensures that the speed of each piston 23 is reduced and that each piston 23 is then moved upwards at low speed to the absolutely tight position P3, as shown in Figure 11. In the absolutely tight position P3, the pistons 23 come into contact with the end walls of the pressure chambers 61 on the head side, that is to say the underside of the cover 6, the impact being cushioned, and stop. This position corresponds to the end of the upward stroke of the pistons 23. Since the pistons 23 collide with the room walls at a reduced speed at this moment, impact noises and vibrations caused by the touch, for example, are prevented in the beginning.
    As soon as the valve plate 3 is moved from the absolutely tight position P3 to the fully open position P1, the head-side opening 21 changes to the air supply operating state and the rod-side opening 22 changes to the air discharge operating state. Now, air flows from the top opening 21 via the top main flow paths 24 and the top connection paths 67 in the top damper shafts 63 into the top damper holes 74, and as a result the top damper packs 75 are pressed open so that the air flows freely into the top pressure chambers 61 can flow; and air in the rod-side pressure chambers 62 is freely discharged from the rod-side damper holes 78 via the rod-side main flow paths 25 from the rod-side opening 22, so that the pistons 23 move downward without slowing down their driving speed.
    Then, after the rod-side damper shafts 85 have been inserted into the rod-side damper holes 78 after the pistons 23 have moved further downward through the intermediate position P2 in Figure 10 and passed the intermediate position of the downward stroke, the connection between the rod-side pressure chambers becomes 62 and the rod-side damper holes 78 are set. The air in the rod-side pressure chambers 62 is therefore discharged via the rod-side throttling flow paths 80 with a limited volume flow. The air damping thus has the effect that the speed of each piston 23 is reduced and each piston 23 then moves slowly down to the fully open position P1 shown in FIG. 8. In the fully open position P1, the pistons 23 come into contact with the end walls of the rod-side pressure chambers 62, that is to say the upper sides of the collars 53, the shock being cushioned, and stop. This position corresponds to the end position of the downward stroke of the pistons 23. Since the pistons 23 come into contact with the collars 53 at a reduced speed at this point, impact noises and vibrations caused by the contact are prevented even in the beginning.
    Since the air cylinders 7A and 7B in the check valve are both equipped with the head-side air damper mechanism and the rod-side air damper mechanism, the pistons 23 are reduced in speed by the onset of air damping as they approach the end of the upward stroke and the end of the stroke Approach downward stroke, stopped, cushioning the impact both at the end of the upward stroke and at the end of the downward stroke. As soon as the valve plate 3 is caused to open or close the blocking opening 2, the impact of the pistons 23 on the head-side pressure chambers 61 and the rod-side pressure chambers 62 is reduced in such a way that noises caused by the impact are prevented in the beginning become.
    The operations of speed throttling by the air damping mechanisms in the end position of the upward stroke and in the end position of the downward stroke of the pistons 23 are carried out synchronously in both cylinders of the pair of air cylinders 7A and 7B.
    Figure 15 shows a diagram illustrating the relationships between the stroke of each piston 23 and noise in the check valve of this embodiment. The diagram below shows the results of measurements of the noises that occur as a result of a piston stroke if each of the pistons 23 moves over a certain period of time after the upward movement from the fully open position P1, which corresponds to the end position of the downward stroke (forward stroke) Intermediate position P2 moves up to the absolutely tight position P3, which corresponds to the end position of the upward stroke (reverse stroke), and moves from the absolutely tight position P3 down to the fully open position P1 via the intermediate position P2, which corresponds to the end position of the downward stroke.
    For comparison, Figure 16 shows, for example, a diagram that illustrates the relationships between piston strokes and noise of a publicly known valve without air damping mechanisms. In this example given for comparison purposes, an impact noise a that occurs when the pistons hit the end walls of the head-side pressure chambers at the end of the upward stroke (the absolutely tight position P3) and an impact noise b that occurs when the pistons at the end of the Downward strokes (the fully open position P1) hit the end walls of the rod-side pressure chambers, very strongly, whereas the impact noise a and the impact noise b in Figure 15 have been significantly attenuated.
    As for a noise c that is believed to be due, for example, to an impact noise that arises when the second block 12 of the shaft support 9 hits the cover 6, or to an impact noise that arises when the Move cam rollers 51a and 51b during the upward stroke of each piston 23 in the vicinity of the intermediate position P2 into the cam grooves 50a and 50b, and as far as a noise d is concerned, which is presumed to be due to a contact noise which arises when the If cam rollers 51a and 51b move into the cam grooves 50a and 50b during the downward stroke of each piston 23 near the intermediate position P2, the noises in the comparative example in FIG. 16 are very strong, whereas it can be seen that the noises in FIG. 15 are considerable are reduced.
    As shown schematically in Figures 7, 8, 10 and 11, a first locking mechanism 91 for locking the valve plate 3 in the fully open position P1 and a second locking mechanism 92 for locking the valve plate 3 in the absolutely tight position P3 the cylinder housing 20 of each of the two air cylinders of the pair of air cylinders 7A and 7B in the check valve. These first locking mechanisms 91 and the second locking mechanisms 92 are arranged on the roller cages 20a of the cylinder housings 20 lying side by side along the axial line L2.
    [0113] The first locking mechanisms 91 are arranged above the second locking mechanisms 92, that is to say closer to the cover 6.
    As shown in Figures 13 and 14, each first locking mechanism 91 includes a locking piston 93 on the roller cage 20a, the locking piston 93 being supported so that it can freely move back and forth with respect to the cam frame 27. Each locking piston 93 includes a piston section 94 at its proximal end and an engaging shaft section 95 at its distal end. Each piston section 94 is displaceably arranged in a piston chamber 96, which is formed in the roller cage 20a, via a piston seal 97, and each engaging shaft section 95 is mounted in a guide bore 99 of a locking cover 98 fixedly attached to the roller cage 20, so that it covers one another seal 100 located on the shaft section and a bushing 101 can freely move back and forth. The diameter of each engaging stem portion 95 is less than the diameter of each piston portion 94, and the distal end of each engaging stem portion 95 has a diameter that is less than the diameter of the portion from the seal 100 and the stem portion the socket 101 is guided.
    Locking springs 103 are provided between the concave portions 102 formed on the end faces of the piston portions 94 and the bottoms of the piston chambers 96, and the locking pistons 93 are normally urged by the locking springs 103 in a direction in which the distal ends the engaging shaft sections 95 emerge from the guide bores 99.
    Release pressure chambers 104 are provided between the piston seals 97 and the seals 100 located on the shaft section, the release pressure chambers 104 communicating with the rod-side main flow paths 25 via the release connection paths 105. Specifically, as shown in Figures 7 and 10, in particular, the release pressure chamber 104 of the first lock mechanism 91 provided on the first air cylinder 7A communicates with the third portion 25c of the rod-side main flow path 25 via the release link 105 and, as shown in Figure 7, the Release pressure chamber 104 of the first lock mechanism 91 provided on the second air cylinder 7B via the release connection path 105 with the fifth portion 25e of the rod-side main flow path 25.
    In contrast, the second locking mechanisms 92 have a structure that substantially corresponds to that of the first locking mechanisms 91, except for part of the structure. The individual elements that are part of the second locking mechanisms 92 are identified by an information sign, namely by an “a” that is attached to the information sign of each element that is part of the first locking mechanisms 91 and are not described in detail .
    [0118] A first difference between the second locking mechanisms 92 and the first locking mechanisms 91 is that the unlocking pressure chambers 104a of the second locking mechanisms 92 communicate with the head-side main flow paths 24 via the unlocking connection paths 105a. Strictly speaking, as shown in Figures 7 and 10, the release pressure chamber 104a of the second lock mechanism 92 provided on the first air cylinder 7A communicates with the second portion 24b of the head side main flow path 24 via the release connection path 105a, and as shown in Figure 7 , the unlocking pressure chamber 104a of the second locking mechanism 92 provided on the second air cylinder 7B communicates via the unlocking connection path 105a with a fourth section 24d, which branches off from the third section 24c of the head-side main flow path 24 and in the direction of the axial line L2 inside the side wall of the cylinder housing 20 of the second air cylinder 7B.
    [0119] A second difference between the second locking mechanisms 92 and the first locking mechanism 91 is that the diameters of the distal ends of the engaging shaft portions 95a of the locking pistons 93a do not taper.
    The operations of the first locking mechanisms 91 and the second locking mechanisms 92 will be described next.
    As shown in Figures 1, 2 and 7, when the valve disc 3 is in the fully open position P1, that is, when the pistons 23 and the drive rods 8 of the air cylinders 7A and 7B have reached their end positions during the downward stroke , the head-side opening 21 in the state of the air supply and the rod-side opening 22 in the state of the air discharge. Thus, since the unlocking pressure chambers 104 of the first locking mechanisms 91 communicate with the rod-side opening 22, they are in the state of air discharge, and since the unlocking pressure chambers 104a of the second locking mechanisms 92 communicate with the head-side opening 21, they are in the state of the air supply.
    The locking pistons 93 of the first locking mechanisms 91 are thus, as shown in Figure 13, pressed by the locking springs 103 and advance into the locking positions, so that the distal ends of the engaging shaft portions 95 with the engagement portions 34b, which at upper end portions of the Guide grooves 34 of the cam frame 27 are formed, come into engagement. As a result, the cam frame 27, that is, the first block 11, is in a coupled state with the roller cages 20a of the cylinder housing 20 and the upward movement thereof is prevented, so that the valve plate 3 is locked in the fully open position P1 .
    [0123] The locking pistons 93a of the second locking mechanisms 92, on the other hand, compress the locking springs 103a and retract under the influence of air in order to assume unlocking positions.
    If, in order to move the valve disk 3 from this state into the absolutely sealed position P3 from FIGS. 5 and 6, the head-side opening 21 is put into the state of air discharge and the rod-side opening 22 into the state of the air supply, then the unlocking pressure chambers 104 of the first locking mechanisms 91 are in the state of the air supply and the unlocking pressure chambers 104a of the second locking mechanisms 92 are in the state of the air discharge.
    Thus, as indicated by the solid line in Figure 14, the lock pistons 93 of the first lock mechanisms 91 retract by the action of the air while compressing the lock springs 103 and assume unlock positions spaced from the engaging portions 34b. so that the cam frames 27, that is to say the first block 11, can or can move upwards.
    The locking pistons 93a of the second locking mechanisms 92, however, as shown by the chain line in Figure 14, are pushed by the locking springs 103a and move forward so that the distal ends of the engaging shaft portions 95a with flat bottoms 34a of the guide grooves 34 of the Cam frames 27 are in contact so that they are relatively movable up and down along the guide grooves 34. At this time, the distal ends of the engaging shaft portions 95a are not engaged with the cam frame 27.
    Due to the action of the air cylinders 7A and 7B, the valve plate 3 moves upwards into the absolutely tight position P3, and, as shown in FIG. 14, when the locking holes 34c provided in the bottoms of the guide grooves 34 rise up to the Positions of the lock pistons 93a, the lock pistons 93a are pushed and moved forward by the lock springs 103a, and the distal ends of the engaging shaft portions 95a are inserted inside and engaged with the snap holes 34c. The locking pistons 93a thus occupy the locking positions. As a result, the cam frames 27, that is to say the first block 11, are or are in a coupled state with the roller cages 20a of the cylinder housings 20 and a downward movement of the same or the same is prevented , so that the valve disc 3 is locked in the absolutely tight position P3.
    If the valve disk 3 is to be moved from the absolutely tight position P3 to the fully open position P1, as described above, then the head-side opening 21 and the unlocking pressure chambers 104a of the second locking mechanisms 92 are in the state of the air supply and the rod-side opening 22 and the unlocking pressure chambers 104 of the first locking mechanisms 91 in the state of air discharge.
    [0129] The locking pistons 93a of the second locking mechanisms 92 thus retract while compressing the locking springs 103a due to the action of air, and assume unlocking positions where they have moved out of the latching holes 34c so that the first block 11 can move downward .
    The locking pistons 93 of the first locking mechanisms 91 in turn move forward due to the pressure of the locking springs 103, and the distal ends of the engaging shaft portions 95 are in contact with the flat bottoms 34a of the guide grooves 34 of the cam frames 27 so as to be along the Guide grooves 34 are relatively movable in the up and down direction. At this time, the distal ends of the engaging shaft portions 95a are not engaged with the cam frame 27.
    When the valve plate 3 moves downward to the fully open position P1 under the action of the air cylinders 7A and 7B, and the engaging portions 34b at the upper ends of the guide grooves 34 of the cam frames 27 down to the positions of the lock pistons 93 of the first Locking mechanisms 91 move, as shown in Figure 13, then the locking pistons 93 are pushed by the locking springs 103 and move forward, and the distal ends of the engaging shaft portions 95 engage the engaging portions 34b so that the valve disc 3 in the fully open position P1 is locked.
    Since the first locking mechanisms 91 and the second locking mechanisms 92 are provided on the air cylinder pair 7A and 7B, and since the valve plate 3 is locked in the fully open position P1 and the absolutely tight position P3 by the first locking mechanisms 91 and the second locking mechanisms 92 Even if the pressure of the air supplied to the air cylinders 7A and 7B fluctuates or the supply of air to the air cylinders 7A and 7B is blocked, it is possible, for example, to prevent an unexpected displacement of the valve plate 3 and to convince in terms of stability.
    List of information signs
    2 blocking opening 3 valve plate 4 valve stem 5 actuating mechanism 6 cover 7A, 7B air cylinder 8 drive rod 9 stem support 20 cylinder housing 21 head-side opening 22 rod-side opening 23 piston 24 head-side main flow path 25 rod-side main flow path 36 air damper 40 damper chamber 41 buffer part 44 damper rod 46 damper pressure chamber 61 head-side 62 rod-side pressure chamber 63 head-side damper shaft 67 head-side connection path 68 head-side throttling flow path 74 head-side damper hole 75 head-side damper packing 78 rod-side damper hole (rod-side connection path) 80 rod-side throttling flow path 85 rod-side damper shaft 86 rod-side locking mechanism P3 opening position 91 lock-up locking mechanism P2 interlocking position 92 locking mechanism 92 opening 91 tight position
    权利要求:
    Claims (7)
    [1]
    1. A low noise check valve comprising:a valve plate (3) which opens and closes a blocking opening (2), a valve stem (4), the distal end of which is connected to the valve plate (3), and an actuating mechanism (5) which causes the valve plate (3) perform an opening / closing process for the valve stem (4),characterized in that the actuating mechanism (5) comprises a cover (6) through which the valve stem (4) extends, an air cylinder pair (7A, 7B) consisting of a left and a right air cylinder which are attached to the cover (6) parallel to each other with valve stem (4) placed in between, and a head-side opening (21) and a rod-side opening (22), which allow the supply and discharge of air to and from the air cylinder pair (7A, 7B),characterized in that each air cylinder includes a cylinder housing (20) attached to the cover (6), a piston (23) housed in the cylinder housing (20) so that it can move freely back and forth, a drive rod (8), the proximal end of which is connected to the piston (23) and the distal end of which protrudes from the cylinder housing (20), and a head-side pressure chamber (61) and a rod-side pressure chamber (62), one of which is connected to the one end and the other is formed on the other end of the piston (23),characterized in that the head-side pressure chambers (61) communicate with the head-side opening (21) via head-side main flow paths (24) formed on the cylinder housings (20) and the cover (6), and the rod-side pressure chambers (62) the rod-side opening (22) communicate via the rod-side main flow paths (25) which are formed on the cylinder housings (20) and the cover (6),characterized in that a proximal end portion of the valve stem (4) is supported by the drive rods (8) of the pair of air cylinders (7A, 7B) via a stem support (9), the valve disc (3) assumes a position in which the blocking opening (2) as a result of a forward stroke of the pistons (23) and the drive rods (8) is opened, and the valve plate (3) assumes a position in which the blocking opening (2) is closed as a result of a reverse stroke of the pistons (23) and the drive rods (8) ,characterized in that each air cylinder comprises an air damping mechanism on the head side and an air damping mechanism on the rod side, which reduce shocks associated with the opening and closing of the blocking opening (2) by the valve plate (3),characterized in that each head-side air damping mechanism includes a head-side communication path (67) and a head-side throttling flow path (68) connecting the head-side pressure chamber (61) and the head-side main flow path (24) in parallel, and a locking mechanism that connects the head-side communication path (67 ) locks when the returning piston (23) approaches the end position of the reverse stroke, andcharacterized in that each rod-side air damping mechanism includes a rod-side communication path (78) and a rod-side throttling flow path (80) connecting the rod-side pressure chamber (62) and the rod-side main flow path (25) in parallel, and a locking mechanism which connects the rod-side communication path (78 ) locks when the forward-moving piston (23) approaches the end position of the forward stroke.
    [2]
    2. Blocking valve according to claim 1, characterized in that the blocking mechanism of each head-side air damping mechanism has a head-side damper shaft (63) which projects from an end wall of the head-side pressure chamber (61) into the head-side pressure chamber (61), a concave-shaped head-side damper hole (74 ), which is formed in the piston (23) so that the head-side damper shaft (63) fits into it when the piston (23) approaches the end position of the rearward stroke, and a head-side damper pack (75) which forms a section between one seals inner boundary surface of the head-side damper hole (74) and an outer boundary surface of the head-side damper shaft (63), and that the head-side connection path is formed in the head-side damper shaft (63), andcharacterized in that the locking mechanism of each rod-side air damper mechanism includes a concave rod-side damper hole (78) formed in an end wall of the rod-side pressure chamber (62), a rod-side damper shaft (85) which fits into the rod-side damper hole (78) when the piston (23) has approached the end position of the forward stroke, anda rod-side damper packing (86) sealing a portion between an inner boundary surface of the rod-side damper hole (78) and an outer boundary surface of the rod-side damper shaft (85), and the rod-side connection path is formed from the rod-side damper hole (78).
    [3]
    3. shut-off valve according to claim 2, characterized in that each head-side damper packing (75) is designed such that an air flow flowing from the head-side pressure chamber (61) to the head-side damper hole (74) blocks and one from the head-side damper hole (74) to the head-side pressure chamber (61) flowing air flow is allowed through, andcharacterized in that each rod-side damper pack (86) is designed such that an air flow flowing from the rod-side pressure chamber (62) to the rod-side damper hole (78) blocks and an air flow flowing from the rod-side damper hole (78) to the rod-side pressure chamber (62) is let through becomes.
    [4]
    4. shut-off valve according to one of claims 1 to 3, characterized in that all head-side connection paths and all head-side throttling flow paths (68) of the head-side air damping mechanisms of the air cylinder pair (7A, 7B) communicate with the head-side main flow paths (24) and all rod-side connection paths and rod-side throttling flow paths (80) of the rod-side air damping mechanisms of the air cylinder pair (7A, 7B) communicate with the rod-side main flow paths (25), so that the head-side air damping mechanisms and the rod-side air damping mechanisms of the air cylinder pair (7A, 7B) operate synchronously with one another.
    [5]
    5. shut-off valve according to one of claims 1 to 4, characterized in that each piston (23) and the valve plate (3) a fully open position (P1) in which the valve plate (3) completely opens the shut-off opening (2), a Intermediate position (P2), in which the valve plate (3) does not close the blocking opening (2), although it faces the blocking opening (2), and an absolutely tight position (P3), in which the valve plate (3) blocks the blocking opening (2) hermetically sealed,wherein during the reverse stroke, during which each piston (23) moves from the fully open position (P1) via the intermediate position (P2) to the absolutely tight position (P3), the locking mechanism of each head-side air damping mechanism moves the head-side connecting path (67 ) blocked before the piston (23) reaches the intermediate position (P2), andwhereby, during the forward stroke, in the course of which each piston (23) moves from the absolutely tight position (P3) via the intermediate position (P2) to the fully open position (P1), the locking mechanism of each rod-side air damping mechanism moves the rod-side connecting path ( 78) blocked after the piston (23) has passed the intermediate position (P2).
    [6]
    6. shut-off valve according to claim 5, characterized in that the cover (6) is equipped with an air damper (36) with which the shaft support (9) comes into contact, the shock being cushioned when the valve plate (3) is off the fully open position (P1) has moved into the intermediate position (P2), andthe air damper (36) having a damper chamber (40) formed on the cover (6), a buffer (41) fixedly housed in the damper chamber (40), a damper rod (44) housed in the damper chamber ( 40) is arranged so that it is displaceable, with a proximal end facing the buffer (41) and a distal end protruding from the cover (6), and a damper pressure chamber (46) which is between the damper rod (44) and the Buffer (41) is formed, and that the damper pressure chamber (46) communicates with the rod-side main flow paths (25).
    [7]
    7. shut-off valve according to claim 5, characterized in that each air cylinder with a first locking mechanism for locking the valve plate (3) in the fully open position (P1) and a second locking mechanism for locking the valve plate (3) in the absolutely tight position (P3 ) Is provided.
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    同族专利:
    公开号 | 公开日
    KR20200083232A|2020-07-08|
    JP6938828B2|2021-09-22|
    TW202037833A|2020-10-16|
    CN111379877A|2020-07-07|
    JP2020106127A|2020-07-09|
    DE102019134576A1|2020-07-02|
    US20200208755A1|2020-07-02|
    US11255464B2|2022-02-22|
    引用文献:
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    US3835753A|1972-09-19|1974-09-17|A Bunyard|Air cylinder|
    JPS519157U|1974-07-09|1976-01-23|
    JPS58152907A|1982-03-05|1983-09-10|Ckd Corp|Air cylinder|
    SE463778B|1989-05-24|1991-01-21|Mecman Ab|PISTON AND DEFENSE SEALER FOR A PRESSURE CYLINDER|
    KR0166223B1|1995-03-29|1998-12-01|서상기|Pneumatic cylinder|
    US5975492A|1997-07-14|1999-11-02|Brenes; Arthur|Bellows driver slot valve|
    JP4304365B2|2002-12-16|2009-07-29|Ｓｍｃ株式会社|Gate valve|
    JP5963091B2|2013-07-10|2016-08-03|Smc株式会社|Non-sliding gate valve|
    JP6160924B2|2014-05-08|2017-07-12|Smc株式会社|Gate valve|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    JP2018247496A|JP6938828B2|2018-12-28|2018-12-28|Low noise gate valve|
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