JP3395881B2 - Rodless cylinder cushion device - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulically operated rodless cylinder cushion device. 2. Description of the Related Art Conventionally, a cushioning device for a rodless cylinder is formed by forming a damper insertion hole in a cylinder cap toward a piston, and a stepped rod-shaped rubber damper is formed in the damper insertion hole in the axial direction. When the rod-shaped rubber damper is inserted and receives an axial compressive force near the stroke end of the piston, the rod-shaped rubber damper bends in the axial direction and its thickness expands in the radial direction to stop the piston. As shown in FIG. 5, an air cushion B is provided between a piston and an end cover A, and an inner / outer seal band C attached to the end cover A is further provided.
.Embedded dampers E that contact the piston yoke connecting the piston and the piston mount between D, and fasten the stopper or shock absorber that contacts the outer moving body to the cylinder tube via the mounting bracket Things (Japanese Patent Publication No. 6-74801, etc.) are known. In the above, when the piston moves left or right at a predetermined speed, the piston comes into contact with a rod-shaped rubber damper near its stroke end, and the axial compression force (the piston's compression force) increases. Energy due to thrust and inertial energy due to a work load on the piston mount act on the rod-shaped rubber damper. Then, the projecting portion of the rod-shaped rubber damper from the cylinder cap is compressed in the axial direction. By increasing the protruding length, the piston has a longer braking distance until it stops, and the acceleration applied to the piston decreases. However, since the piston and the piston mount are connected at a distance in the vertical direction by the piston yoke, although the piston thrust can be absorbed, the inertial energy due to the load on the piston mount acting as an offset load with respect to the piston axis is absorbed. There was a problem that the rod-shaped rubber damper could not completely absorb the-, causing a dynamic bending moment in the piston yoke. In the prior art, since a damper is provided between the inner and outer seal bands in addition to the internal air cushion, separate members for damper contact are usually required before and after the piston yoke shorter than the longitudinal length of the piston mount. Although the number of parts and the labor for assembling are large, and the damper is arranged at a position closer to the piston mount, it surely absorbs the inertial energy due to a conveyed object such as a work mounted on the piston mount. Therefore, the distance from the load is still large, and the load still acts as an eccentric load. As a result, there is a problem that the dynamic bending moment acting on the piston yoke cannot be reduced. In the case of using the further stopper, the stroke of the external moving body can be regulated, but an impact sound is generated between the moving body and the outer moving body, which is not preferable. Also, shock absorbers are expensive. Accordingly, an object of the present invention is to provide a dynamic bending moment that occurs in a piston yoke by reliably absorbing thrust by a piston near a stroke end and inertial energy due to a work load on a piston mount. It is another object of the present invention to provide a rodless cylinder cushion device that can be extremely inexpensive and can be implemented inexpensively with less labor for assembling. [0005] The movement of the piston inside the tube is integrated with the piston outside the tube through a longitudinal slit provided in a cylinder tube whose both ends are closed by end members. transmitted to the outer moving body, the slit is in the rodless cylinder of the fluid pressure operated consisting closes in and out sealing band, in the cylinder tube, Sri
A mounting groove for the end member is provided over the entire length in parallel with the
The mounting groove extends from the opening facing outward to the inside.
It has a sharp cross section and a tapping screw is screwed into the mounting groove.
The end member is attached to the end surface of the cylinder tube, an internal rubber damper that contacts the piston is provided between the piston and the end member, and an external rubber damper that contacts the outer moving member is provided between the outer moving member and the end member . The above
A cover part that covers the threaded part of the tapping screw is installed integrally.
I did . Embodiments of the present invention will be described with reference to the drawings. The fluid (air) pressure operated rodless cylinder 1 will be described as an example. 1 to 4, a tube (cylinder tube) 2 formed by extruding or drawing a non-magnetic material (for example, aluminum alloy) has a non-circular (oval) cylinder hole 2a. A slit 3 illustrated as an opening over the entire length in the longitudinal direction.
Is formed. When viewed in cross section, the cylinder tube 2 has, in addition to the cylinder hole 2a and the slit 3, a mounting groove 4 for mounting an end member and a sensor mounting groove 5 in parallel with the cylinder hole 2a on the left and right outer wall surfaces in the width direction. Are formed. The mounting groove 4 has an opening 4a facing outward, extends inward from the opening 4a, and has a shape in which a part of a round hole is cut out. [0010] Both longitudinal ends of the cylinder tube 2 are closed by end caps 10, 11 which are formed as end members and project upward from the upper surface of the tube 2, and a cylinder is provided between the end caps 10, 11. A chamber 6 is formed. Since the end cap 10 and the end cap 11 are the same except that the left and right shapes are symmetrical, the following description will be made with reference to the drawings showing the end cap 10. The end cap 10 (11) and the cylinder tube 2 are fitted with the fitting shaft 12 of the end cap 10 (11) into the end of the piston hole 2a via the cylinder gasket 13, and the slit 3 of the tube 2 is formed. An intermediate wall portion 36 described later is provided at the end.
Tapping screw (for example, as defined in JIS (Japanese Industrial Standards) B-1122) which is fastened by forming a female screw in the pilot hole by screwing in itself with the protrusion 36a of the ) 14 is screwed into the end of the mounting groove 4 for mounting the end member, so that the end cap 1
0 (11) is determined by determining the position in the width direction with respect to the tube 2. With this connection configuration, it is not necessary to form a female screw in advance at the end of the mounting groove 4 for mounting the end member,
Processing man-hours can be reduced. There are three connection points for the end cap 10 (11) in relation to the fluid supply / discharge port 15 formed on the side surface of the end cap 10 (11). The cylinder chamber 6 has piston ends 2 at both ends.
1 is partitioned into front and rear cylinder chambers 6A and 6B by a piston 20 as an inner moving body (an inner member of a moving body described later) having the first cylinder body 1. In the piston 20, a force transmitting member (piston yoke) 22 that penetrates the slit 3 is formed integrally with a piston body 20a at an intermediate portion between the piston ends 21 and 21 provided with the piston packings 21a. The force transmitting member 22 extends right and left outside the tube 2 to form a piston mount 23 as a main body member of the outer moving body. The front and rear walls 23c, 23 of the piston mount 23 have front and rear walls 23a, 23b in the width direction.
A band passing space 24 extending from the front wall 23c to the rear wall 23d through the upper part of the piston yoke 22 and through which an outer seal band 31 to be described later passes is formed of a cover made of a resin material. The outer moving body 26 is closed with the member 25.
Is composed. The piston body 20a, the force transmitting member 22, and the piston mount 23 are a single member entirely made of an aluminum alloy. A scraper 28 is attached to the entire outer periphery of the lower end of the piston mount 23, and a gap between the upper surface of the cylinder tube 2 (the outer surface on the slit opening direction side) and the lower surface of the piston mount 23 is provided. Prevents dust from entering from above. The end cap 10 (11) is lightweight,
Further, it is a molded product of a synthetic resin material such as plastic for cost reduction. In the end cap 10 (11), band fitting holes 32, 33 are formed above and below the intermediate wall portion 36 in correspondence with the inner and outer seal bands 30, 31. The left and right widths of the fitting holes 32 and 33 may be adapted so that the corresponding inner and outer seal bands 30 and 31 can be fitted tightly to position the right and left positions of the respective seal bands 30 and 31. However, in this embodiment, the width is sufficiently larger than the bandwidth. In addition, inner seal band 3
The height of the band fitting hole 32 for the inner seal band 30 is
And has a height sufficiently larger than the thickness of the inner and outer seal bands 30, 31 and communicates with a space S sandwiched between the upper and lower seal bands. Continuing with the band fitting hole 32, the end cap 10
A communication hole 34 communicating with the external space of (11) is provided in the end cap 10 (11). End cap 10
In (11), from the upper side of the upper band insertion hole 33, the intermediate wall portion 36 and the lower band insertion hole 3
2, a pin hole 38 is formed. An inner and outer seal for closing the slit 3 from inside and outside
The band 30, 31 passes above and below the piston yoke 22, and its ends reach the respective end caps 10 (11). The inner and outer seal bands 30, 31 are thin flexible bands and are made of a magnetic material such as a steel band. The inner and outer seal bands 30, 31 have the width of the slit 3, as is well known. Seal band 30
At the longitudinal ends, mounting holes are formed at positions corresponding to the respective pin holes 38 of the end cap 10 (11). At the longitudinal ends of the seal band 31, the end cap 1 is provided.
A mounting hole is formed at a position corresponding to each pin hole 38 of 0 (11). Each of the seal bands 30, 31 is fitted with its both ends into the corresponding band fitting holes 32, 33,
Mounting holes for seal bands 30, 31 and end cap 1
With the pin hole 38 of 0 (11) aligned, the mounting pin 39 is fitted into the pin hole 38 from the outside and connected to the end cap 10 (11). Further, the cover 56 for retaining the mounting pin 39 is attached to the end cap 10 (11).
Removably fit into It is preferable that the fitting state of the pin hole 38 and the mounting pin 39 is such a fitting state that the pin hole 38 can be pushed in with a finger and pulled out with a finger. The mounting pins 39 are parallel to each other at both end caps 10 (11), and are attached to the end caps 10 (11).
Since the upper and lower portions and the intermediate portion are supported, the mounting pins 3
9 is fitted into the end cap 10 (11)
Since the bands 30 and 31 can be attached to the end cap 10 (11) without using screws or the like, the labor for assembling is greatly reduced. Magnets 45 for attracting the inner and outer seal bands 30 and 31 are arranged along the longitudinal direction on both sides of the slit 3 on the outer surface of the tube 2. Except for the portion passing through the piston yoke 22, the inner seal band 30 closes the slit 3 from the inside by the magnetic attraction force and the fluid pressure applied to the cylinder chamber 6, and the outer seal band 31 The slit 3 is closed from the outside by the magnetic attraction force. Tube 2 of end cap 10 (11)
An inner rubber damper 70 that abuts on the end of the piston 20 at the piston stroke end at the tip of the shaft portion 12 that fits
Is provided. The cylinder rubber gasket holding groove 16 for holding the cylinder gasket 13 between the fitting shaft portion 12 and the internal rubber damper 70 is formed by fixing the internal rubber damper 70 to the tip of the fitting shaft portion 12 by bonding or the like. Fluid from the supply / discharge port 15 provided on the side surface of the end cap 10 (11) is supplied through a supply / discharge hole 71 of the end cap 10 (11) and a supply / discharge hole 72 provided at the center of the internal rubber damper 70.
It is supplied and discharged to and from the corresponding cylinder chamber 6, whereby the piston 20, that is, the outer moving body 26 moves left and right. The internal rubber damper 70 is provided with a damper insertion hole 70b in a front end face 70a facing the piston 20. From the damper insertion hole 70b, a bar-like projection 70c is formed on the left and right with a pair of pistons 2
It protrudes in the 0 direction. The diameter of the damper insertion hole 70b is larger than the diameter of the rod-shaped protrusion 70c, and the size thereof is
0c receives a predetermined axial compressive force, the protrusion 70c
Is bent in the axial direction, and the protrusion 70c fits into the damper insertion hole 70b when the thickness thereof is expanded in the radial direction. The internal rubber damper 70 makes the protrusion 70c easily bend in the axial direction. Particularly, nitrile rubber, which is a material having relatively low resilience, is preferable. On the inner side in the axial direction corresponding to the outer moving body 26 (piston mount 23) of the end cap 10 (11), the outer moving body 2 is provided at the stroke end of the outer moving body 26.
6 against the front wall 23c (rear wall 23d).
6 and an external rubber damper 80 for absorbing inertia energy due to a work load thereon. The front end face 80a of the external rubber damper 80 is provided with a plurality of grooves 80b in the vertical direction with respect to the axial direction in order to bend easily in the axial direction. 80c is the concave portion 8 of the end cap 10 (11).
0d. The lower end of the external rubber damper 80 in the width direction is formed in an extended portion 81 extending inward in the axial direction, and a fitting portion 82 is provided at the tip of the extended portion 81.
In the state of contact with (11), the mounting groove 4 on the outer surface of the tube 2
When the fitting portions 82 are fitted into the fittings 82, the fitting portions 82 are located just axially inward of the tip end of the tapping screw 14, and the upper two pieces respectively fix the end cap 10 (11) to the end of the tube 2. The tapping screw 14 is covered so that it cannot be seen from the outside. As described above, the external rubber damper 80 fits the convex portion 80c on the back surface into the concave portion 80d of the end cap 10 (11), and the fitting portion 82
Is fitted in the mounting groove 4 and is mounted on the end cap 10 (11) outside the tube, so that mounting and dismounting are extremely simple. When a load caused by a work or other conveyed object is applied to the piston mount 23 and the piston 20 moves leftward or rightward at a predetermined speed, the piston 20 firstly contacts the internal rubber damper 70 near its stroke end. At the beginning, the axial thrust by the piston 20 and the inertial energy due to the load start to act on the internal rubber damper 70.
Then, the rod-shaped projection 70c expands in a direction (radial direction) perpendicular to the axial direction while being compressed in the axial direction. Projection 70c
Is formed in a rod shape, the ratio of the length to the area receiving the load increases, and the bending in the axial direction increases. The widening displacement generated by this bending is easily deformed until the projection 70c is pressed against the damper insertion hole 70b because there is a radial gap between the projection 70c and the damper insertion hole 70b. Since the large axial deflection results in a long cushion stroke, the piston 20 has a longer braking distance before stopping, and as a result, the acceleration applied to the piston 20 decreases, and the piston 20 tries to stop smoothly. . When the expansion of the projection 70c is restricted by the damper insertion hole 70b, the axial bending of the projection 70c is also restricted, and the bending of the projection 70c causes the piston 20 to absorb the energy while the front end of the internal rubber damper 70 is being absorbed. It comes into contact with the surface 70a. Around the time when the piston 20 makes contact with the front end surface 70a of the internal rubber damper 70, the outer moving body 26 starts to make contact with the external rubber damper 80,
0, remaining energy for stopping the external moving body 26
Absorb. At this time, the front wall 23c of the outer moving body 26 (piston mount 23) comes into contact with the external rubber damper 80 provided at substantially the same height as the front wall 23c. As a result of applying the inertial energy due to the load at a position closer to the load of
The degree to which the load acts as an eccentric load can be extremely small, the dynamic bending moment applied to the piston yoke 22 can be reduced, and the impact sound with the piston mount 20 can be extremely small. In this embodiment, the projection 70c is provided on the internal rubber damper 70, and the piston 2 is first attached to the internal rubber damper 70.
0, and then the piston mount 23 is made to act on the external rubber damper 80. However, a projection is provided on the external rubber damper 80 to act on the piston mount 23 first, and then the piston acts on the internal rubber damper. You may do so. Further, the piston and the piston mount may simultaneously act on the inner and outer rubber dampers. As described above, according to the present invention, the inertial energy due to the thrust of the piston, the outer moving body and the load attached thereto is applied to the inner and outer rubber dampers, and the outer rubber damper is connected to the outer rubber damper. Since it is provided so as to be in contact with the moving body, as a result of applying inertial energy due to the load at a position closer to the load of the external moving body, the degree of the load acting as an eccentric load can be extremely reduced, and a dynamic bending moment is applied to the piston yoke. Can be reduced. Further, since the inner and outer rubber dampers are used, the cost is lower than when an absorber is provided outside. In addition, since an external rubber damper is provided on the outside of the tube, it can be easily attached and detached, and can absorb an impact sound during braking. Further, according to the external rubber damper of the present invention, by attaching the external rubber damper to the cylinder tube, the covering portion allows the tapping screw used for coupling the end member and the cylinder tube to be exposed, thereby improving the external shape. it can.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view of a rodless cylinder embodying the present invention. FIG. 2 is a plan view of FIG. FIG. 3 is a sectional view taken along line III-III of FIG. 2; FIG. 4 is a reference perspective view of a rodless cylinder. FIG. 5 is a diagram showing a conventional rodless cylinder cushion device. DESCRIPTION OF SYMBOLS 1 Rodless cylinder 2 Tube 3 Slit 4 Mounting groove 4 a for mounting end member 4 Opening 10 End cap 11 End cap 12 Fitting shaft 13 Cylinder gasket 14 Tapping screw 16 Cylinder gasket holding groove 20 Piston 26 Outer moving body 30 Outer seal band 31 Inner seal band 70 Inner rubber damper 70b Damper insertion hole 70c Projection 80 External rubber damper 82 fitting portion

Claims (1)

(57) [Claims 1] The movement of the piston inside the tube and the piston outside the tube via a longitudinal slit provided in a cylinder tube whose both ends are closed by end members. The fluid is transmitted to an integral outer moving body, and the slit is closed by an inner and outer seal band. In a fluid pressure operated rodless cylinder, an end member is provided in the cylinder tube in parallel with the slit.
A mounting groove for mounting is provided over the entire length, and the mounting groove is provided.
Has a cross-sectional shape with the inside expanding from the opening facing the outside.
And screw a tapping screw into the mounting groove to
Attaching the end members to over blanking end face, between the piston and the end member is provided an internal rubber damper piston and abutment, the external rubber damper which abuts the outer moving body provided between the outer mobile and the end member, the outer rubber damper Is the screw of the tapping screw.
A cushioning device for a rodless cylinder, wherein a covering portion for covering a fitting portion is provided integrally .