JPH0716005U - Brake device for cable cylinder - Google Patents

Abstract

(57) [Summary] [Object] With respect to a cable cylinder braking device, it is an object to provide a cable cylinder braking device that is small in size and has a strong braking action. [Structure] Inner metals 22 and 23 to be slidably contacted with both side surfaces 14 and 15 of a dovetail-shaped guide groove 13 formed above the cylinder chamber 1 of the cylinder block 2 are supported by a base portion 21 of a slider 18 to form a guide groove. A wedge-shaped outer metal 29, 30 is inserted between the head portion 26 of the slider 18 protruding above 13 and the upper surfaces 16, 17 of both side walls of the guide groove 13 so as to be movable back and forth in the width direction of the guide groove 13. The outer metal 29/30 is moved back and forth by the brake cylinder 36 and the release springs 44 to 47.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a cable cylinder braking device, and more particularly to a cable cylinder braking device that is small in size and has a strong braking action.

[0002]

[Prior art]

 For example, as shown in FIG. 2, the cable cylinder is constructed by assembling end blocks 3 and 4 at both ends of a cylinder block 2 having a cylinder chamber 1 and closing both ends of the cylinder chamber 1 to form a piston 5 in the cylinder chamber 1. Is inserted oil-tightly and slidably in the axial direction of the cylinder chamber 1 (hereinafter, simply referred to as the axial direction).

The piston 5 is provided with respective halves 5a and 5b which are divided into two in the axial direction, and a center bolt 5c which is inserted into both halves 5a and 5b and has threads formed at both ends. It is integrated by screwing a pair of cable holders 6 and 7 at both ends of 5c. Both cable holders 6 and 7 hold one ends of cables 8 and 9, respectively, and wind the cables 8 and 9 around pulleys 10 and 11 that are rotatably supported by the end blocks 3 and 4 outside the cylinder chamber 1. By being hung, the cylinder chamber 1 is turned upside down.

A dovetail-shaped guide groove 13 independent of the cylinder chamber 1 is provided on the upper end surface 12 of the cylinder block 2. Both side surfaces 14 of the guide groove 13 and upper surfaces 16 on both outer sides of the guide groove 13 are provided. Is the guide surface of the slider 18. In this conventional cylinder, when a brake device is provided to stop the slider 18 at an arbitrary position, a brake shoe is supported by the slider 18 so as to be able to move forward and backward toward the upper surface 16 of the cylinder block 2. A brake cylinder that presses the shoes against the upper surfaces 16 and 17 of the cylinder block 2 and a release spring that biases the brake shoes against the upper surfaces 16 and 17 of the cylinder block 2 against the brake cylinder are provided. .

[0005]

[Problems to be solved by the device]

 In order to stop the moving slide 18 at an arbitrary position with this conventional brake device, it is necessary to set the output of the brake cylinder to several times or more the cylinder output for moving the slide 18, which makes the brake device large. There is a problem that becomes. In particular, when the cylinder block 2 is made of an extruded aluminum material, a hard brake shoe cannot be used, and the friction coefficient of the brake shoe becomes low. Therefore, it is necessary to further increase the output of the brake cylinder. Yes, the brake system becomes even larger.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a cable cylinder brake device that is small in size and capable of obtaining a strong brake operation.

[0007]

[Means for Solving the Problems]

 In order to achieve the above object, the present invention forms a dovetail-shaped or T-shaped groove-shaped guide groove above a cylinder chamber in a cylinder block having a cylinder chamber, and inserts the guide groove in the guide groove. While the metal supported by the base of the slider is slidably contacted with both side surfaces or the downward surface of the guide groove, the head portion of the slider is projected above the guide groove, and both side portions of the head portion are connected with the guide groove. A pair of wedge-shaped outer metal pieces, which protrude over both sidewalls and become thicker on both the left and right outer sides between both sides of the head section and the upper surfaces of both side walls of the guide groove, move forward and backward in the width direction of the guide groove. A brake cylinder that can be inserted as much as possible to pull the outer metals toward each other in the width direction of the guide groove, and a release spring that urges the outer metals in a direction separating from each other against the brake cylinder are provided. To.

[0008]

In the present invention, when the brake device is in the released state, the outer metal is urged in the direction in which the outer metal is separated from each other by the release spring, and the slider is, so to speak, floatingly supported by the cylinder block. When the brake device is actuated and the outer cylinders are pulled closer to each other by the brake cylinder, the wedge effect of the outer metal pushes the outer metal against the upper surfaces of both side walls of the guide groove and pushes the slider upward, The metal is pressed against both sides or the downward side of the groove.

As a result, a frictional force is generated between the outer metal and the upper surfaces of both side walls of the guide groove, and a frictional force is also generated between the inner metal and both side surfaces or the downward surface of the guide groove. The force can be distributed to two outer metals and two inner metals. Therefore, a large braking force can be obtained even if the surface pressure at which the outer metal and the inner metal are pressed against the upper surfaces of both side walls of the guide groove and both side surfaces of the guide groove or the downward surface is small, and it is necessary for a small brake cylinder with a small output. A great braking force can be obtained.

[0010]

【Example】

 Hereinafter, a slider guide device for a cable cylinder to which an embodiment of the present invention is applied will be described in detail with reference to FIGS. In this cable cylinder, as shown in the side view of FIG. 2, end blocks 3 and 4 are attached to both ends of a cylinder block 2 having a cylinder chamber 1, and both ends of the cylinder chamber 1 are closed. The piston 5 is inserted in an oil-tight manner and slidably in the axial direction of the cylinder chamber 1 (hereinafter, simply referred to as the axial direction).

The piston 5 is provided with halves 5a and 5b which are divided into two in the axial direction, and a center bolt 5c which is inserted into both halves 5a and 5b and has a screw formed at both ends. It is integrated by screwing a pair of cable holders 6 and 7 at both ends of 5c. Both cable holders 6 and 7 hold one ends of cables 8 and 9, respectively, and wind the cables 8 and 9 around pulleys 10 and 11 that are rotatably supported by the end blocks 3 and 4 outside the cylinder chamber 1. By being hung, the cylinder chamber 1 is turned upside down.

As shown in the sectional view of FIG. 1, a dovetail-shaped guide groove 13 independent of the cylinder chamber 1 is provided in the upper end surface 12 of the cylinder block 2, and both side surfaces of the guide groove 13 are formed. Upper surfaces 16 and 17 on both outer sides of 14 and 15 and the guide groove 13 serve as guide surfaces of the slider 18. The edge portions 19 and 20 of the guide groove 13 are made to project inwardly on both side surfaces 14 and 15 so that foreign matter such as dust is unlikely to enter the guide groove 13.

The base 21 of the slider 18 holds inner metals 22 and 23 that are in surface contact with the side surfaces 14 and 15 of the guide groove 13. The base portion 21 of the slider 18 may be configured to fixedly support the inner metals 22 and 23, but in this embodiment, the inner metal portions 22 and 23 are mounted on the base portion 21 of the slider 18 in the axial direction of the slider 18. It is rotatably held around an axis parallel to the inner metal 22 and 23, and the inner metal 22 and 23 naturally slide along the side surfaces 14 and 15 of the guide groove 13 to cause uneven wear of the inner metal 22 and 23. To prevent that.

As a method of holding the inner metals 22 and 23 on the base 21 of the slider 18 so as to be rotatable about an axis parallel to the axial direction of the slider 18, the inner metals 22 and 23 are attached to the base 21 via an axis. However, in this embodiment, in order to simplify the structure and reduce the number of parts, the inner metal members 22 and 23 are formed into a lunar cross section, and The peripheral surfaces of the partial cylinders 23 are received by the grooves 24 and 25 formed on both side surfaces of the base 21 so as to be slidable in the circumferential direction.

The concave grooves 24 and 25 formed on both side surfaces of the base portion 21 may be formed in a V shape, but in this embodiment, the concave grooves 24 and 25 are formed on the partial cylindrical peripheral surface of the inner metal 22 and 23. Is formed on the peripheral surface of the cylinder to distribute the surface pressure acting between the inner metal 22/23 and the groove 24/25 over as wide an area as possible, The 25 is designed to be hard to wear.

The head portion 26 of the slider 18 is formed so as to cover the upper surface of the cylinder block 2, and the lower surfaces 27 and 28 on both sides thereof may be formed horizontally, but they are directed toward the center of the cylinder block 2. It is formed on an inclined surface that descends and inclines along with. Between the lower surfaces 27 and 28 on both sides of the head portion 26 and the upper surfaces 16 and 17 on both sides of the cylinder block 2, wedge-shaped outer metal 29 that becomes thinner toward the center of the cylinder block 2 respectively.・ 30 is inserted.

Grooves 31 and 32 are formed on the upper surfaces of the outer portions of the outer metals 29 and 30, respectively, and the balancer 31 and 32 has a balancer disposed on the head portion 26 so as to face both outer surfaces thereof. The lower edges of the plates 33 and 34 are inserted. As shown in the plan views of FIGS. 1 and 3, a hexagonal shaft 35 can move forward and backward in a direction perpendicular to the axial direction of the slider 18 (hereinafter referred to as the width direction) at the central portion of the slider 18 in the axial direction. Adjustment screw 37, which is inserted into the center of the balancer plate 34 in the axial direction, is screwed into one end of the hexagonal shaft 35, and the piston rod of the brake cylinder 36 is attached to the other end of the hexagonal shaft 35. 36c is screwed.

The cylinder body 36a of the brake cylinder 36 is received by the other balancer plate 33 so as not to rotate around its axis through the pin 36e, and the slider 18 of the piston 36b in the cylinder body 36a. When a working fluid such as pressure oil or compressed air is supplied to the pressure receiving chamber 36d defined on the side, the piston 36b and the piston rod 63b are driven to the side opposite to the slider 18, and the balancer plates 33 and 34 are interposed. The outer metal 29 and 30 are pulled toward each other.

The hexagonal shaft 35 needs to be held non-rotatably by the slider 18 around its axis so that the adjusting screw 37 can be screwed back and forth with respect to the hexagonal shaft 35 by a rotating operation. For this purpose, there is also a method of forming a hexagonal hole corresponding to the hexagonal shaft 35 in the slider 18, but in order to reduce the cost by simplifying the shape of the hole through which the hexagonal shaft 35 is inserted, in this embodiment, As shown in the sectional view of FIG. 4, a circular hole 38 in which the hexagonal shaft 35 is inscribed is formed in the slider 18, and a locking screw 39 screwed from the upper surface of the slider 18 is tightened on the outer peripheral surface of the hexagonal shaft 35. Rotation around the axis of the hexagonal shaft 35 is prevented.

As shown in FIG. 3, spring holding holes 40 to 43 are recessed in both sides of the slider 18 in the axial direction in symmetrical positions with respect to the axial centers of the brake cylinder 36, the adjusting screw 37 and the hexagonal shaft 35, respectively. The respective balancer plates 33 and 34 are urged in the direction in which they are separated from each other by the uniform release springs 44 to 47 inserted into the spring holding holes 40 to 43, respectively. Therefore, if the adjusting screw 37 is rotated in the tightening direction, the balancer plates 33, 34 on both sides and the outer metal 29, 30 move in parallel in a direction in which they approach each other equally, and the adjusting screw 37 is loosened in both directions. The balancer plates 33 and 34 and the outer metals 29 and 30 move in parallel in the direction in which they are evenly spaced from each other, so that the slider 18 is floatingly supported by the cylinder block 2 via the release springs 44 to 47. Will be.

When the outer metals 29, 30 approach each other, the wedge action pushes the outer metals 29, 30 against the upper surfaces 16, 17 of both side walls of the guide groove 13, and the slider 18 is pushed upward, Metals 22 and 23 are pressed against both side surfaces 14 and 15 of the guide groove 13. As a result, a frictional force is generated between the outer metal 29/30 and the upper surfaces 16/17 of both side walls of the guide groove 13, and friction is also generated between the inner metal 22/23 and both side surfaces 14/15 of the guide groove 13. The force is generated and the braking force can be distributed to the two outer metals 29 and 30 and the two inner metals 22 and 23.

Therefore, the outer metal 29, 30 and the inner metal 22, 23 are pressed against the upper surfaces 16, 17 of both side walls of the guide groove 13 and the both side surfaces 14, 15 of the guide groove 13 even if the surface pressure is small, a large braking force is exerted. Therefore, the required braking force can be obtained with the small brake cylinder 36 having a small output. In the above-described embodiment, the lower surfaces 27 and 28 on both side portions of the head portion 26 are inclined surfaces, but it is possible to make them horizontal surfaces. However, by forming the lower surfaces 27 and 28 of both sides of the head portion 26 into inclined surfaces that follow the outer metal 29 and 30, the contact area between the outer metal 29 and 30 and the lower surface 27 and 28 of the head portion 26 is wide. This is advantageous because uneven wear of the outer metal 29/30 can be prevented.

In addition, the upper surfaces 16 and 17 of the cylinder block 2 may be formed as inclined surfaces that gradually descend toward both outer sides. In this case, the lower surface of the outer metal 29 and 30 is the upper surface 16 and the upper surface of the cylinder block 2. It is preferable to form an inclined surface following the shape of 17. Further, in the above-described one embodiment, the brake action is exerted when the brake cylinder 36 receives the supply of the working fluid. For example, as shown in the sectional view of FIG. The springs 48c and 48d for urging the piston 48b in the braking direction are provided in the 48a, and the piston 48b and the piston rod 48e are opposed to each other when a working fluid whose supply pressure exceeds a certain value is supplied against the springs 48c and 48d. It may be configured to be driven in the brake release direction.

In this case, when the supply pressure of the working fluid is reduced to a certain pressure or lower for some reason, the brake is activated, so that the safety can be improved. In addition, although the guide groove 13 is formed in a dovetail groove shape in the above-described embodiment, the guide groove 13 may be a T-shaped groove. In this case, by receiving the inner metal on the downward surface of the guide groove, the same effect as that of the above-described embodiment can be obtained.

[0025]

[Effect of device]

 As described above, in the brake device for a cylinder of the present invention, the outer metal and the inner metal interposed between the slider and the cylinder block are also used as the brake shoe, so the number of parts is small and the cost is reduced. Can be achieved. Further, since the braking force is distributed to the outer metal and the inner metal, a strong braking force can be obtained with a small brake cylinder, and a separate brake shoe is not required, so that the brake device can be downsized.

In the present invention, in particular, the brake cylinder is composed of a single cylinder including a tubular body connected to one outer metal of both outer metals and a piston connected to the other outer metal. In this case, the number of parts can be minimized and the configuration can be the simplest, which is most advantageous in terms of downsizing and cost reduction.

Further, in the present invention, particularly when the release spring is arranged in a symmetrical position around the tightening step in the slider sliding direction, the slider is stably floated on the cylinder block via the release spring. It can be supported in a stable manner, and the movement path of the slider can be stabilized with high accuracy.

[Brief description of drawings]

FIG. 1 is a sectional view of a cable cylinder to which an embodiment of the present invention is applied.

FIG. 2 is a side view of a cable cylinder to which an embodiment of the present invention is applied.

FIG. 3 is a plan view of a main part of a cable cylinder to which an embodiment of the present invention is applied.

FIG. 4 is a sectional view of an essential part of a cable cylinder to which an embodiment of the present invention is applied.

FIG. 5 is a sectional view of a brake cylinder used in another embodiment of the present invention.

[Explanation of symbols]

 1 ... Cylinder chamber 2 ... Cylinder block 16/17 ... Top surface 13 ... Guide groove 14/15 ... Side surface 18 ... Slider 21 ... Base 22/23 ... Inner metal 26 ... Head part 29/30 ... Outer metal 35 ... Shaft 36 ... Brake Cylinder 36a ... Cylinder 36b ... Pistons 44 to 47 ... Release spring

Claims (3)

[Scope of utility model registration request] 1. A cylinder block having a cylinder chamber is provided with a dovetail-shaped or T-shaped groove-shaped guide groove which is independent of the cylinder chamber above the cylinder chamber, and is supported by a base portion of a slider inserted into the guide groove. While sliding the metal into sliding contact with both sides or the downward surface of the guide groove, the head part of the slider is projected above the guide groove, and both sides of this head part are projected above both side walls of the guide groove. , A pair of wedge-shaped outer metals, which become thicker on both the left and right outer sides, are inserted between both sides of the head portion and the upper surfaces of both side walls of the guide groove so as to be able to advance and retreat in the width direction of the guide groove. A brake cylinder for a cable cylinder, comprising: a brake cylinder that pulls the guide metal toward each other in the width direction of the guide groove; Ki device. 2. The brake cylinder is composed of a single cylinder including a cylindrical body connected to one outer metal of both outer metals and a piston connected to the other outer metal. The brake device for a cable cylinder according to claim 1, which is characterized in that. 3. The cable cylinder brake device according to claim 3, wherein the release springs are arranged symmetrically with respect to the brake cylinder in the sliding direction of the slider.