Fluid pressure cylinder

Abstract

To achieve reduction of stress concentration and reduction of waste of materials in a fluid pressure cylinder.SOLUTION: A hydraulic cylinder 100 includes a cylinder tube 10. The cylinder tube 10 has a body part 12, an annular connection part 13 in which the cylinder head 40 is connected to an end surface 11, and a welding part 14 formed between the body part 12 and the connection part 13. An outer peripheral surface of the connection part 13 has: a first curved surface 13b formed so that it has a larger diameter as it goes away from the welding part 14; a second curved surface 13c formed nearer on the end surface 11 side than the first curved surface 13b so that it has a larger diameter as it nears the end surface 11; a shoulder surface 13e which is formed in succession to the end part on the end surface 11 side on the second curved surface 13c and extends outward in a radial direction; a large diameter part 13f formed in succession to the end surface 11; and an inclined surface 13g formed between the large diameter part 13f and the shoulder surface 13e. The first curved surface 13b is larger in a curvature radius than the second curved surface 13c.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present invention relates to a fluid pressure cylinder. [Background technology]

[0002] Patent Document 1 discloses a cylinder device including a cylinder with an opening at one end, a cylinder head attached so as to close the opening of the cylinder and fixed with a number of bolts, a piston rod that passes through the cylinder head and is arranged slidably inside the cylinder, and a piston attached to the piston rod. The cylinder has a cylindrical main body and a connecting part to which the cylinder head is connected. A bolt for fixing the cylinder head is fastened to the connecting part, and the connecting part has a radial thickness greater than that of the main body. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Publication No. 3-249415 Summary of the Invention [Problem to be solved by the invention]

[0004] In a cylinder device such as that described in Patent Document 1, a welded portion is formed between a main body portion and a connecting portion. Since stress concentration is likely to occur in the welded portion, it is conceivable to provide a curved portion at the connecting portion to reduce the stress concentration occurring at the welded portion. In this case, if the radius of curvature of the curved portion is increased, the stress concentration is further reduced. However, if the radius of curvature of the curved portion is increased, the area where the curved portion is formed (specifically, the axial length where the curved portion is formed) becomes larger, and the area of ​​the cylinder where the curved portion is machined becomes larger, resulting in more wasted cylinder material. In this way, it is difficult to achieve both reduction in stress concentration and reduction in material waste.

[0005] The present invention has been made in consideration of the above problems, and has an object to achieve both a reduction in stress concentration and a reduction in material waste in a fluid pressure cylinder. [Means for solving the problem]

[0006] The present invention is a fluid pressure cylinder comprising: a cylinder tube, a piston rod provided reciprocably within the cylinder tube, a piston connected to the piston rod and slidably housed within the cylinder tube, and a cylinder head connected to the cylinder tube and supporting the piston rod slidably, the cylinder tube having a cylindrical main body, a ring-shaped connecting portion whose end surface is connected to the cylinder head, and a welded portion formed between the main body and the connecting portion, the outer circumferential surface of the connecting portion having a first curved surface formed so as to have a larger diameter as it moves away from the welded portion, a second curved surface formed on the end face side than the first curved surface and formed so as to have a larger diameter as it approaches the end face, a shoulder surface formed continuously with an end portion of the second curved surface on the end face side and extending radially outward, a large diameter portion formed continuously with the end face, and an inclined surface formed between the large diameter portion and the shoulder surface, the first curved surface having a larger radius of curvature than the second curved surface.

[0007] In this invention, although stress concentration is likely to occur at the welded portion, the welded portion and the first curved surface are adjacent to each other, so that the stress concentration at the welded portion is reduced. In addition, the second curved surface away from the welded portion has a smaller radius of curvature than the first curved surface, and the second curved surface and the large diameter portion are connected via a shoulder surface and an inclined surface, so that the axial length of the connecting portion can be shortened while ensuring the strength of the cylinder tube. Therefore, it is possible to achieve both reduction in stress concentration and reduction in material waste.

[0008] In the present invention, the outer circumferential surface of the connecting portion further has a tapered surface formed between the first curved surface and the second curved surface.

[0009] In the present invention, the shoulder surface extends perpendicular to the axial direction of the cylinder tube.

[0010] In this invention, the axial length of the connecting portion can be made shorter, and the amount of material removed during machining of the cylinder tube can be made smaller. Effect of the Invention

[0011] According to the present invention, it is possible to reduce both stress concentration and material waste in a fluid pressure cylinder. [Brief description of the drawings]

[0012] [Figure 1] 1 is a partial cross-sectional view of a fluid pressure cylinder according to an embodiment of the present invention. [Diagram 2] FIG. 2 is an enlarged cross-sectional view of a portion A shown in FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0013] A fluid pressure cylinder according to an embodiment of the present invention will be described with reference to the drawings. In the following, a case will be described in which the fluid pressure cylinder is a hydraulic cylinder 100 that uses hydraulic oil as a working fluid.

[0014] First, the overall configuration of a hydraulic cylinder 100 will be described with reference to FIG.

[0015] As shown in FIG. 1, a hydraulic cylinder 100 includes a cylinder tube 10, a piston rod 20 reciprocally provided within the cylinder tube 10, a piston 30 connected to the piston rod 20 and slidably housed within the cylinder tube 10, and a cylinder head 40 connected to the cylinder tube 10 and supporting the piston rod 20 so as to be slidable.

[0016] The cylinder tube 10 is formed in a cylindrical shape. The inside of the cylinder tube 10 is divided into a rod side chamber 2 and an anti-rod side chamber 3 by the piston 30. The rod side chamber 2 and the anti-rod side chamber 3 communicate with a hydraulic pump (not shown) or a tank (not shown) as a hydraulic supply source through a switching valve (not shown). When one of the rod side chamber 2 and the anti-rod side chamber 3 communicates with the hydraulic pump, the other communicates with the tank. The hydraulic cylinder 100 expands and contracts when hydraulic oil (working fluid) is introduced from the hydraulic pump to the rod side chamber 2 or the anti-rod side chamber 3 and the piston rod 20 moves in the axial direction. Note that a working fluid such as a water-soluble substitute liquid may be used instead of the hydraulic oil. Hereinafter, the axial direction of the cylinder tube 10 will also be simply referred to as the "axial direction" and the radial direction of the cylinder tube 10 will also be simply referred to as the "radial direction".

[0017] One opening of the cylinder tube 10 (left side in FIG. 1) is closed by a cylinder head 40, and the other opening (right side in FIG. 1) is closed by a cylinder bottom (not shown). The piston rod 20 is inserted through the cylinder head 40 and slidably supported by the cylinder head 40. The cylinder head 40 has an annular flange portion 41 and an annular fitting portion 42 that fits into the inner peripheral surface of the cylinder tube 10. The flange portion 41 is fastened to the end surface 11 of the cylinder tube 10 via a plurality of fastening members 50 such as bolts. The flange portion 41 is formed with a supply / discharge port 45 that extends in the radial direction and is connected to a hydraulic pipe (not shown). An annular passage 46 that connects the supply / discharge port 45 and the rod side chamber 2 is formed between the outer peripheral surface of the piston rod 20 and the inner peripheral surface of the fitting portion 42. Hydraulic oil is supplied and discharged to the rod side chamber 2 through the supply / discharge port 45 and the annular passage 46.

[0018] The piston rod 20 has a small diameter portion 21 formed at the tip end thereof and to which the piston 30 is fastened, a large diameter portion 22 that slides against the inner circumferential surface of the cylinder head 40 and is formed with a diameter larger than the small diameter portion 21, and a medium diameter portion 23 that is formed between the small diameter portion 21 and the large diameter portion 22 and is provided with an annular cushion ring 81 described later. The cushion ring 81 is sandwiched between the piston 30 and the large diameter portion 22.

[0019] The piston 30 is formed in an annular shape and is provided on the outer periphery of the small diameter portion 21 of the piston rod 20. A seal member 31 is provided on the outer periphery of the piston 30. This blocks communication between the rod side chamber 2 and the anti-rod side chamber 3 through the gap between the inner periphery of the cylinder tube 10 and the outer periphery of the piston 30.

[0020] When the rod side chamber 2 is connected to the hydraulic pump and the anti-rod side chamber 3 is connected to the tank, hydraulic oil is supplied to the rod side chamber 2 through the supply / discharge port 45, and hydraulic oil in the anti-rod side chamber 3 is discharged to the tank. As a result, the piston rod 20 moves to the right in FIG. 1 and the hydraulic cylinder 100 contracts.

[0021] On the other hand, when the hydraulic pump is connected to the anti-rod side chamber 3 and the rod side chamber 2 is connected to the tank, hydraulic oil is supplied to the anti-rod side chamber 3 and the hydraulic oil in the rod side chamber 2 is discharged to the tank through the supply / discharge port 45. As a result, the piston rod 20 moves to the left in FIG. 1 and the hydraulic cylinder 100 extends.

[0022] The hydraulic cylinder 100 further includes a cushion ring 81 for decelerating the piston rod 20 near the stroke end when the hydraulic oil in the rod side chamber 2 is discharged and the piston rod 20 strokes. The cushion ring 81 is provided on the outer periphery of the medium diameter portion 23 of the piston rod 20, and has an inner diameter larger than that of the medium diameter portion 23 and smaller than that of the inner periphery of the fitting portion 42 of the cylinder head 40. A flow path 82 is formed between the outer periphery of the medium diameter portion 23 and the inner periphery of the cushion ring 81. The cushion ring 81 is formed so that the outer diameter is smaller on the tip side (left side in FIG. 1), and a groove 81a is formed on the base end side (right side in FIG. 1). The cushion ring 81 enters the annular passage 46 near the stroke end.

[0023] As shown in FIG. 1, when the hydraulic cylinder 100 is extended and the piston rod 20 is in a normal stroke range (not at the stroke end), the hydraulic oil in the rod side chamber 2 is guided to the supply / discharge port 45 through the annular passage 46 and discharged. On the other hand, when the hydraulic cylinder 100 is extended and the piston rod 20 is near the stroke end, the cushion ring 81, which has a diameter larger than the large diameter portion 22, enters the annular passage 46. Therefore, the hydraulic oil in the rod side chamber 2 is guided to the supply / discharge port 45 through the groove 81a of the cushion ring 81 and the flow passage 82 and discharged. Since the flow passage 82 has a smaller flow passage cross-sectional area than the annular passage 46, the pressure in the rod side chamber 2 increases, and the piston rod 20 decelerates. In this way, the cushion ring 81 produces a cushioning effect.

[0024] Next, the cylinder tube 10 will be described in detail.

[0025] The cylinder tube 10 has a cylindrical main body portion 12, an annular connecting portion 13 whose end face 11 is connected to a cylinder head 40, and a welded portion 14 formed between the main body portion 12 and the connecting portion 13. The cylinder tube 10 has a uniform inner diameter over the main body portion 12, the welded portion 14, and the connecting portion 13.

[0026] The main body 12 is formed to have a uniform outer diameter. The welded portion 14 is formed by welding, and is formed at the boundary between the main body 12 and the connecting portion 13. The welded portion 14 is formed by protruding radially from the outer circumferential surfaces of the main body 12 and the connecting portion 13.

[0027] 2, the outer peripheral surface of the connecting portion 13 has a flat surface 13a formed continuously with the welded portion 14, a first curved surface 13b formed continuously with the flat surface 13a, a second curved surface 13c formed closer to the end surface 11 than the first curved surface 13b, a tapered surface 13d formed between the first curved surface 13b and the second curved surface 13c, a shoulder surface 13e formed continuously with the end portion of the second curved surface 13c on the end surface 11 side and extending radially outward, a large diameter portion 13f formed continuously with the end surface 11, and an inclined surface 13g formed between the large diameter portion 13f and the shoulder surface 13e. In this way, the outer peripheral surface of the connecting portion 13 has the flat surface 13a, the first curved surface 13b, the tapered surface 13d, the second curved surface 13c, the shoulder surface 13e, the inclined surface 13g, and the large diameter portion 13f formed continuously in this order from the welded portion 14 side. The connecting portion 13 is formed so as to have a gradually increasing diameter from the welded portion 14 toward the end face 11. In addition, in Fig. 2, the boundaries between the flat surface 13a and the first curved surface 13b, between the first curved surface 13b and the tapered surface 13d, and between the tapered surface 13d and the second curved surface 13c are indicated by dotted lines.

[0028] The flat surface 13a has a uniform outer diameter and is formed to be approximately the same diameter as the main body portion 12. The first curved surface 13b is formed so that the diameter increases as it moves away from the welded portion 14. The second curved surface 13c is formed so that the diameter increases as it approaches the end surface 11. The first curved surface 13b has a larger radius of curvature than the second curved surface 13c and is more gently inclined than the second curved surface 13c. The tapered surface 13d is formed so that the diameter increases as it approaches the second curved surface 13c so as to connect the first curved surface 13b and the second curved surface 13c. The tapered surface 13d expands in diameter at a constant inclination angle. The shoulder surface 13e is formed to extend perpendicularly to the axial direction. The large diameter portion 13f has a uniform outer diameter and is the largest outer diameter at the connecting portion 13. The inclined surface 13g is formed in a tapered shape that expands in diameter at a constant inclination angle. A curved chamfer is formed at the boundary C between the large diameter portion 13f and the inclined surface 13g. In this manner, the outer circumferential surface of the connecting portion 13 is formed so that the diameter gradually increases from the first curved surface 13b to the tapered surface 13d, and the diameter suddenly increases from the second curved surface 13c to the inclined surface 13g. Note that the boundary C between the large diameter portion 13f and the inclined surface 13g is closer to the welded portion 14 than the intersection D between the extension line of the first curved surface 13b and the large diameter portion 13f, which is shown by the two-dot chain line in FIG. 2.

[0029] When axial tensile stress occurs in the cylinder tube 10, stress concentration is likely to occur at the welded portion 14. If a portion where stress is likely to concentrate is located adjacent to the welded portion 14, even greater stress concentration will occur at the welded portion 14, reducing the strength of the cylinder tube 10. However, in this embodiment, the welded portion 14 is adjacent to the first curved surface 13b, which has a large radius of curvature, so that a portion where stress is likely to concentrate is not located adjacent to the welded portion 14, and stress concentration at the welded portion 14 is reduced. Furthermore, the flat surface 13a increases the distance between the welded portion 14 and the first curved surface 13b, further reducing stress concentration at the welded portion 14.

[0030] 2 indicates the line of force when axial tensile stress is generated in the cylinder tube 10. The second curved surface 13c away from the welded portion 14 has a larger outer diameter than the first curved surface 13b and is away from the line of force indicated by the arrow B, so stress concentration is unlikely to occur. Therefore, even if the radius of curvature of the second curved surface 13c is small, the strength of the cylinder tube 10 is maintained.

[0031] Here, if the outer peripheral surface of the connecting portion 13 does not have the tapered surface 13d, the second curved surface 13c, the shoulder surface 13e, and the inclined surface 13g, and the first curved surface 13b is formed between the flat surface 13a and the large diameter portion 13f, the first curved surface 13b has a large radius of curvature, so the area in which the first curved surface 13b is formed (specifically, the axial length in which the first curved surface 13b is formed) is large. Therefore, the area in which the first curved surface 13b is machined in the cylinder tube 10 is large, so that the material of the cylinder tube 10 is wasted. Furthermore, since the cylinder tube 10 is subjected to the cushion pressure generated by the cushion ring 81, if the area in which the first curved surface 13b is formed is large, the thickness of the area in the cylinder tube 10 (connecting portion 13) that is subjected to the cushion pressure is reduced, and the strength of the cylinder tube 10 may be reduced. In contrast, when the radius of curvature of the first curved surface 13b is reduced, the area where the first curved surface 13b is formed becomes smaller, and therefore the amount of wasted material of the cylinder tube 10 is reduced, but the stress concentration generated at the first curved surface 13b and the welded portion 14 increases. Thus, it is difficult to simultaneously reduce the stress concentration and the amount of wasted material in the cylinder tube 10.

[0032] However, in this embodiment, the outer circumferential surface of the connecting portion 13 has a first curved surface 13b and a second curved surface 13c, and the first curved surface 13b has a larger radius of curvature than the second curved surface 13c. The first curved surface 13b reduces stress concentration that occurs at the welded portion 14, and the second curved surface 13c and the large diameter portion 13f are connected via the shoulder surface 13e and the inclined surface 13g, so that the axial length of the connecting portion 13 can be shortened while ensuring the strength of the cylinder tube 10. Therefore, it is possible to achieve both reduction in stress concentration and reduction in material waste.

[0033] In addition, since the shoulder surface 13e extends perpendicular to the axial direction of the cylinder tube 10, the axial length of the connecting portion 13 can be made shorter and the area where material is removed when machining the cylinder tube 10 can be made smaller.

[0034] According to the present embodiment described above, the following advantageous effects are obtained.

[0035] In the hydraulic cylinder 100, although stress concentration is likely to occur at the welded portion 14, the welded portion 14 and the first curved surface 13b are adjacent to each other, so that the stress concentration occurring at the welded portion 14 is reduced. In addition, the second curved surface 13c away from the welded portion 14 has a smaller radius of curvature than the first curved surface 13b, and the second curved surface 13c and the large diameter portion 13f are connected via the shoulder surface 13e and the inclined surface 13g, so that the axial length of the connecting portion 13 can be shortened while ensuring the strength of the cylinder tube 10. Therefore, it is possible to achieve both reduction in stress concentration and reduction in material waste.

[0036] Next, modified examples of this embodiment will be described. The following modified examples are also within the scope of the present invention, and it is possible to combine the configuration shown in the modified example with the configuration described in the above embodiment, or to combine the configurations described in the different modified examples below.

[0037] <Variation 1> In the above embodiment, the outer peripheral surface of the connecting portion 13 has a tapered surface 13d formed between the first curved surface 13b and the second curved surface 13c. However, the tapered surface 13d is not an essential configuration, and the first curved surface 13b and the second curved surface 13c may be formed continuously. In addition, a curved surface may be formed between the first curved surface 13b and the second curved surface 13c instead of the tapered surface 13d that expands in diameter at a constant inclination angle. Even with this configuration, the same effect as the above embodiment is achieved.

[0038] <Variation 2> In the above embodiment, the outer circumferential surface of the connecting portion 13 has the flat surface 13a formed continuously with the welded portion 14. However, the flat surface 13a is not an essential component, and the welded portion 14 and the first curved surface 13b may be formed continuously with each other. In addition, the flat surface 13a does not have to be formed to have substantially the same diameter as the main body portion 12, and may be formed to have a smaller or larger diameter than the main body portion 12.

[0039] <Variation 3> In the above embodiment, the shoulder surface 13e is formed to extend perpendicular to the axial direction. However, the shoulder surface 13e does not have to be formed to extend perpendicular to the axial direction, but may be formed to extend radially outward. In other words, the shoulder surface 13e may be formed to be inclined with respect to the radial direction. The inclination angle α of the shoulder surface 13e with respect to the axial direction (see FIG. 2) is larger than the inclination angle β of the inclined surface 13g with respect to the axial direction (see FIG. 2).

[0040] <Variation 4> In the above embodiment, the inclined surface 13g is formed in a tapered shape that expands in diameter at a constant inclination angle. However, the inclined surface 13g may be curved. In other words, the inclined surface 13g includes a tapered or curved configuration.

[0041] <Variation 5> In the above embodiment, the first curved surface 13b is formed between the flat surface 13a and the tapered surface 13d, and the second curved surface 13c is formed between the tapered surface 13d and the shoulder surface 13e. In addition, a curved surface may also be formed between the shoulder surface 13e and the inclined surface 13g.

[0042] <Variation 6> In the above embodiment, in the connecting portion 13, the flat surface 13a, the first curved surface 13b, the tapered surface 13d, the second curved surface 13c, the shoulder surface 13e, the inclined surface 13g, and the large diameter portion 13f are formed continuously in this order from the welding portion 14 side. In addition to this, another flat surface, tapered surface, or curved surface may be formed on the outer circumferential surface of the connecting portion 13. For example, a tapered surface having a smaller inclination angle than the tapered surface 13d may be formed on the end portion of the first curved surface 13b on the end surface 11 side, and a curved surface may be formed between the tapered surface and the tapered surface 13d.

[0043] The configuration, operation, and effects of the embodiment of the present invention configured as above will be described below.

[0044] A hydraulic cylinder 100 as a fluid pressure cylinder includes a cylinder tube 10, a piston rod 20 provided reciprocally within the cylinder tube 10, a piston 30 connected to the piston rod 20 and slidably housed within the cylinder tube 10, and a cylinder head 40 connected to the cylinder tube 10 and supporting the piston rod 20 so as to be slidable. The cylinder tube 10 includes a cylindrical main body portion 12, an annular connecting portion 13 to which the cylinder head 40 is connected at an end surface 11, a welded portion 14 formed between the main body portion 12 and the connecting portion 13, The outer peripheral surface of the connecting portion 13 has a first curved surface 13b formed so as to have a larger diameter as it moves away from the welded portion 14, a second curved surface 13c formed closer to the end face 11 than the first curved surface 13b and formed so as to have a larger diameter as it approaches the end face 11, a shoulder surface 13e formed continuous with the end portion of the second curved surface 13c on the end face 11 side and extending radially outward, a large diameter portion 13f formed continuous with the end face 11, and an inclined surface 13g formed between the large diameter portion 13f and the shoulder surface 13e, and the first curved surface 13b has a larger radius of curvature than the second curved surface 13c.

[0045] In this configuration, although stress concentration is likely to occur at the welded portion 14, the welded portion 14 and the first curved surface 13b are adjacent to each other, so that the stress concentration occurring at the welded portion 14 is reduced. In addition, the second curved surface 13c away from the welded portion 14 has a smaller radius of curvature than the first curved surface 13b, and the second curved surface 13c and the large diameter portion 13f are connected via the shoulder surface 13e and the inclined surface 13g, so that the axial length of the connecting portion 13 can be shortened while ensuring the strength of the cylinder tube 10. Therefore, it is possible to achieve both reduction in stress concentration and reduction in material waste.

[0046] In addition, the outer circumferential surface of the connecting portion 13 further has a tapered surface 13d formed between the first curved surface 13b and the second curved surface 13c.

[0047] Moreover, the shoulder surface 13e extends perpendicular to the axial direction of the cylinder tube 10.

[0048] In this configuration, the axial length of the connecting portion 13 can be made shorter, and the amount of material that is removed when machining the cylinder tube 10 can be made smaller.

[0049] Although the embodiments of the present invention have been described above, the above-mentioned embodiments merely show some of the application examples of the present invention, and it is not intended that the technical scope of the present invention be limited to the specific configurations of the above-mentioned embodiments. [Explanation of symbols]

[0050] 10...cylinder tube, 11...opening end, 12...main body portion, 13...connecting portion, 13b...first curved surface, 13c...second curved surface, 13d...tapered surface, 13e...shoulder surface, 13f...large diameter portion, 13g...inclined surface, 14...welded portion, 20...piston rod, 30...piston, 40...cylinder head, 100...hydraulic cylinder (fluid pressure cylinder)

Claims

1. A cylinder tube; a piston rod provided reciprocably within the cylinder tube; a piston connected to the piston rod and slidably accommodated within the cylinder tube; a cylinder head connected to the cylinder tube and supporting the piston rod so as to be capable of sliding; The cylinder tube is A cylindrical main body; an annular connecting portion having an end surface to which the cylinder head is connected; a weld portion formed between the main body portion and the connecting portion, The outer circumferential surface of the connecting portion is A first curved surface formed to have a larger diameter as it moves away from the welded portion; a second curved surface formed closer to the end surface than the first curved surface and having a larger diameter as it approaches the end surface; a shoulder surface formed continuously with an end portion of the second curved surface on the end face side and extending radially outward; a large diameter portion formed continuously on the end surface; an inclined surface formed between the large diameter portion and the shoulder surface; The fluid pressure cylinder, wherein the first curved surface has a larger radius of curvature than the second curved surface.

2. 2. The fluid pressure cylinder according to claim 1, A fluid pressure cylinder, wherein an outer peripheral surface of the connecting portion further has a tapered surface formed between the first curved surface and the second curved surface.

3. 2. The fluid pressure cylinder according to claim 1, A fluid pressure cylinder, wherein the shoulder surface extends perpendicular to an axial direction of the cylinder tube.

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