Anti-tilt fast cylinder

Abstract

The utility model relates to oil press technical field especially relates to a kind of quick cylinder of anti eccentric load, it includes cylinder barrel and the piston rod of sliding connection in cylinder barrel, piston rod is double-end rod structure, two rod bodies are stretched out cylinder barrel from the upper and lower ends of cylinder barrel, anti eccentric load structure is respectively arranged in the upper and lower ends of cylinder barrel;Anti eccentric load structure includes first flange, second flange and copper bush, first annular gap is arranged in the junction of the tail end surface of first flange and its inner circumferential wall surface, second annular gap is arranged in the junction of the head end surface of second flange and its inner circumferential wall surface, first annular gap and second annular gap constitute accommodating groove, copper bush is placed in accommodating groove;The inner diameter of copper bush is less than the inner diameter of first flange and the inner diameter of second flange, in first flange, second flange and copper bush, the rod body of piston rod can only contact with copper bush.This kind of quick cylinder of anti eccentric load has stronger anti eccentric load capacity, and service life is also long.

Description

Technical Field

[0001] This utility model relates to the field of hydraulic press technology, and in particular to a fast cylinder that resists off-center loading. Background Technology

[0002] For some hydraulic presses with large worktables, rapid cylinders are needed to achieve rapid descent and return of the mold frame in order to improve efficiency. However, when the hydraulic press has a large worktable or when multiple molds are installed on the worktable, the center of gravity of the worktable will generally shift, meaning the hydraulic press is under uneven load. When there is uneven load, the piston rod of the rapid cylinder will deflect relative to its original axis. This deflection will cause abnormal contact between the piston and the inner wall of the cylinder, resulting in scratches between the piston and the cylinder, commonly known as cylinder scoring. Cylinder scoring will affect the normal operation of the rapid cylinder and reduce its service life.

[0003] Therefore, it is necessary to make improvements to address the problems existing in the current technology. Utility Model Content

[0004] The purpose of this invention is to provide a fast cylinder that resists off-center loads, aiming to solve the problem of short service life of fast cylinders in the prior art when facing off-center loads in hydraulic presses.

[0005] To achieve the above objectives, this utility model provides a fast-acting cylinder with anti-eccentric load, comprising a cylinder barrel and a piston rod slidably connected within the cylinder barrel. The piston rod is a double-ended rod structure, with two rods extending from the upper and lower ends of the cylinder barrel. Anti-eccentric load structures are respectively provided at the upper and lower ends of the cylinder barrel. The anti-eccentric load structures include a first flange, a second flange, and a copper sleeve. The first and second flanges are made of steel. The head end face of the first flange abuts against the end face of the cylinder barrel. The second flange is coaxially arranged with the first flange and connected to the tail end of the first flange. The head end face of the second flange is opposite to the tail end face of the first flange. A first annular notch is provided at the junction of the tail end face of the first flange and its inner peripheral wall surface, and a second annular notch is provided at the junction of the head end face of the second flange and its inner peripheral wall surface. The first and second annular notches form a receiving groove, and the copper sleeve is placed in the receiving groove. The inner diameter of the copper sleeve is smaller than the inner diameter of the first flange and the inner diameter of the second flange. Among the first flange, the second flange, and the copper sleeve, the piston rod can only contact the copper sleeve.

[0006] Furthermore, the inner circumferential wall of the second annular notch has a smaller diameter as it moves further away from the cylinder barrel, and the outer circumferential wall of the portion of the copper sleeve located within the second annular notch also has a smaller diameter as it moves further away from the cylinder barrel, so that the inner circumferential wall of the second annular notch and the outer circumferential wall of the portion of the copper sleeve located within the second annular notch are in close contact.

[0007] Furthermore, the angle ∠1 between the inner circumferential wall of the second annular notch and the axis is 3°-4°.

[0008] Furthermore, the maximum diameter of the second annular notch is less than or equal to the maximum diameter of the copper sleeve.

[0009] Furthermore, the inner peripheral wall of the first annular notch has a constant diameter structure, and the outer peripheral wall of the portion of the copper sleeve located within the first annular notch also has a constant diameter structure.

[0010] Furthermore, the first flange and the second flange are equipped with mounting holes that penetrate their thickness direction, and the end face of the cylinder is provided with threaded holes corresponding to the mounting holes. A screw is provided to pass through the mounting holes and then screwed into the threaded holes, so that the anti-eccentric load structure is installed at the end of the cylinder.

[0011] Furthermore, the first flange extends into the cylinder, and a first sealing ring receiving groove is provided on the outer peripheral wall surface of the portion of the first flange located inside the cylinder. The number of first sealing ring receiving grooves is two or more.

[0012] Furthermore, a second sealing ring receiving groove is provided on the outer peripheral wall surface of the portion of the copper sleeve located inside the first flange.

[0013] Furthermore, a third sealing ring receiving groove is provided on the inner circumferential wall surface of the copper sleeve, and the number of the third sealing ring receiving groove is more than two.

[0014] Furthermore, a dustproof ring receiving groove is provided on the inner peripheral wall surface of the portion of the second flange opposite to the piston rod body.

[0015] This utility model provides a fast-acting cylinder with anti-eccentric load capability. It employs a double-rod structure with anti-eccentric load structures at both the upper and lower ends of the cylinder barrel. These two structures provide two-point constraint on the rod, and combined with the existing constraint between the piston and cylinder barrel, the piston rod is constrained at three points, resulting in strong anti-eccentric load capability. Furthermore, the anti-eccentric load structure includes a copper sleeve. The anti-eccentric load structure contacts the rod via the copper sleeve, which is wear-resistant. Even if the rod rubs against the copper sleeve during eccentric load, it will not cause significant damage to either. However, because the copper sleeve is relatively soft, to prevent deformation under eccentric load and maintain sealing, the anti-eccentric load structure also includes two flanges. These flanges are made of steel and are not easily deformed. By using the two flanges to enclose the copper sleeve, its shape and position are defined, preventing deformation and displacement. The combination of these structural features gives this fast-acting cylinder strong anti-eccentric load capability and a long service life. Attached Figure Description

[0016] Figure 1 This is a three-dimensional structural diagram of the present invention;

[0017] Figure 2This is an exploded structural diagram of the present invention;

[0018] Figure 3 This is a three-dimensional sectional view of the present invention;

[0019] Figure 4 This is a cross-sectional view of the anti-eccentric load structure;

[0020] Figure 5 It is a three-dimensional sectional view of the structure after decomposition of the anti-eccentric load structure.

[0021] Explanation of reference numerals in the attached figures:

[0022] 1. Cylinder barrel; 11. Threaded hole;

[0023] 2. Piston rod; 21. Rod body;

[0024] 3. First flange; 31. First annular notch; 32. First sealing ring receiving groove;

[0025] 4. Second flange; 41. Second annular notch; 42. Dust ring receiving groove;

[0026] 5. Copper sleeve; 51. Second sealing ring receiving groove; 52. Third sealing ring receiving groove;

[0027] 6. Mounting holes. Detailed Implementation

[0028] The embodiments of this utility model are described in detail below.

[0029] In this embodiment, unless otherwise explicitly specified and limited, terms such as "set in," "connected," and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection or a connection through one or more intermediate media. Those skilled in the art can understand the specific meaning of these terms in this embodiment based on the specific circumstances. The directional terms appearing in this embodiment are for the purpose of better describing the characteristics of the features and the relationships between them. It should be understood that when the placement direction of this embodiment changes, the direction of the characteristics of the features and the relationships between them also changes accordingly. Therefore, directional terms do not constitute an absolute limitation on the characteristics of the features and the relationships between them in space, but only a relative limitation.

[0030] This embodiment provides a fast-acting cylinder that resists off-center loading, such as... Figures 1 to 5 As shown, it includes a cylinder 1 and a piston rod 2 slidably connected inside the cylinder 1. The piston rod 2 is a double-ended rod structure, with two rods 21 extending out of the cylinder 1 from the upper and lower ends. Anti-eccentric load structures are respectively provided at the upper and lower ends of the cylinder 1.

[0031] In this embodiment, anti-eccentric load structures are respectively provided at both the upper and lower ends of the cylinder 1. The anti-eccentric load structures can be considered to be symmetrical. In the following text, only the structure of one of the anti-eccentric load structures will be described. For better explanation, the direction of some components is described as head and tail. The head end refers to the end of the component that is closer to the cylinder 1, and the tail end refers to the end of the component that is farther away from the cylinder 1.

[0032] The anti-eccentric load structure includes a first flange 3, a second flange 4, and a copper sleeve 5. The first flange 3 and the second flange 4 are made of steel. The head end face of the first flange 3 abuts against the end face of the cylinder 1. The second flange 4 is coaxially arranged with the first flange 3 and connected to the tail end of the first flange 3. The head end face of the second flange 4 is opposite to the tail end face of the first flange 3. A first annular notch 31 is provided at the junction of the tail end face of the first flange 3 and its inner peripheral wall. A second annular notch 41 is provided at the junction of the head end face of the second flange 4 and its inner peripheral wall. The first annular notch 31 and the second annular notch 41 form a receiving groove, and the copper sleeve 5 is placed in the receiving groove. The inner diameter of the copper sleeve 5 is smaller than the inner diameter of the first flange 3 and the inner diameter of the second flange 4. Among the first flange 3, the second flange 4, and the copper sleeve 5, the rod 21 can and can only contact the copper sleeve 5.

[0033] Based on the above structural design, this type of anti-eccentric load rapid cylinder adopts a double-rod structure, with anti-eccentric load structures at both the upper and lower ends of the cylinder barrel 1. These two anti-eccentric load structures provide two-point constraints on the rod body 21. In addition, the piston rod 2 forms a single-point constraint with the cylinder barrel 1, resulting in a total of three-point constraints on the piston rod 2, thus providing strong anti-eccentric load capability. Simultaneously, the anti-eccentric load structure includes a copper sleeve 5. The anti-eccentric load structure contacts the rod body 21 via the copper sleeve 5. The copper sleeve 5 is wear-resistant, and even if the rod body 21 rubs against the copper sleeve 5 during eccentric load, it will not cause significant damage to either. However, because the copper sleeve 5 is relatively soft, to prevent deformation of the copper sleeve 5 under eccentric load and thus affecting the seal, the anti-eccentric load structure also includes two flanges. The flanges are made of steel and are not easily deformed. By using the two flanges to wrap around the copper sleeve 5, the shape and position of the copper sleeve 5 are limited, making it less prone to deformation and displacement.

[0034] In this embodiment, the inner circumferential wall of the second annular notch 41 has a smaller diameter as it moves further away from the cylinder 1, and the outer circumferential wall of the portion of the copper sleeve 5 located within the second annular notch 41 also has a smaller diameter as it moves further away from the cylinder 1. The inner circumferential wall of the second annular notch 41 and the outer circumferential wall of the portion of the copper sleeve 5 located within the second annular notch 41 are in close contact. Preferably, the angle ∠1 between the inner circumferential wall of the second annular notch 41 and the axis is 3°-4°. The maximum diameter of the second annular notch 41 is less than or equal to the maximum diameter of the copper sleeve 5. As described above, this embodiment requires two flanges to enclose the copper sleeve 5 to define its shape and position. However, dimensional errors inevitably occur in the components during manufacturing. Therefore, this embodiment sets both the inner circumferential wall of the second annular notch 41 and the outer circumferential wall of the copper sleeve 5 to be diameter-reduced structures, and adopts the aforementioned angle and height relationship. During the assembly of the anti-eccentric load structure, as the second flange 4 moves closer to the first flange 3, the fit between the reduced-diameter structures allows the inner circumferential wall of the second annular notch 41 to tightly adhere to the outer circumferential wall of the portion of the copper sleeve 5 located within the second annular notch 41. This fit provides strong support to the portion of the copper sleeve 5 located within the second annular notch 41, preventing deformation under eccentric loads and minimizing displacement of the copper sleeve 5. Even when the maximum diameter of the second annular notch 41 is smaller than the maximum diameter of the copper sleeve 5, it ensures a tight fit between the inner circumferential wall of the second annular notch 41 and the outer circumferential wall of the portion of the copper sleeve 5 located within the second annular notch 41 when the anti-eccentric load structure is in place. Although this creates a gap between the first flange 3 and the second flange 4, hydraulic oil leakage is prevented due to the third sealing ring receiving groove 52 and the sealing ring within it, as described below.

[0035] In this embodiment, the inner circumferential wall of the first annular notch 31 has a constant diameter structure, and the outer circumferential wall of the portion of the copper sleeve 5 located within the first annular notch 31 also has a constant diameter structure. In this embodiment, as described below, since a sealing ring needs to be placed between the copper sleeve 5 and the first flange 3, a constant diameter structure is more suitable at this location.

[0036] In this embodiment, the first flange 3 and the second flange 4 are provided with mounting holes 6 that penetrate their thickness direction. The end face of the cylinder 1 is provided with a screw hole 11 corresponding to the mounting hole 6. A screw rod is provided to pass through the mounting hole 6 and then screwed into the screw hole 11 so that the anti-eccentric load structure is installed at the end of the cylinder 1.

[0037] In this embodiment, the first flange 3 extends into the cylinder 1. A first sealing ring receiving groove 32 is provided on the outer peripheral wall of the portion of the first flange 3 located inside the cylinder 1. There are two or more first sealing ring receiving grooves 32, which are used to hold static sealing rings. A second sealing ring receiving groove 51 is provided on the outer peripheral wall of the portion of the copper sleeve 5 located inside the first flange 3. The second sealing ring receiving groove 51 is used to hold static sealing rings. A third sealing ring receiving groove 52 is provided on the inner peripheral wall of the copper sleeve 5. There are two or more third sealing ring receiving grooves 52, which are used to hold dynamic sealing rings. A dustproof ring receiving groove 42 is provided on the inner peripheral wall of the portion of the second flange 4 opposite to the rod body 21. The dustproof ring receiving groove 42 is used to hold dustproof rings. By providing sealing ring receiving grooves at the aforementioned locations, it can be ensured that the hydraulic oil inside the cylinder 1 will not leak out.

[0038] In summary, this type of fast cylinder with anti-eccentric load has strong anti-eccentric load capability and a long service life.

[0039] Where there is no conflict, the above embodiments and features can be combined with each other.

[0040] Finally, it should be noted that the above embodiments are only used to illustrate the preferred technical solutions of this utility model, and are not intended to limit the scope of protection of this utility model. Although this utility model has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of this utility model without departing from the essence and scope of this utility model.

Claims

1. A fast-acting cylinder for resisting off-center loading, comprising a cylinder barrel (1) and a piston rod (2) slidably connected within the cylinder barrel (1), characterized in that: The piston rod (2) is a double-ended rod structure. Two rods (21) extend from the upper and lower ends of the cylinder (1). Anti-eccentric load structures are provided at both the upper and lower ends of the cylinder (1). The anti-eccentric load structure includes a first flange (3), a second flange (4), and a copper sleeve (5). The first flange (3) and the second flange (4) are made of steel. The head end face of the first flange (3) abuts against the end face of the cylinder (1). The second flange (4) is coaxially arranged with the first flange (3) and connected to the tail end of the first flange (3). The head end face of the second flange (4) is opposite to the tail end face of the first flange (3). A first annular notch (31) is provided at the junction of the tail end face of the first flange (3) and its inner peripheral wall. A second annular notch (41) is provided at the junction of the head end face of the second flange (4) and its inner peripheral wall. The first annular notch (31) and the second annular notch (41) form a receiving groove. The copper sleeve (5) is placed in the receiving groove. The inner diameter of the copper sleeve (5) is smaller than the inner diameter of the first flange (3) and the inner diameter of the second flange (4). Among the first flange (3), the second flange (4) and the copper sleeve (5), the rod (21) can and can only contact the copper sleeve (5).

2. The anti-eccentric load fast cylinder according to claim 1, characterized in that: The inner circumferential wall of the second annular notch (41) has a smaller diameter as it moves further away from the cylinder (1), and the outer circumferential wall of the part of the copper sleeve (5) located inside the second annular notch (41) also has a smaller diameter as it moves further away from the cylinder (1). The inner circumferential wall of the second annular notch (41) and the outer circumferential wall of the part of the copper sleeve (5) located inside the second annular notch (41) are closely fitted.

3. The anti-eccentric load fast cylinder according to claim 2, characterized in that: The angle ∠1 between the inner circumferential wall of the second annular notch (41) and the axis is 3°-4°.

4. The anti-eccentric load fast cylinder according to claim 2, characterized in that: The maximum diameter of the second annular notch (41) is less than or equal to the maximum diameter of the copper sleeve (5).

5. The anti-eccentric load fast cylinder according to claim 1, characterized in that: The inner circumferential wall of the first annular notch (31) has a uniform diameter structure, and the outer circumferential wall of the part of the copper sleeve (5) located inside the first annular notch (31) also has a uniform diameter structure.

6. The anti-eccentric load fast cylinder according to claim 1, characterized in that: The first flange (3) and the second flange (4) are provided with mounting holes (6) that penetrate their thickness direction. The end face of the cylinder (1) is provided with a screw hole (11) corresponding to the mounting hole (6). A screw rod is provided to pass through the mounting hole (6) and then screwed into the screw hole (11) so that the anti-eccentric load structure is installed at the end of the cylinder (1).

7. The anti-eccentric load fast cylinder according to claim 1, characterized in that: The first flange (3) extends into the cylinder (1). A first sealing ring receiving groove (32) is provided on the outer peripheral wall of the part of the first flange (3) located inside the cylinder (1). The number of first sealing ring receiving grooves (32) is two or more.

8. The anti-eccentric load fast cylinder according to claim 1, characterized in that: A second sealing ring receiving groove (51) is provided on the outer peripheral wall of the portion of the copper sleeve (5) located inside the first flange (3).

9. The anti-eccentric load fast cylinder according to claim 1, characterized in that: A third sealing ring receiving groove (52) is provided on the inner circumferential wall of the copper sleeve (5), and the number of the third sealing ring receiving groove (52) is more than two.

10. The anti-eccentric load fast cylinder according to claim 1, characterized in that: A dust ring receiving groove (42) is provided on the inner peripheral wall of the part of the second flange (4) opposite to the rod body (21).

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