WO2017086044A1

WO2017086044A1 - Seal member

Info

Publication number: WO2017086044A1
Application number: PCT/JP2016/079587
Authority: WO
Inventors: 純一山下; 謙一高橋; 彰上田
Original assignee: 日本バルカー工業株式会社
Priority date: 2015-11-19
Filing date: 2016-10-05
Publication date: 2017-05-26
Also published as: TWI696775B; KR102439898B1; TW201719060A; KR20180081766A; JP6655365B2; JP2017096332A; CN108291648A; CN108291648B

Abstract

This seal member (10) is configured so that a curved surface (110) and a sloped surface (120) will be provided in the region where a first side surface (101) of a heel section (10h) and a third side surface (103) thereof intersect, the curved surface (110) being provided so as to be in contact with the first side surface (101) and the sloped surface (120), the sloped surface (120) being provided so as to intersect the third side surface (103).

Description

Seal member

The present invention relates to a seal structure, and more particularly to a structure of a seal member used in a sliding gap between a rod (piston rod) and a cylinder in a hydraulic / pneumatic device or the like.

For example, in a sliding gap between a cylinder and a rod (piston rod) in hydraulic equipment, hydraulic oil introduced into the oil chamber is prevented from leaking (leakage of hydraulic oil from the high pressure side to the low pressure side) and the rod In order to smoothly realize the reciprocating motion, a seal structure in which a seal member is fitted into a seal groove provided in the cylinder is employed. Such a sealing structure is disclosed in Japanese Patent Application Laid-Open No. 2005-337440 (Patent Document 1), Japanese Patent Application Laid-Open No. 2014-214769 (Patent Document 2), and the like.

JP 2005-337440 A JP 2014-214769 A

In recent years, in order to further improve the sealing performance by the sealing structure, the sealing member is improved every day.

The present invention has been made to solve the above-described problems, and it is an object of the present invention to provide a sealing member that can further enhance the sealing performance of the sealing structure.

In the sealing member according to the present invention, the high pressure side and the low pressure side are partitioned in the sliding gap between the cylinder and the rod in the hydraulic / pneumatic equipment, and the sealing groove is provided annularly along the circumferential direction of the outer peripheral surface of the rod Is a sealing member that closes the sliding gap between the cylinder and the rod, and has the following configuration.

A heel portion located on the low pressure side; and a lip portion located on the high pressure side, wherein the heel portion is a first side surface located on the rod side, a second side surface opposed to the first side surface, and A third side surface located on the high-pressure side, the lip portion has a first lip portion that expands toward the rod side, and a second lip portion that expands toward the side opposite to the rod side; A curved surface and an inclined surface are provided in a region where the first side surface and the third side surface of the heel portion intersect, and the curved surface is provided so as to be in contact with the first side surface and the inclined surface, The slope is provided so as to intersect with the third side surface.

In another embodiment, the projection length of the curved surface and the slope on the third side surface is 0.3 mm or more and 2 mm or less, the radius of the curved surface is 2 mm or more and 15 mm or less, The inclination angle with respect to the third side surface is 30 ° to 80 °.

According to the present invention, it is possible to provide a seal structure that can further enhance the sealing performance of the seal structure.

It is sectional drawing which shows the seal structure employ | adopted as the hydraulic equipment of embodiment. It is a perspective view which shows the structure of the 1st seal member of embodiment. FIG. 3 is a cross-sectional view taken along line III in FIG. 2. It is a partial expansion schematic diagram which shows the sealing state of the 1st seal member in embodiment. It is a figure which shows the seal pressure state of the 1st seal member at the time of mounting | wearing of embodiment. It is a figure which shows the relationship between the contact width of a 1st seal member at the time of mounting | wearing of embodiment, and a contact surface pressure. It is a figure which shows the seal pressure state of the 1st seal member at the time of the pressure load of embodiment. It is a figure which shows the relationship between the contact width of a 1st seal member at the time of the pressure load of embodiment, and a contact surface pressure. It is sectional drawing which shows the structure of the 1st seal member in related technology. It is a partial expansion schematic diagram which shows the sealing state of the 1st seal member in related technology. It is a figure which shows the seal pressure state in the 1st seal member at the time of mounting | wearing of related technology. It is a figure which shows the relationship between the contact width at the time of mounting | wearing of related technology, and contact surface pressure. It is a figure which shows the seal pressure state in the 1st seal member at the time of the pressure load of related technology. It is a figure which shows the relationship between the contact width at the time of the pressure load of related technology, and a contact surface pressure. It is a figure which shows the relationship of sliding distance and leakage amount of embodiment and related technology. It is sectional drawing which shows the modification of the 1st seal member of embodiment. It is sectional drawing which shows the other modification of the 1st seal member of embodiment. It is a figure which shows the seal pressure state of (R = 15, (theta) = 80 degrees, a = 0.3) at the time of the pressure load of Example 1. FIG. It is a figure which shows the relationship between the contact width at the time of the pressure load of Example 1, and a contact surface pressure. It is a figure which shows the seal pressure state of (R = 2, (theta) = 30 degrees, a = 2) at the time of the pressure load of Example 2. FIG. It is a figure which shows the relationship between the contact width at the time of the pressure load of Example 2, and a contact surface pressure. It is a figure which shows the seal pressure state of (R = 0.5, (theta) = 30 degrees, a = 2) at the time of the pressure load of Example 3. FIG. It is a figure which shows the relationship between the contact width at the time of the pressure load of Example 3, and a contact surface pressure.

The seal member and the seal structure using the seal member in the embodiment based on the present invention will be described below with reference to the drawings. In the embodiments described below, when referring to the number, amount, and the like, the scope of the present invention is not necessarily limited to the number, amount, and the like unless otherwise specified. The same parts and corresponding parts are denoted by the same reference numerals, and redundant description may not be repeated. In the following, a hydraulic cylinder is cited as an example of a hydraulic / pneumatic device, but the present invention is not limited to a hydraulic cylinder, and can be widely applied to a hydraulic / pneumatic device.

(Seal structure)
With reference to FIG. 1, the seal structure in this Embodiment is demonstrated. FIG. 1 is a cross-sectional view showing a seal structure employed in the hydraulic cylinder in the embodiment. In FIG. 1, a cylinder 1 and a rod (piston rod) 2 are shown by broken lines for convenience of explanation. The seal structure shown in FIG. 1 is deformed with the pressure contact with the rod 2 and the reciprocating motion of the rod 2 (vertical direction in FIG. 1). However, in order to clearly understand the seal structure, pressure is applied to the seal structure. The state is not shown.

An annular first seal groove 10G is provided along the circumferential direction of the outer peripheral surface of the rod 2. The first seal groove 10 </ b> G accommodates a first seal member 10 that closes the sliding gap between the cylinder 1 and the rod 2.

The second seal groove 20G is provided in an annular shape along the circumferential direction of the outer peripheral surface of the rod 2 and on the high pressure side of the first seal groove 10G. In the drawing, a high-pressure hydraulic chamber is provided on the upper side. A second seal member 20 that closes a sliding gap between the cylinder 1 and the rod 2 is accommodated in the second seal groove 20G.

(First seal member 10)
With reference to FIG. 2 and FIG. 3, the 1st seal member 10 in this Embodiment is demonstrated. 2 is a perspective view showing the structure of the first seal member 10, and FIG. 3 is a cross-sectional view taken along line III in FIG.

The first seal member 10 has an annular shape as a whole, and is integrally formed of synthetic resin such as urethane resin, natural rubber, synthetic rubber, or fluororubber. The first seal member 10 has a substantially U-shaped cross section having an open side on the high pressure side.

More specifically, it includes a heel portion 10h located on the low pressure side and a lip portion 10r located on the high pressure side in the sectional view shown in FIG. The heel portion 10h includes a first side face 101 located on the rod 2 side, a second side face 102 located opposite to the first side face 101, and a third side face 103 located on the high pressure side.

The lip portion 10r includes a first lip portion 10b that expands toward the rod 2 side and a second lip portion 10c that expands toward the side opposite to the rod 2 side. The first lip portion 10b and the second lip portion 10c form a substantially U shape.

Further, a curved surface 110 and an inclined surface 120 are provided in a region where the first side surface 101 and the third side surface 103 of the heel portion 10h intersect, which is the low pressure side on the rod 2 side when viewed from the heel portion 10h. . The curved surface 110 is provided so as to be in contact with the first side surface 101 and the inclined surface 120, and the inclined surface 120 is provided so as to intersect with the third side surface 103.

The projected length of the curved surface 110 and the inclined surface 120 onto the third side surface 103 is “a”, the radius of the curved surface 110 is “R”, and the inclination angle of the inclined surface 120 with respect to the third side surface 103 is “θ”. In order to obtain better sealing performance with respect to the rod 2 in the first seal member 10, the projection length “a” is 0.3 mm or more and 2 mm or less, and the radius “R” of the curved surface 110 is 2 mm or more and 15 mm or less. The inclination angle “θ” of the inclined surface 120 with respect to the third side surface 103 is preferably 30 ° to 80 °. This point will be described in an embodiment described later.

Referring again to FIG. 1, when viewed from the first seal member 10, when the rod 2 moves from the low pressure side toward the high pressure side, this is called a “pulling step”, and the rod 2 is moved to the high pressure side. When moving from a low pressure side to a low pressure side, this is called a “pushing process”.

The sealing state of the first seal member 10 will be described with reference to FIGS. FIG. 4 is a partially enlarged schematic diagram showing a sealing state in the “pulling step”, FIG. 5A is a diagram showing a sealing pressure state of the first seal member 10 at the time of mounting, and FIG. 5B is a first sealing member at the time of mounting. FIG. 6A is a diagram showing a seal pressure state of the first seal member 10 when pressure is applied, and FIG. 6B is a diagram showing a relationship between the contact width and the contact surface pressure of FIG. It is a figure which shows the relationship between a contact width and a contact surface pressure. In FIG. 5A and FIG. 6A, P1 to P10 indicate internal pressure distributions, indicating that the internal pressure decreases from P1 to P10.

As shown in FIG. 4 and FIG. 5A, the first lip portion 10 b has a form that expands toward the rod 2 side, and the region where the first side surface 101 and the third side surface 103 of the heel portion 10 h of the first seal member 10 intersect with each other. Further, by providing the curved surface 110 and the inclined surface 120, the heel portion 10h is in a non-contact state with the rod 2 even at the time of wearing, and the oil OL can be easily introduced into the cylinder 1 during the “pulling process”. It is possible to return to

As is apparent from the diagram showing the relationship between the contact width of the first seal member 10 and the contact surface pressure during the mounting of FIG. 5B, in the region where the first side surface 101 and the third side surface 103 of the heel portion 10h intersect, Since it does not contact the rod 2, no peak surface pressure is generated in the region R1. On the other hand, since the first lip portion 10b and the second lip portion 10c are sandwiched between the first seal groove 10G and the rod 2 and greatly deformed, based on the reaction force, the region P2 (P9 in (A)) In the region shown), the peak surface pressure due to contact is generated.

Next, even during the pressure load in FIGS. 6A and 6B, the curved surface 110 and the inclined surface 120 are provided in the region R1 in the region where the first side surface 101 and the third side surface 103 of the heel portion 10h intersect. Even if the contact width moves, the contact surface pressure can be kept smooth without generating the peak surface pressure. As a result, it is possible to reduce the resistance of oil to the inside of the cylinder 1 and to improve the oil suction characteristic by the seal structure using the first seal member 10 and to further improve the sealing performance.

On the other hand, FIG. 7 shows a cross-sectional view of the first seal member 10X in the related art. FIG. 3 is a view corresponding to a cross section taken along line III-III in FIG. 2. The shapes of the first lip portion 10b and the second lip portion 10c of the lip portion 10r are the same as those of the first seal member 10 of the present embodiment. In the first seal member 10X, only the slope 150 is provided in the region where the first side surface 101 and the third side surface 103 intersect, and no curved surface is provided.

8 to 10B, the seal state of the related art first seal member 10X will be described. FIG. 8 is a partially enlarged schematic view showing a seal state in the “pulling step”, FIG. 9A is a view showing a seal pressure state of the first seal member 10X at the time of mounting, and FIG. 9B is a first seal member at the time of mounting. 10A is a diagram showing the relationship between the contact width of 10X and the contact surface pressure, FIG. 10A is a diagram showing the seal pressure state of the first seal member 10X at the time of pressure load, and FIG. 10B is the diagram of the first seal member 10X at the time of pressure load. It is a figure which shows the relationship between a contact width and a contact surface pressure. In FIGS. 9A and 10A, P1 to P10 indicate the distribution of internal pressure, and the internal pressure decreases from P1 to P10.

As shown in FIGS. 8 and 9A, in the first seal member 10X, the heel portion 10h of the first seal member 10X is not provided with a curved surface, and only the inclined surface 150 is provided. As a result, at the time of mounting, the heel portion 10h comes into contact with the rod 2, and a peak surface pressure is formed in the region R3 as shown in FIG. 9B. Further, even when the pressure is applied in FIGS. 10A and 10B, since the region where the first side surface 101 and the third side surface 103 of the heel portion 10h intersect is only the slope 150, a larger peak surface pressure is present in the region R4. appear. As a result, during the drawing process, the oil suction characteristic was poor, which was one factor in causing oil leakage.

FIG. 11 explains the amount of leakage between the first seal member 10 of the embodiment and the first seal member 10X of the related art. FIG. 11 is a diagram illustrating the relationship between the sliding distance and the leakage amount between the first seal member 10 of the embodiment and the first seal member 10X of the related art.

Both the first seal member 10 and the first seal member 10X are synthetic resins such as urethane resin (hardness durometer A90, tensile strength Mpa 44.0, elongation 500%, compression set 40%, compression set test conditions. 8) (80 ° C.-70 h): Nippon Valqua Industries, Ltd., product number R5590)).

The first seal member 10 has R = 2 mm, θ = 60 °, and a = 0.6 mm. The first sealing member 10X is not provided with a curved surface, and the inclined surface 150 has R = 0 mm, θ = 45 °, and a = 0.5 mm (so-called C surface = 0.5 mm).

In the measurement, only the first seal member was attached, and the amount of external leakage of oil from the cylinder 1 was measured. The result is shown in FIG. It has been confirmed that the first seal member 10 in the present embodiment has better sealing performance than the first seal member 10X in the related art.

(Example)
12 and 13 show a structure of a modified example of the first seal member 10 in the present embodiment. FIG. 12 shows the shape of the first seal member 10A having a relatively large “a”, and FIG. 13 shows the case of the first seal member 10B having a relatively large “θ”.

Further, FIGS. 14A to 16B show the relationship between the contact width and the contact surface pressure at the time of pressure loading, as specific examples 1 to 3. FIG. The first seal member 10 in Example 1 has a shape of R = 15, θ = 80 °, and a = 0.3, and the first seal member 10 in Example 2 has R = 2 and θ = 30 °. , A = 2, and the first seal member 10 in Example 3 has a shape of R = 0.5, θ = 30 °, and a = 2. In each figure A, P1 to P10 indicate the distribution of the internal pressure, and the internal pressure decreases from P1 to P10.

In the case of Example 1 shown in FIG. 14A and FIG. 14B, no peak surface pressure is generated in the entire contact width, and good surface pressure is shown. I was able to confirm.

In the case of Example 2 shown in FIG. 15A and FIG. 15B, compared to Example 1 above, no peak surface pressure is generated in the entire contact width, and a better surface pressure is shown. It was confirmed that it had excellent sealing performance.

In the case of Example 3 shown in FIGS. 16A and 16B, compared to Example 1 above, a minute peak surface pressure is generated in a region where the contact width is about 1 mm. Although it is not good at all, it is better than the related technology shown in FIG. 10A and FIG. 10B, so that it has been confirmed that it has a good sealing performance as a whole.

According to the above embodiment, the curved surface 110 and the inclined surface 120 are provided in the region where the first side surface 101 and the third side surface 103 of the heel portion 10h intersect, and the curved surface 110 includes the first side surface and the inclined surface 120. The inclined surface 120 is provided so as to intersect the third side surface 103. Thereby, the 1st sealing member in this Embodiment has favorable sealing performance.

Further, the projection length “a” of the curved surface 110 and the inclined surface 120 onto the third side surface 103 is set to 0.3 mm or more and 2 mm or less, and the radius “R” of the curved surface 110 is set to 2 mm or more and 15 mm or less. By setting the inclination angle “θ” with respect to the third side surface 103 to 30 ° to 80 °, it is possible to obtain more preferable sealing performance.

Although the embodiments and examples have been described above, the embodiments disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

1 cylinder, 2 rod, 10, 10A, 10B first seal member, 10G first seal groove, 10h heel portion, 10r lip portion, 20 second seal member, 20G second seal groove, 101 first side surface, 102 second Side surface, 103 3rd side surface, 10b 1st lip part, 10c 2nd lip part, 110 curved surface, 120 slope.

Claims

In the sliding gap between the cylinder and the rod in the hydraulic / pneumatic equipment, the high pressure side and the low pressure side are partitioned, and housed in an annular seal groove provided along the circumferential direction of the outer peripheral surface of the rod, A sealing member for closing a sliding gap with the rod,
A heel portion located on the low pressure side;
Including a lip portion located on the high pressure side,
The heel part is
A first side located on the rod side, a second side located opposite the first side, and a third side located on the high pressure side,
The lip portion is
A first lip portion that expands toward the rod side, and a second lip portion that expands toward the opposite side of the rod side,
A curved surface and a slope are provided in a region where the first side surface and the third side surface of the heel portion intersect,
The curved surface is provided so as to contact the first side surface and the inclined surface,
The slope is a seal member provided so as to intersect with the third side surface.
The projection length of the curved surface and the inclined surface onto the third side surface is 0.3 mm or more and 2 mm or less,
The radius of the curved surface is 2 mm or more and 15 mm or less,
The sealing member according to claim 1, wherein an inclination angle of the inclined surface with respect to the third side surface is 30 ° to 80 °.