CN113669360B - Rubber spherical hinge for reducing friction force between curved surface sliding block and curved surface coating - Google Patents
Rubber spherical hinge for reducing friction force between curved surface sliding block and curved surface coating Download PDFInfo
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- CN113669360B CN113669360B CN202110936995.2A CN202110936995A CN113669360B CN 113669360 B CN113669360 B CN 113669360B CN 202110936995 A CN202110936995 A CN 202110936995A CN 113669360 B CN113669360 B CN 113669360B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C11/00—Pivots; Pivotal connections
- F16C11/04—Pivotal connections
- F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/08—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with rubber springs ; with springs made of rubber and metal
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Abstract
The invention discloses a rubber spherical hinge for reducing friction force between a curved surface sliding block and a curved surface coating, and belongs to the technical field of rubber spherical hinges. The rubber spherical hinge for reducing the friction force between the curved surface sliding block and the curved surface coating is characterized in that the curved surface on the inner side of the curved surface sliding block is processed into a concave spherical surface with spherical surface characteristics; arranging a coating on the outer spherical surface of the mandrel ball which also has spherical surface characteristics and is positioned in the cavity, and enabling the coating to have a smooth coating surface; planning a pressed area corresponding to the pressure of the concave spherical surface on the coating surface; the friction resistance of the concave spherical surface during sliding is reduced by arranging the smooth coating surface, and meanwhile, the pressed area corresponding to the bearing pressure is planned on the coating surface, so that the stress area of the coating surface is prevented from being damaged due to overlarge pressure when the concave spherical surface slides on the coating surface.
Description
Technical Field
The invention relates to a rubber ball hinge used in a side rolling resisting device of a train, in particular to a rubber ball hinge for reducing friction force between a curved surface sliding block and a curved surface coating, and belongs to the technical field of rubber ball hinges.
Background
Conventionally, rubber ball hinges are used at the upper end and the lower end of a vertical pull rod of an anti-rolling torsion bar on a train.
The rubber ball hinge has low manufacturing cost and is not easy to generate abnormal sound. However, the existing rubber ball joints for the anti-roll torsion bar are all formed by solid rubber filling through vulcanization, namely rubber solid vulcanization is adopted between the mandrel and the outer sleeve. Compared with the anti-rolling of a train, the rubber ball hinge is characterized in that the radial rigidity is smaller, the partial torsional rigidity is larger, and the limit partial torsional angle is smaller.
The radial rigidity is small, and the pull rod and the torsion arm cannot be timely and sufficiently transferred with pulling force or pushing force, so that the reaction of resisting the side rolling of the carriage is delayed, and the side rolling of the carriage cannot be timely and effectively inhibited in an initial state.
The adverse effect that the limit deflection torsion angle is smaller when the deflection torsion rigidity is larger affects the service life of the rubber ball hinge. When the anti-rolling torsion bar works, the pull rod needs to change the angle to drive the spherical hinge outer sleeve to deflect or twist around the mandrel, and the solid rubber body between the outer sleeve and the mandrel ensures that the deflection or twisting rigidity is very high. Under certain working conditions, the deflection or torsion angle is more than 15 degrees, and the rubber body between the outer sleeve and the mandrel is repeatedly twisted at a large angle and a strong force for a long time, so that the fatigue of the rubber body and the crack between the rubber body and a vulcanized part are caused, and the service life of the rubber ball hinge is shortened.
In order to solve the problem of small radial rigidity, a mode of adding a plurality of layers of metal spacer sleeves in a rubber layer for vulcanization is adopted in the industry, so that the radial rigidity of the rubber ball hinge is obviously enhanced, but the problems of large partial torsional rigidity and small limit partial torsional angle are not solved, and are more serious than the rubber ball hinge filled and supported by pure rubber.
In order to adapt to severe combined load working conditions of large deflection angle, large torsion angle and large radial load, the company carries out series improvement on a rubber ball hinge (patent application is filed on the same day), wherein the problem of long-term and repeated friction between a curved surface sliding block and a curved surface coating under high pressure (20-40 KN) is involved. The key of the improvement is that the measures adopted for reducing the frictional resistance between the curved surface slide block and the mandrel ball must have high reliability, and special structural design and manufacturing process are required besides the selection of proper materials.
Disclosure of Invention
The technical problem to be solved by the invention is as follows: the problem of how to reliably reduce the friction resistance between the curved surface slide block 6 and the mandrel ball 41 in the rubber ball joint under the working condition of large radial load is solved.
Aiming at the problems, the technical scheme provided by the invention is as follows:
a cavity 3 is formed in a rubber layer 2 between a mandrel 4 and an outer sleeve 1 which are positioned on the upper portion of a mandrel 4 in a rubber ball hinge and a rubber layer 2 between the mandrel 4 and the outer sleeve 1 which are positioned on the lower portion of the mandrel 4 in the rubber ball hinge, a spherical mandrel ball 41 is positioned in the cavity 3, a curved surface sliding block 6 with the rigidity, which is far greater than that of rubber, is arranged in the cavity 3, the outer side of the curved surface sliding block 6 is fixed with the outer sleeve 1, the inner side of the curved surface sliding block is in contact with the mandrel ball 41 and is matched with the curved surface of the mandrel ball 41, and the curved surface sliding of the mandrel ball 41 can realize the partial torsion function of the ball hinge.
Thus, the radial rigidity of the spherical hinge is obviously enhanced because the curved surface slide block 6 with rigidity far greater than that of rubber replaces rubber. Due to the existence of the cavity 3, the total rubber amount of the rubber layer 2 is reduced by about 40 percent, so that the partial torsion rigidity is obviously reduced, and the partial torsion angle is correspondingly increased.
However, factors that affect the reduction of the partial torsional rigidity and the corresponding increase of the partial torsional angle still exist, which is a problem of the frictional resistance between the curved surface slider 6 and the spindle ball 41. The larger the frictional resistance, the more the torsional rigidity of the spherical hinge is actually increased, and even the torsional angle can be influenced. Moreover, too much frictional resistance also increases the abrasion between the curved surface slide block 6 and the mandrel ball 41, affects the service life of the spherical hinge, and causes frictional noise between the curved surface slide block 6 and the mandrel ball 41. Therefore, the improvement of the rubber ball joint is to reduce the frictional resistance between the curved surface slide 6 and the mandrel ball 41.
Because the pressure applied to the mandrel ball 41 by the curved surface sliding block 6 under the working condition is up to 20-40 KN, the high pressure is applied between the curved surface sliding block 6 and the mandrel ball 41 by less than 10cm 2 And the relative sliding between the curved surface slider 6 and the mandrel ball 41 is repeated for a long period of time.
Therefore, the key of the improvement is that the measures taken to reduce the frictional resistance between the curved surface slide block 6 and the mandrel ball 41 must have high reliability, and special structural design and manufacturing process are required besides selecting proper materials.
A rubber ball hinge for reducing the friction force between a curved surface slide block and a curved surface coating is characterized in that a curved surface on the inner side of the curved surface slide block is processed into a concave spherical surface with spherical surface characteristics; arranging a coating on the outer spherical surface of the mandrel ball which also has spherical surface characteristics and is positioned in the cavity, and enabling the coating to have a smooth coating surface; planning a pressed area corresponding to the pressure of the concave spherical surface on the coating surface; the friction resistance of the concave spherical surface during sliding is reduced by arranging the smooth coating surface, and meanwhile, the pressed area corresponding to the bearing pressure is planned on the coating surface, so that the stress area of the coating surface is prevented from being damaged due to overlarge pressure when the concave spherical surface slides on the coating surface.
Further, the coating layer is provided with a smooth coating surface, and the outer layer of the coating layer is made of TPFE materials with self-lubricating properties.
Further, the maximum pressure area of the coating surface when the maximum pressure of the concave spherical surface is planned to be borne by the coating surface is that the whole concave spherical surface can contact the coating surface, so that the coating surface can bear the maximum pressure exerted by the concave spherical surface in the maximum area.
Furthermore, the whole concave spherical surface can contact the coating surface, when the concave spherical surface of the curved surface sliding block applies pressure to the coating surface of the TPFE coating to form an interaction force, the curved surface sliding block and the TPFE coating simultaneously generate elastic deformation, and the distance between the concave spherical surface and the coating surface is controlled to realize the purpose.
The rubber spherical hinge for reducing the friction force between the curved surface sliding block and the curved surface coating adopts elastic high polymer composite materials to manufacture the curved surface sliding block, and meanwhile, the thickness of the coating is set to be 40-70 mu m; when the curved surface slide block is rigidly connected with the lining block, the distance between the concave spherical surface of the curved surface slide block and the coating surface of the mandrel ball is smaller than 100 um.
The rubber spherical hinge for reducing the friction force between the curved surface sliding block and the curved surface coating adopts elastic polymer composite material to manufacture the curved surface sliding block, and the thickness of the coating is set to be 40-70 um; when the distance between the concave spherical surface of the curved surface slide block and the coating surface of the mandrel ball is set to be 100-300 um, the curved surface slide block can be further bent when being stressed.
Furthermore, the curved surface sliding block can be further bent when stressed, a rubber interlayer is additionally arranged between the curved surface sliding block and the lining block through vulcanization, and the thickness in the middle of the rubber interlayer is larger than the thickness at two ends of the rubber interlayer.
Furthermore, the thickness of the middle of the rubber interlayer is larger than the thickness of the two ends, the outer arc surface of the curved surface sliding block and the outer arc surface of the lining block are kept unchanged, and the curvature of the inner arc surface of the lining block is reduced.
Furthermore, the thickness of the middle of the rubber interlayer is larger than the thickness of the two ends, so that the inner arc surface of the lining block is kept unchanged, and the curvature of the outer arc surface of the curved surface sliding block is increased.
The rubber ball hinge for reducing the friction force between the curved surface sliding block and the curved surface coating is to chamfer the periphery of the concave spherical surface of the curved surface sliding block, and when the coating surface deforms and sinks under the pressure of the concave spherical surface and the concave spherical surface slides on the coating surface, the coating surface is prevented from being scratched by the edge of the concave spherical surface.
Has the advantages that:
1. the smooth coating surface is arranged on the outer spherical surface of the mandrel ball, so that the frictional resistance of the concave spherical surface and the outer spherical surface during sliding can be reduced;
2. by planning the pressed area corresponding to the bearing pressure on the coating surface, the damage of the stressed area of the coating surface due to overlarge pressure intensity is avoided when the concave spherical surface slides on the coating surface, and the reliability of long-term and repeated use of the special friction pair of the curved surface sliding block and the curved surface coating under high pressure can be obviously improved.
3. Through set up the rubber intermediate layer between curved surface slider and filler block, when the rubber ball pivot meets with impact load suddenly, the rubber intermediate layer can play fine cushioning effect, alleviates the rigid impact of curved surface slider to the coating face to a great extent to make the coating face obtain better protection.
Drawings
FIG. 1 is a perspective view of a rubber ball joint according to the first embodiment and the first embodiment;
FIG. 2 is a perspective view of a mandrel according to embodiments one and two;
FIG. 3 is a perspective view of a pad and a curved slider according to an embodiment of the present invention;
fig. 4 is a schematic cross-sectional view of a mandrel ball, a curved surface slider and a pad in the rubber ball joint according to the first embodiment, which illustrates a state in which the rubber ball joint is not under pressure, and a set distance is maintained between a coating surface and a concave spherical surface;
fig. 5 is a schematic cross-sectional view of a mandrel ball, a curved surface slider, and a pad in the rubber ball hinge according to the first embodiment, in which a concave spherical surface of the curved surface slider is pressed against a coating surface with a small pressure, the concave spherical surface and the coating surface respectively form a pressing surface and a pressed surface which are stressed with each other, and a range of the pressing surface on the concave spherical surface and a range of the pressed surface on the coating surface are between straight lines L1 and L2;
fig. 6 is a schematic cross-sectional view of a mandrel ball, a curved surface slider and a pad in the rubber ball hinge according to the first embodiment, wherein the concave spherical surface of the curved surface slider is pressed on the coating surface by a pressure reaching a set large pressure value, and the whole concave spherical surface is pressed on the coating surface;
FIG. 7 is a perspective view of the pad and curved slider of the second embodiment, with the rubber layer not shown;
fig. 8 is a schematic cross-sectional view of a mandrel ball, a curved surface slider, and a pad in the rubber ball joint according to the second embodiment, which illustrates a situation in which the rubber ball joint is not under pressure, and a set distance is maintained between a coating surface and a concave spherical surface;
fig. 9 is a schematic cross-sectional view of a mandrel ball, a curved surface slider, and a pad in a rubber ball hinge according to a second embodiment, in which a concave spherical surface of the curved surface slider is pressed against a coating surface with a small pressure, the concave spherical surface and the coating surface respectively form a pressing surface and a pressed surface which are stressed with each other, and a range of the pressing surface on the concave spherical surface and a range of the pressed surface on the coating surface are between straight lines L3 and L4;
fig. 10 is a schematic cross-sectional view of the mandrel ball, the curved surface slider and the pad in the rubber ball hinge according to the first embodiment, in which the concave spherical surface of the curved surface slider is pressed against the coating surface of the mandrel ball with a large pressure, the two ends of the rubber interlayer are compressed to the limit, arrows F2 and F3 indicate that the pad applies an increasing pressure to the two outer ends of the curved surface slider, and the radially outward reaction force F1 generated by the coating surface is concentrated in the central region of the concave spherical surface on the inner side of the curved surface slider, so that the curved surface slider is forced to bend further until the entire concave spherical surface is pressed against the coating surface, and the coating surface obtains the largest pressed area.
In the figure: 1. a jacket; 2. a rubber layer; 3. a cavity; 4. a mandrel; 41. a mandrel ball; 42. an outer spherical surface; 43. coating a surface; 44. a compression point; 45. a pressed surface; 5. a filler block; 51. an intrados surface; 6. a curved surface slider; 61. a concave spherical surface; 62. an outer arc surface; 63. a positive pressure point; 64. pressing the surface; 65. chamfering; 7. a rubber interlayer; 8. and (4) spacing.
Detailed Description
The invention is further described with reference to the following examples and figures:
the structure to which the invention relates will now be described in detail for a better description and understanding of the method of the invention.
As shown in fig. 1, 2, and 3, in order to adapt to severe combined load conditions of a large deflection angle, a large torsion angle, and a large radial load, cavities 3 are formed in a rubber layer 2 between a mandrel 4 and an outer sleeve 1 on the upper portion of a mandrel 4 and in the rubber layer 2 between the mandrel 4 and the outer sleeve 1 on the lower portion of the mandrel 4 in a rubber ball hinge, the portions of the mandrel 4 located in the upper and lower cavities 3 are spherical mandrel balls 41, and the spherical surfaces of the mandrel balls 41 exposed in the upper and lower cavities 3 are outer spherical surfaces 42. The rigidity of the outer side of the cavity 3 fixed with the outer sleeve 1 is far higher than that of the curved surface sliding block 6 made of rubber, so that the inner side of the curved surface sliding block 6 is in contact with the outer spherical surface 42 of the mandrel ball 41 and is matched with the outer spherical surface 42 to form a special sliding friction pair, and the outer sleeve 1 can slide on the outer spherical surface 42 of the mandrel ball 41 through the curved surface sliding block 6 to realize the eccentric torsion function of the spherical hinge.
The curved surface slide block 6 can be regarded as a section cut out on a circular ring, the circumferential length of the curved surface slide block is about three times of the axial width, the radial thickness of the curved surface slide block is equal everywhere, the inner side surface of the curved surface slide block is processed into a concave spherical surface 61 with spherical surface characteristics, the outer side surface of the concave spherical surface is an arc-shaped outer arc surface 62, and the spherical center of the concave spherical surface 61 and the circle center of the outer arc surface 62 are in a same point.
And a lining block 5 connected with the curved surface slide block 6 is arranged on the outer side of the curved surface slide block 6.
The lining block 5 is a rigid body which does not generate deformation, the inner side of the lining block 5 is an arc-shaped inner arc surface 51, and the circumferential length and the axial width of the inner arc surface 51 of the lining block 5 are respectively equal to or larger than the circumferential length and the axial width of the outer arc surface 62 of the curved surface slide block 6. The extrados surface 62 of the curved slider 6 is connected with the intrados surface 51 of the pad 5.
The periphery of the lining block 5 is the outer sleeve 1 of the whole rubber spherical hinge, and the curved surface sliding block 6 with rigidity far higher than that of rubber is arranged in the cavity 3 and fixedly connected with the outer sleeve 1 at the outer side, namely the curved surface sliding block 6 is fixedly connected with the outer sleeve 1 through the lining block 5 in the cavity 3.
There is a radial distance 8 between the outer spherical surface 42 of the mandrel ball 41 and the concave spherical surface 61 of the curved surface slider 6, and this radial distance 8 is equal everywhere, that is, the outer spherical surface 42 of the mandrel and the concave spherical surface 61 of the curved surface slider 6 have a common spherical center, and the spherical radius of the concave spherical surface 61 is larger than that of the outer spherical surface 42.
Since the spherical radius of the concave spherical surface 61 of the curved slider 6 is larger than that of the outer spherical surface 42 of the mandrel ball 41, theoretically, there is only one point of contact between the concave spherical surface 61 and the outer spherical surface 42 when the concave spherical surface 61 is pressed against the outer spherical surface 42 on the premise that the concave spherical surface 61 and the outer spherical surface 42 are not deformed.
When the concave spherical surface 61 presses on the outer spherical surface 42, the point at which the concave spherical surface 61 presses on the outer spherical surface 42 is always located at the top region of the concave spherical surface 61, and this point is hereinafter referred to as the positive pressure point 63 of the concave spherical surface 61. The point at which the outer spherical surface 42 is subjected to the pressure of the concave spherical surface 61, which point is referred to hereinafter as the pressure point 44 of the outer spherical surface 42, can slide on the outer spherical surface 42.
Most preferably, the radial distance 8 between the outer spherical surface 42 of the mandrel and the concave spherical surface 61 of the curved slider 6 is as small as infinitely close to zero. Thus, when the concave spherical surface 61 applies pressure to the outer spherical surface 42, the entire concave spherical surface 61 can contact the outer spherical surface 42, and the force applied to the outer spherical surface 42 is a maximized surface rather than a pressure point 44, which is very beneficial for protecting the outer spherical surface 42. However, due to the factors of the processing equipment and the processing technology, it is difficult to achieve that the radial distance 8 between the outer spherical surface 42 of the mandrel and the concave spherical surface 61 of the curved slider 6 is as small as infinitely close to zero, and at present, it is easy to achieve that the radial distance 8 between the outer spherical surface 42 and the concave spherical surface 61 is between 100um and 300 um.
Example one
As shown in fig. 3-6, the rubber ball hinge for reducing the friction between the curved surface slider and the curved surface coating is to expose the mandrel ball 41 on the outer surface of the cavity 3 to form an outer spherical surface 42 with spherical characteristics, and to process the curved surface on the inner side of the curved surface slider 6 to form a concave spherical surface 61 with spherical characteristics; the coating is provided on the outer spherical surface 42 and has a smooth coated surface 43, so that the concave spherical surface 61 of the curved slider 6 does not directly act on the outer spherical surface 42 of the mandrel ball 41, but acts on the smooth coated surface 43 and slides on the smooth coated surface 43. The coating surface 43 is designed to have a pressure-receiving area corresponding to the pressure applied by the concave spherical surface 61, that is, when the pressure applied by the concave spherical surface 61 to the coating surface 43 is small, the coating surface 43 may have a small pressure-receiving area, and when the pressure applied by the concave spherical surface 61 to the coating surface 43 is increased, the pressure-receiving area of the coating surface 43 is increased accordingly. Thus, the smooth coating surface 43 reduces the frictional resistance when the concave spherical surface 61 slides. Meanwhile, by planning a pressure bearing area corresponding to the bearing pressure on the coating surface 43, the stress area of the coating surface 43 is prevented from being damaged due to overlarge pressure intensity when the concave spherical surface 61 slides on the coating surface 43, and the reliability of long-term and repeated use of the special friction pair of the curved surface sliding block 6 and the curved surface coating under high pressure can be obviously improved.
The coating layer is provided with a smooth coating surface 43, and the outer layer of the coating layer is made of TPFE material with self-lubricating property. The TPFE material not only has very good self-lubricating property, but also has very good wear resistance; meanwhile, the elastic material can have certain elasticity when reaching a certain thickness or volume, and can generate elastic deformation capable of restoring to the original shape. Thus, not only can the coating surface 43 with low friction coefficient and wear resistance be manufactured, but also a pressure receiving surface 45 can be formed around the pressure receiving point 44 of the coating surface 43, and the pressure of the pressure receiving point 44 can be obviously reduced.
The maximum pressure area of the coating surface 43, which is designed to receive the maximum pressure of the concave spherical surface 61, is such that the entire concave spherical surface 61 can contact the coating surface 43, and the coating surface 43 can receive the maximum pressure applied by the concave spherical surface 61 with the maximum area.
The whole concave spherical surface 61 can contact the coating surface 43, and the curved surface slide block 6 and the TPFE coating are simultaneously elastically deformed when the concave spherical surface 61 of the curved surface slide block 6 applies pressure to the coating surface 43 of the TPFE coating to form an interaction force, and the distance 8 between the concave spherical surface 61 and the coating surface 43 is controlled.
The specific method is that the curved surface slide block 6 is made of elastic polymer composite material, and meanwhile, the thickness of the coating is set to be 40-70 um; when the curved surface slide block 6 and the lining block 5 are rigidly connected, the distance 8 between the concave spherical surface 61 of the curved surface slide block 6 and the coating surface 43 of the mandrel ball 41 is smaller than 100 um.
The curved surface slide block 6 made of the elastic polymer composite material can generate smaller recoverable elastic deformation, and the rigidity of the curved surface slide block is actually larger than that of the TPFE coating.
The coating thickness set to 40-70 um here actually comprises an adhesive layer, e.g. 40um, 55um, 70um, brushed between the mandrel ball 41 and the TPFE coating. The setting is to meet the abrasion loss of the TPFE coating in the whole life cycle and to enable the whole coating to generate a set deformation amount.
When the curved surface slide block 6 and the pad 5 are rigidly connected, the curved surface slide block 6 cannot be bent and deformed integrally under the constraint of the pad 5.
The principle of the method is as follows:
when the pad 5 presses the curved surface slide block 6 with smaller pressure, the positive pressure point 63 of the concave spherical surface 61 presses the pressure point 44 of the coating surface 43, the pressure point 44 is sunken inward, the coating near the pressure point 44 is bulged toward the coating surface 43 under the action of stress, and a pressure surface 45 which surrounds the pressure point 44 and is in contact with the concave spherical surface 61 is formed; meanwhile, the positive pressure point 63 of the concave spherical surface 61 is recessed into the block body of the curved surface slider 6, and the block body near the positive pressure point 63 is raised toward the concave spherical surface 61 under the action of stress, so as to form a pressing surface 64 surrounding the positive pressure point 63 and contacting with the pressure receiving surface formed on the coating surface 43. Thus, the TPFE coating and the elastic deformation of the curved slider 6 form the pressing surface 64 and the pressure receiving surface 45 matching therewith.
As the rubber ball joint is subjected to greater loads, the areas of the pressing surface 64 and the pressure receiving surface 45 are correspondingly increased.
Since the spacing 8 between the concave spherical surface 61 and the coating surface 43 of the mandrel ball 41 is less than 100um, the spacing 8 between the periphery of the concave spherical surface 61 and the coating surface 43 has been further reduced to below 30um when the positive pressure point 63 of the concave spherical surface 61 contacts the coating surface 43. Therefore, when the load applied to the rubber ball joint is continuously increased to a certain value, the stress deforms the coating surface 43 and the concave spherical surface 61 enough to press the entire concave spherical surface 61 on the coating surface 43, so that the coating surface 43 obtains the maximum pressed area.
The method further comprises chamfering the periphery of the concave spherical surface 61 of the curved slider 6 to form a chamfered surface 65 at the periphery of the concave spherical surface 61, so as to avoid scraping the coating surface 43 by the edge of the concave spherical surface 61 when the coating surface 43 deforms and sags under the pressure of the concave spherical surface 61 and the concave spherical surface 61 slides on the coating surface 43.
Example two
As shown in fig. 7 to 10, the rubber ball hinge for reducing the friction between the curved surface slider and the curved surface coating is also to use a polymer composite material with elasticity to manufacture the curved surface slider 6, and set the thickness of the coating to be 40 to 70um, which is different from the first embodiment in that: when the distance 8 between the concave spherical surface 61 of the curved surface slide block 6 and the coating surface 43 of the mandrel ball 41 is set to be 100-300 um, the curved surface slide block 6 can be further bent when being stressed. The purpose is to further bend the curved surface slide block 6 to make the spherical radius of the concave spherical surface 61 close to the spherical radius of the coating surface 43, and then combine the concave spherical surface 61 and the micro-deformation generated by the coating surface 43 under pressure to make the whole concave spherical surface 61 press on the coating surface 43, so that the coating surface 43 obtains the maximum pressure area.
The curved surface slide block 6 can be further bent when stressed, a rubber interlayer 7 is additionally arranged between the curved surface slide block 6 and the lining block 5 through vulcanization, and the thickness in the middle of the rubber interlayer 7 is larger than the thickness at two ends. The principle is as follows:
the lining block 5 pushes the curved surface slide block 6 through the rubber interlayer 7, so that the positive pressure point 63 of the concave spherical surface 61 of the curved surface slide block 6 is contacted with the pressed point 44 of the coating surface 43;
the pad block 5 continuously applies pressure to the curved surface slide block 6 through the rubber interlayer 7, and the curved surface slide block 6 applies pressure to the pressure point 44 of the coating surface 43 through the positive pressure point 63 of the concave spherical surface 61; this process takes place simultaneously with the following three changes:
1. the acting force and the reacting force between the positive pressure point 63 and the pressure point 44 respectively deform the concave spherical surface 61 in the area of the positive pressure point 63 and the coating surface 43 in the area of the pressure point 44 to form a pressure surface 64 and a pressure surface 45.
2. The rubber interlayer 7 is simultaneously subjected to the positive pressure of the pad 5 and the reaction force of the curved surface slide 6, and the rubber interlayer 7 is compressed. Because the thickness in the middle of the rubber interlayer 7 is larger than the thickness at the two ends, when the pressure is continuously increased, the two ends of the rubber interlayer 7 reach the compression limit at first, and then the two ends of the curved surface slide block 6 can not be close to the two ends of the filler block 5.
3. Since the positive pressure point is always located in the top area of the concave spherical surface 61, the reaction force of the coating surface 43 actually radially outward presses the middle part of the inner side of the curved surface slide block 6; when the two ends of the curved surface slide block 6 are limited by the two ends of the lining block 5 by the continuously increased pressure and can not be close to the two ends of the lining block 5 any more, because the thickness of the middle of the rubber interlayer 7 is larger than the thickness of the two ends, that is, the curved surface slide block 6 can also continuously compress the middle part of the rubber interlayer 7, then the continuously increased pressure can make the middle part of the inner side of the curved surface slide block 6 receive larger radial outward reaction force from the coating surface 43, so that the curved surface slide block 6 is forced to further bend until the whole concave spherical surface 61 is attached to the coating surface 43, and the coating surface 43 obtains the largest compression area.
The thickness of the middle of the rubber interlayer 7 is larger than the thickness of the two ends, the outer arc surface of the curved surface slide block 6 and the outer arc surface of the lining block 5 are kept unchanged, and the curvature of the inner arc surface 51 of the lining block 5 is reduced. One way is to bore and mill the inner arc surface 51 of the lining block 5, wherein the middle part of the inner arc surface 51 is deeply bored and milled, and the depth is gradually reduced to the end part to be cut.
The thickness of the middle of the rubber interlayer 7 is larger than the thickness of the two ends, so that the curvature of the outer arc surface 62 of the curved surface slide block 6 is increased while the inner arc surface 51 of the pad 5 is kept unchanged. One mode is to mill the outer arc surface 62 of the curved surface slide block 6, wherein the middle part of the outer arc surface 62 is thickened and milled, and the middle part is gradually shallow to the end part to be discharged.
In this embodiment, in the case where the distance 8 between the concave spherical surface 61 of the curved surface slider 6 and the coating surface 43 of the core shaft ball 41 is set to 100 to 300um, by providing the rubber interlayer 7 having a thickness greater at the middle section than at both ends between the curved surface slider 6 and the pad 5, the following two unexpected effects are obtained while the coating surface 43 can obtain the largest pressed area: firstly, when encountering impact load suddenly at the rubber ball pivot, rubber intermediate layer 7 can play fine cushioning effect, alleviates the rigid impact of curved surface slider 6 to coating face 43 to a great extent to make coating face 43 obtain better protection. And secondly, the rubber interlayer 7 plays a good role in vibration and noise reduction, and can obviously reduce the noise generated when the curved surface slide block 6 impacts the coating surface 43 and rubs with the coating surface 43.
The above-described embodiments are intended to illustrate the invention more clearly and should not be construed as limiting the scope of the invention covered thereby, any modification of the equivalent should be considered as falling within the scope of the invention covered thereby.
Claims (7)
1. The utility model provides a reduce rubber ball pivot of frictional force between curved surface slider and curved surface coating, includes dabber (4), overcoat (1) and is located rubber layer (2) between dabber (4) and overcoat (1), its characterized in that: arranging a cavity (3) in a rubber layer (2) between a mandrel (4) and a jacket (1) which are positioned at the upper part of the mandrel (4) in a rubber spherical hinge and in the rubber layer (2) between the mandrel (4) and the jacket (1) which are positioned at the lower part of the mandrel (4), arranging a curved surface sliding block (6) the outer side of which is fixed with the jacket (1) in the cavity (3), and arranging a lining block (5) connected with the curved surface sliding block (6) on the outer side of the curved surface sliding block (6); processing the curved surface on the inner side of the curved surface slide block (6) into a concave spherical surface (61) with spherical surface characteristics; arranging a coating on an outer spherical surface (42) of a mandrel ball (41) with the same spherical surface characteristic and positioned in the cavity, and manufacturing the outer layer of the coating by a TPFE material with a self-lubricating characteristic; planning a pressure bearing area corresponding to the pressure bearing surface (61) on the coating surface (43) so that the whole concave spherical surface (61) can contact the coating surface (43) and the coating surface (43) can bear the maximum pressure applied by the concave spherical surface (61) in the maximum area; the friction resistance of the concave spherical surface (61) during sliding is reduced by arranging the smooth coating surface (43), and meanwhile, the stress area corresponding to the bearing pressure is planned on the coating surface (43), so that the stress area of the coating surface (43) is prevented from being damaged due to overlarge pressure when the concave spherical surface (61) slides on the coating surface (43); the whole concave spherical surface (61) can contact the coating surface (43), and the curved surface sliding block (6) and the TPFE coating are simultaneously elastically deformed when the concave spherical surface (61) of the curved surface sliding block (6) applies pressure to the coating surface (43) of the TPFE coating to form an interaction force, and the distance (8) between the concave spherical surface (61) and the coating surface (43) is controlled to realize the purpose.
2. The rubber ball pivot for reducing the friction force between the curved surface sliding block and the curved surface coating according to claim 1, wherein the curved surface sliding block (6) is made of an elastic polymer composite material, and meanwhile, the thickness of the coating is set to be 40-70 um; when the curved surface slide block (6) is rigidly connected with the lining block (5), the distance (8) between the concave spherical surface (61) of the curved surface slide block (6) and the coating surface (43) of the mandrel ball (41) is smaller than 100 um.
3. The rubber spherical hinge for reducing the friction force between the curved surface sliding block and the curved surface coating according to claim 1, wherein the curved surface sliding block (6) is made of a high polymer composite material with elasticity, and the thickness of the coating is set to be 40-70 um; when the distance (8) between the concave spherical surface (61) of the curved surface slide block (6) and the coating surface (43) of the mandrel ball (41) is set to be 100-300 um, the curved surface slide block (6) can be further bent when being stressed.
4. The rubber spherical hinge for reducing the friction force between the curved surface sliding block and the curved surface coating according to claim 3, wherein the curved surface sliding block (6) can be further bent when being stressed, a rubber interlayer (7) is additionally arranged between the curved surface sliding block (6) and the lining block (5) through vulcanization, and the thickness of the middle of the rubber interlayer (7) is larger than the thickness of the two ends.
5. A rubber ball pivot for reducing the friction between a curved surface slider and a curved surface coating according to claim 4, characterized in that the thickness of the middle of the rubber interlayer (7) is larger than the thickness of the two ends, the camber surface of the curved surface slider (6) and the camber surface of the lining block (5) are kept unchanged, and the curvature of the camber surface (51) of the lining block (5) is reduced.
6. A rubber ball hinge for reducing friction between a curved slider and a curved coating according to claim 4, wherein the thickness of the middle of the rubber interlayer (7) is larger than the thickness of the two ends, so that the inner arc surface (51) of the pad block (5) is kept unchanged, and the curvature of the outer arc surface (62) of the curved slider (6) is increased.
7. A rubber ball hinge for reducing friction between a curved slider and a curved coating according to any one of claims 1 to 6, wherein the periphery of the concave spherical surface (61) of the curved slider (6) is chamfered to prevent the edge of the concave spherical surface (61) from scratching the coating surface (43) when the coating surface (43) is deformed by the pressure of the concave spherical surface (61) and the concave spherical surface (61) slides on the coating surface (43).
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| CN202110936995.2A CN113669360B (en) | 2021-08-16 | 2021-08-16 | Rubber spherical hinge for reducing friction force between curved surface sliding block and curved surface coating |
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| CN202110936995.2A CN113669360B (en) | 2021-08-16 | 2021-08-16 | Rubber spherical hinge for reducing friction force between curved surface sliding block and curved surface coating |
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| CN113669360B true CN113669360B (en) | 2022-08-26 |
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| US4447094A (en) * | 1981-07-24 | 1984-05-08 | O & S Manufacturing Company | Prelubricated sealed bearings |
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| KR20140065699A (en) * | 2012-11-20 | 2014-05-30 | 주식회사 일진 | Ball joint and method of manufacturing the same |
| CN104411520A (en) * | 2012-06-29 | 2015-03-11 | 日进株式会社 | Ball joint |
| CN105952843A (en) * | 2016-06-27 | 2016-09-21 | 株洲时代新材料科技股份有限公司 | Method for improving vibration attenuation reliability of metal rubber joints and metal rubber joint assembly |
| CN208457031U (en) * | 2018-07-20 | 2019-02-01 | 株洲时代新材料科技股份有限公司 | A kind of structure for eliminating torsion bar system noise |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4447094A (en) * | 1981-07-24 | 1984-05-08 | O & S Manufacturing Company | Prelubricated sealed bearings |
| JPH06129460A (en) * | 1992-10-15 | 1994-05-10 | Toyoda Gosei Co Ltd | Vibro-isolating bush |
| CN104411520A (en) * | 2012-06-29 | 2015-03-11 | 日进株式会社 | Ball joint |
| KR20140065699A (en) * | 2012-11-20 | 2014-05-30 | 주식회사 일진 | Ball joint and method of manufacturing the same |
| CN105952843A (en) * | 2016-06-27 | 2016-09-21 | 株洲时代新材料科技股份有限公司 | Method for improving vibration attenuation reliability of metal rubber joints and metal rubber joint assembly |
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| CN113669360A (en) | 2021-11-19 |
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