阅读说明：本技术 一种非线性缓和变刚沙漏簧 (Nonlinear transition steel hourglass spring ) 是由 黄江彪 冯万盛 蒋仲三 罗俊 张玉祥 邓梦君 陈俊辉 于 2019-10-29 设计创作，主要内容包括：本发明公开了一种非线性缓和变刚沙漏簧,包括具有上弹性体的上减振组件和具有下弹性体的下减振组件,上弹性体具有用于非线性缓和变刚的上变刚件,下弹性体具有用于非线性缓和变刚的下变刚件；上弹性体还具有上部的上压胀体,上变刚件为上变刚托盘,上变刚托盘外周为环形的上变刚边；上压胀体的底部在上变刚边内与上变刚托盘连接；所述下弹性体还具有下部的下压胀体,所述下变刚件为下变刚托盘,下变刚托盘外周为环形的下变刚边；下压胀体的底部在下变刚边内与下变刚托盘连接。本发明的优点是：电车运行过程中实现垂向、纵向和横向非线性缓和变刚使乘客乘行的舒适感显著增强,列车车厢与车厢之间,车厢与转向架之间的协调性也明显增强。(The invention discloses a nonlinear moderate-stiffness hourglass spring, which comprises an upper vibration damping assembly with an upper elastic body and a lower vibration damping assembly with a lower elastic body, wherein the upper elastic body is provided with an upper stiffness piece for nonlinear moderate stiffness; the upper elastic body is also provided with an upper pressure expansion body at the upper part, the upper stiffening member is an upper stiffening tray, and the periphery of the upper stiffening tray is an annular upper stiffening edge; the bottom of the upper pressure expansion body is connected with the upper stiffening tray in the upper stiffening edge; the lower elastic body is also provided with a lower pressure expansion body at the lower part, the lower stiffening member is a lower stiffening tray, and the periphery of the lower stiffening tray is an annular lower stiffening edge; the bottom of the lower pressure expansion body is connected with the lower stiffening tray in the lower stiffening edge. The invention has the advantages that: the vertical, longitudinal and transverse non-linear relaxation and rigidity change is realized in the running process of the electric car, so that the comfort of passengers in riding is obviously enhanced, and the coordination between the train carriages and the bogie is also obviously enhanced.)

1. A non-linear gradual stiffening hourglass spring, characterized by: the damping device comprises an upper damping assembly (1) with an upper elastic body and a lower damping assembly (2) with a lower elastic body, wherein the upper elastic body is provided with an upper stiffening member for nonlinear mild stiffening, and the lower elastic body is provided with a lower stiffening member for nonlinear mild stiffening; the upper vibration damping assembly (1) and the lower vibration damping assembly (2) are connected up and down to form a vibration damping body with nonlinear gradual stiffness.

2. The non-linear gradual stiffening hourglass spring of claim 1, wherein: the upper elastic body is also provided with an upper pressure expansion body (3) at the upper part, the upper stiffening member is an upper stiffening tray (5) with an upward disc opening, and the periphery of the upper stiffening tray (5) forms an annular upper stiffening edge (51); the bottom of the upper pressure expansion body (3) is connected with the upper stiffening tray (5) in the upper stiffening edge (51); the lower elastic body is also provided with a lower pressure expansion body (4) at the lower part, the lower stiffening member is a lower stiffening tray (6) with a downward disk opening, and the periphery of the lower stiffening tray (6) forms an annular lower stiffening edge (61); the bottom of the lower pressure expansion body (4) is connected with the lower stiffening tray (6) in the lower stiffening edge (61).

3. The non-linear gradual stiffening hourglass spring of claim 2, wherein: an upper pressure expansion space (32) is arranged between the upper stiffening edge (51) and the periphery of the lower part of the upper pressure expansion body (3); and a lower expansion space (42) is formed between the lower stiffening edge (61) and the periphery of the upper part of the lower pressure expansion body (4).

4. The non-linear gradual stiffening hourglass spring of claim 3, wherein: the upper stiffening edge (51) is provided with an edge base I (52) and an edge I (53), and a height difference exists between the edge base I (52) and the edge I (53); the outer side surface of the upper stiffening edge (51) is an inverted cone-shaped surface; the inner side surface of the upper rigid side (51) is a concave arc-shaped upper inner arc surface (54) from the first side bottom (52) to the first edge (53); the lower stiffening edge (61) is provided with a second edge bottom (62) and a second edge (63), and a height difference exists between the second edge bottom (62) and the second edge (63); the outer side surface of the lower rigidifying side (61) is a conical surface; the inner side surface of the lower rigid side (61) is a concave arc-shaped lower inner arc surface (64) from the side bottom II (62) to the edge II (63).

5. The non-linear gradual stiffening hourglass spring of claim 4, wherein: the upper intrados (54) is sequentially divided into a no-load expansion section I (55), a full-load expansion section I (56) and an overload expansion section I (57) from the edge bottom I (52) to the edge I (53); the lower intrados (64) is sequentially divided into an unloaded bulging section II (65), a fully loaded bulging section II (66) and an overloaded bulging section II (67) from the edge bottom II (62) to the edge II (63).

6. The non-linear gradual stiffening hourglass spring of claim 5, wherein: the upper vibration reduction assembly (1) further comprises an upper limit stop disc (7) with an upward disc opening, an annular upper stop flange (71) is arranged on the periphery of the upper stop disc (7), and an upper stiffening tray (5) at the bottom of the upper elastic body is fixedly connected with the upper stop disc (7) in the upper stop flange (71); the lower vibration damping assembly (2) further comprises a limit limiting lower stop disc (8) with a disc opening facing downwards, an annular lower stop edge (81) is arranged on the periphery of the lower stop disc (8), and a lower stiffening tray (6) at the top of the lower elastic body is fixedly connected with the lower stop disc (8) in the lower stop edge (81).

7. The non-linear gradual stiffening hourglass spring of claim 6, wherein: an upper limit stiffening space (9) is arranged between the upper stop rib (71) and the upper stiffening rib (51); and a limit lower stiffening space (10) is arranged between the lower stopping edge (81) and the lower stiffening edge (61).

8. The non-linear gradual stiffening hourglass spring of claim 7, wherein: the thickness of the bottom edge I (52) of the upper stiffening edge (51) is larger than that of the edge I (53); the thickness of the bottom two (62) of the lower stiffened edge (61) is larger than that of the edge two (63).

9. The non-linear gradual stiffening hourglass spring of claim 8, wherein: the outer side surface of the upper variable rigid side (51) is a convex arc-shaped upper side outer arc surface (58) from the side bottom I (52) to the edge I (53); the outer side surface of the lower rigidifying side (61) is a convex arc-shaped lower outer arc surface (68) from the side bottom II (62) to the edge II (63).

10. The non-linear gradual stiffening hourglass spring of claim 9, wherein: the inner side surface of the upper stop flange (71) is a slope-shaped upward limit upper stiffening surface (72) from inside to outside; the inner edge surface of the lower stopping edge (81) is a downward slope-shaped lower-limit stiffening surface (82) from inside to outside.

Technical Field

The invention relates to a nonlinear transition steel hourglass spring, and belongs to the field of urban rail transit.

Background

The low-floor tramcar and the emerging intelligent rail train (the rail train without the ground) are gradually popularized and applied due to the advantages of low manufacturing cost, energy conservation, environmental protection, capability of running on urban ground roads, higher passenger capacity, riding comfort and stability than those of buses and the like.

However, the urban running track line has many curves and small radius, the starting and braking are frequent, the vertical, transverse and longitudinal deformation of the secondary suspension is large, meanwhile, the bogie needs to adopt a low-floor design for facilitating passengers to get on or off the train after the ground is parked, the bogie is generally compact in structure and small in mass, and the hourglass spring structure can better meet the special use requirements.

The rigidity of the hourglass spring has a direct relation to the running stability and safety of the train and the comfort of passengers in the train, and the rigidity of the hourglass spring is designed according to the load of the train, road conditions and the allowable speed of a line.

In actual operation, a low-floor train is always in an empty (no passengers or few passengers in the train), full (the number of passengers is in a rated range) or overload condition, and the three conditions have different requirements on the vertical, longitudinal and transverse rigidity of the hourglass spring.

In addition, the requirements for longitudinal and transverse rigidity of the hourglass spring are different when the same speed passes through curves with different radii and when the same speed passes through curves with the same radius.

Therefore, the hourglass spring needs to be stiffened to meet the stiffness requirements of the hourglass spring.

Disclosure of Invention

The invention mainly solves the technical problems that: the problem that the rigidity of the hourglass spring in the secondary suspension of the bogie of the ground low-floor electric car is poor in pertinence, and the problem that the rigidity of the hourglass spring is sharply enhanced after the pertinence design, and the nonlinear rigidity is also affected to influence the riding comfort is also solved.

Aiming at the problems, the technical scheme provided by the invention is as follows:

a non-linear gradual stiffening hourglass spring includes an upper damping assembly having an upper elastomer with an upper stiffening member for non-linear gradual stiffening, and a lower damping assembly having a lower elastomer with a lower stiffening member for non-linear gradual stiffening; the upper vibration damping assembly and the lower vibration damping assembly are connected up and down to form a vibration damping body with nonlinear gradual stiffness.

Further, the upper elastic body is also provided with an upper pressure expansion body at the upper part, the upper stiffening member is an upper stiffening tray with an upward disk opening, and the periphery of the upper stiffening tray forms an annular upper stiffening edge; the bottom of the upper pressure expansion body is connected with the upper stiffening tray in the upper stiffening edge; the lower elastic body is also provided with a lower pressure expansion body at the lower part, the lower stiffening member forms a lower stiffening tray with a downward disk opening, and the periphery of the lower stiffening tray is an annular lower stiffening edge; the bottom of the lower pressure expansion body is connected with the lower stiffening tray in the lower stiffening edge.

Furthermore, an upper pressure expansion space is formed between the upper stiffening edge and the periphery of the lower part of the upper pressure expansion body; and a lower pressure expansion space is formed between the lower stiffening edge and the periphery of the upper part of the lower pressure expansion body.

Further, the upper stiffened edge is provided with a first edge bottom and a first edge, and a height difference exists between the first edge bottom and the first edge; the outer edge surface of the upper stiffening edge is an inverted cone-shaped surface; the inner side surface of the upper rigid edge is a concave arc-shaped upper inner arc surface from the first edge bottom to the first edge; the lower stiffening edge is provided with a second edge bottom and a second edge, and a height difference exists between the second edge bottom and the second edge; the outer side surface of the lower variable-rigidity edge is a conical surface; the inner side surface of the lower rigidified edge is a concave arc-shaped lower inner arc surface from the second edge bottom to the second edge.

Furthermore, the upper intrados is sequentially divided into a no-load expansion section I, a full-load expansion section I and an overload expansion section I from the edge bottom I to the edge I; the lower intrados is sequentially divided into a no-load expansion section II, a full-load expansion section II and an overload expansion section II from the edge bottom II to the edge II.

Furthermore, the upper vibration damping assembly further comprises a limit upper stop disc with an upward disc opening, an annular upper stop flange is arranged on the periphery of the upper stop disc, and an upper stiffening tray at the bottom of the upper elastic body is fixedly connected with the upper stop flange in the upper stop flange; the lower vibration reduction assembly further comprises a limit limiting lower stop disc with a disc opening facing downwards, an annular lower stop flange is arranged on the periphery of the lower stop disc, and a lower stiffening tray at the top of the lower elastic body is fixedly connected with the lower stop disc in the lower stop flange.

Further, a limit upper stiffening space is arranged between the upper stop rib and the upper stiffening rib; and a lower limit stiffening space is arranged between the lower stop edge and the lower stiffening edge.

Further, the thickness of the first edge bottom of the upper stiffened edge is greater than that of the first edge; and the thickness of the second edge and the bottom of the lower stiffened edge is greater than that of the second edge.

Furthermore, the outer side surface of the upper stiffened edge is a convex arc-shaped upper outer arc surface from the first edge bottom to the first edge; the outer side surface of the lower rigidifying edge is a convex arc-shaped lower outer arc surface from the edge bottom II to the edge II.

Furthermore, the inner side surface of the upper stop flange is a slope-shaped upward limit upper rigid surface from inside to outside; the inner edge surface of the lower stopping edge is a slope-shaped downward-facing rigid surface from inside to outside.

The invention has the advantages that: the comfort of passengers is obviously enhanced in the running process of the electric car, and the coordination between the train carriage and the bogie and between the carriage and the bogie are also obviously enhanced.

Drawings

Fig. 1 is a schematic axial sectional structure diagram of a nonlinear gradual-change hourglass spring, which shows that an upper pressure expansion body and an upper rigidity changing tray are formed by different materials in a split manner and then are fixedly connected together, and a lower pressure expansion body and a lower rigidity changing tray are also formed by different materials in a split manner and then are fixedly connected together.

FIG. 2 is a schematic axial sectional structure view of a nonlinear gradual stiffening hourglass spring; the upper dilatant and the upper stiffening pallet are integrally formed from the same material, and the lower dilatant and the lower stiffening pallet are integrally formed from the same material.

Fig. 3 is a schematic cross-sectional structure of an upper stiffening pallet, in which the dotted lines are dividing lines rather than structural lines.

Fig. 4 is a schematic cross-sectional structure of a lower stiffening pallet, in which the dotted lines are dividing lines rather than structural lines.

Fig. 5 is a schematic view of the hourglass spring in its unloaded state, with the upper and lower dilators shown in phantom in their unstressed states.

Fig. 6 is a schematic view of the hourglass spring state when fully loaded, with the upper and lower dilators shown in phantom in their unstressed state.

Fig. 7 is a schematic view of the hourglass spring in an overloaded state, with the upper and lower dilators shown in phantom lines in an uncompressed state.

Fig. 8 is a schematic diagram showing the vertical extreme pressure state of the hourglass spring during overload, and the upper pressure expander and the lower pressure expander are in the non-pressure state as shown by dotted lines.

Fig. 9 is a schematic diagram showing the extreme compressed state of the hourglass spring in a certain horizontal direction during overload, and the upper and lower dilators are in an uncompressed state as shown by dotted lines.

In the figure: 1. an upper vibration reduction assembly; 2. a lower vibration reduction assembly; 3. an upper pressure expansion body; 31. an upper volume expansion cavity; 32. an upper pressure expansion space; 4. pressing the expansion body; 41. a lower expansion cavity; 42. pressing and expanding the space; 5. an upper stiffening tray; 51. an upper stiffened edge; 52. a first edge; 53. a first edge; 54. an upper inner arc surface; 55. a no-load expansion section I; 56. a first full-load expansion section; 57. an overload expansion section I; 58. an upper outer arc surface; 6. a lower stiffening tray; 61. lower stiffened edges; 62. a second side bottom; 63. a second edge; 64. the lower inner arc surface; 65. a no-load expansion section II; 66. a second full-load expansion section; 67. an overload expansion section II; 68. the lower outer arc surface; 7. an upper stop disc; 71. an upper stop flange; 72. an extreme upper stiffening surface; 8. a lower stop plate; 81. a lower stop flange; 82. a lower limit rigidified surface; 9. a stiffening space at the limit; 10. and rigidity changing space under the limit.

Detailed Description

The invention will now be described in its entirety with reference to the accompanying drawings:

as shown in figure 1, the hourglass spring with non-linear gradual stiffness or rigidity changing is used for supporting a carriage and providing vertical, longitudinal and transverse vibration damping for the carriage in the running process between a bogie and the carriage of an emerging intelligent tram bogie secondary suspension. The nonlinear gradual stiffening hourglass spring comprises an upper damping assembly 1 and a lower damping assembly 2.

As shown in fig. 1, 2 and 3, the upper vibration damping assembly 1 comprises an upper elastic body and an upper limit stop disc 7 with an upward disc opening; the upper elastic body comprises an upper pressure expansion body 3 at the upper part of the upper elastic body and an upper stiffening tray 5 with an upward disk opening at the bottom of the upper elastic body; the upper pressure expansion body 3 is a cup-shaped body with an upward cup mouth, and the diameter of the upper part of the upper pressure expansion body 3 is larger than that of the lower part of the upper pressure expansion body 3; the upper part of the upper pressure expansion body 3 is provided with an upper expansion cavity 31 with an upward opening; when the upper pressure expansion body 3 bears the weight of the carriage, the upper pressure expansion body 3 can be extruded to the periphery and the upper expansion cavity 31 while the upper pressure expansion body 3 is compressed downwards. The outer periphery of the upper stiffening pallet 5 is an upper stiffening edge 51, and the bottom of the upper expander 3 is connected with the upper stiffening pallet 5 in the upper stiffening edge 51. The upper stiffening tray 5 and the upper pressure expander 3 may be the same material or different elastic materials; when the upper stiffening tray 5 and the upper dilatant 3 are made of the same material, the upper stiffening tray 5 and the upper dilatant 3 are usually made by integral molding; when the upper stiffening tray 5 and the upper pressure-expanding body 3 are made of different elastic materials, the upper stiffening tray 5 and the upper pressure-expanding body 3 are manufactured in a split mode and connected in a vulcanization fixing mode. An upper pressure expansion space 32 is arranged between the upper stiffening edge 51 and the periphery of the lower part of the upper pressure expansion body 3; the upper stiffening edge 51 has an edge base one 52 and an edge one 53; the first edge 52 and the first edge 53 have a height difference; the outer edge surface of the upper stiffening edge 51 is a conical surface with an inverted cone shape; an upper intrados surface 54, of which the inner side surface of the upper stiffened edge 51 is concave from the edge bottom one 52 to the edge one 53; the upper intrados 54 is divided into an unloaded expansion section I55, a fully loaded expansion section I56 and an overloaded expansion section I57 from the edge bottom I52 to the edge I53 in sequence; the thickness of the first edge 52 of the upper stiffened edge 51 is greater than that of the first edge 53; the outer side surface of the upper stiffening edge 51 is an upper outer arc surface 58 in a convex arc shape from the edge bottom I52 to the edge I53; the periphery of the upper stop disc 7 is provided with an annular upper stop rib 71, and an upper stiffening tray 5 at the bottom of the upper elastic body is fixedly connected with the upper stop disc 7 in the upper stop rib 71; the upper stop rib 71 and the upper stiffening rib 51 have a limiting upper stiffening space 9 therebetween, and the inner edge surface of the upper stop rib 71 is a ramp-like upward limiting upper stiffening surface 72 from inside to outside.

As shown in fig. 1, 2 and 4, the lower vibration damping module 2 has the same components as the upper vibration damping module 1, and the components in the lower vibration damping module 2 have the same structures, shapes and functions as those of the components in the upper vibration damping module 1, but the components in the lower vibration damping module 2 are oriented in the opposite direction to those of the components in the upper vibration damping module 1, and the sizes of the components in the lower vibration damping module 2 and those of the components in the upper vibration damping module 1 may not be equal. The lower damping module 2 is constructed as follows:

the lower vibration damping assembly 2 comprises a lower elastic body and a limit limiting lower stop disc 8 with a disc opening facing downwards; the lower elastic body comprises a lower pressure expansion body 4 at the lower part of the lower elastic body and a lower stiffening tray 6 with a downward disc opening at the top of the lower elastic body; the lower pressure expansion body 4 is a cup-shaped body with a downward cup opening, and the diameter of the lower part of the lower pressure expansion body 4 is larger than that of the upper part of the lower pressure expansion body 4; the lower part of the lower pressure expansion body 4 is provided with a lower expansion cavity 41 with a downward opening; when the lower pressure expander 4 bears the weight of the carriage, the lower pressure expander 4 is compressed, and simultaneously, the lower pressure expander 4 is extruded to the periphery and the lower expansion cavity 41. The outer periphery of the lower rigidifying tray 6 is a lower rigidifying edge 61, and the top of the lower expander 4 is connected with the lower rigidifying tray 6 in the lower rigidifying edge 61. The lower stiffening tray 6 and the lower pressure expander 4 may be the same material or different elastic materials; when the lower stiffening tray 6 and the lower dilatant 4 are made of the same material, the lower stiffening tray 6 and the lower dilatant 4 are usually made by integral molding; when the lower stiffening tray 6 and the lower dilatant 4 are made of different elastic materials, the lower stiffening tray 6 and the lower dilatant 4 are manufactured separately and then connected by a vulcanization and fixing mode. A lower pressure expansion space 42 is arranged between the lower stiffening edge 61 and the periphery of the upper part of the lower pressure expansion body 4; the lower stiffening edge 61 is provided with a second edge base 62 and a second edge 63; the second edge 62 and the second edge 63 have a height difference; the outer side surface of the lower stiffening edge 61 is a conical surface; the inner side surface of the lower rigidified edge 61 is a concave arc-shaped lower inner arc surface 64 from the second edge base 62 to the second edge 63; the lower intrados 64 is divided into a no-load expansion section II 65, a full-load expansion section II 66 and an overload expansion section II 67 from the bottom II 62 to the edge II 63 in sequence; the thickness of the bottom II 62 of the lower stiffened edge 61 is greater than that of the edge II 63; the outer side surface of the lower stiffening edge 61 is a convex arc-shaped lower outer arc surface 68 from the edge bottom II 62 to the edge II 63; the periphery of the lower stop disc 8 is provided with an annular lower stop edge 81, and the lower stiffening tray 6 at the top of the lower elastic body is fixedly connected with the lower stop disc 8 in the lower stop edge 81; the lower stop edge 81 and the lower stiffening edge 61 have a lower limiting stiffening space 10 therebetween, and the inner surface of the lower stop edge 81 is a downward limiting stiffening surface 82 in a ramp shape from inside to outside.

The upper damping assembly 1 and the lower damping assembly 2 are fixedly connected through an upper stop disc 7 and a lower stop disc 8 to form the nonlinear gradual-change rigidity hourglass spring. The upper stop disc 7 and the lower stop disc 8 are steel hard discs, and the hourglass spring assembled by neglecting the upper stop disc 7 and the lower stop disc 8 is dumbbell-shaped with two large ends and a small middle.

Nonlinear gradual stiffening hourglass spring's nonlinear gradual stiffening principle:

the hourglass spring bears the weight of the carriage on the bogie and provides vertical vibration damping, and provides horizontal vibration damping, i.e. longitudinal vibration damping and vertical vibration damping, when the train is started, accelerated, decelerated and braked or passes through a curve during variable speed operation.

As shown in fig. 1-4, when the nonlinear gradual-change hourglass spring standing on the bogie is heavily pressed by a train carriage, the height of the hourglass spring is reduced, and an upper pressure expansion body 3 and a lower pressure expansion body 4 of the hourglass spring are respectively extruded to an upper accommodating expansion cavity 31 and a lower accommodating expansion cavity 41 and are mainly extruded to the periphery of the hourglass spring; when the pressure applied to the hourglass spring by a carriage is suddenly increased, the upper pressure expansion body 3 and the lower pressure expansion body 4 are quickly axially compressed and simultaneously extruded out of the periphery, the pressure is limited by the upper stiffening tray 5 and the lower stiffening tray 6, the extruded parts of the upper pressure expansion body 3 and the lower pressure expansion body 4 are forced to overflow from the upper stiffening edge 51 of the upper stiffening tray 5 and the lower stiffening edge 61 of the lower stiffening tray 6 respectively, the upper pressure expansion space 32 between the upper stiffening edge 51 and the upper pressure expansion body 3 and the lower pressure expansion space 42 between the lower stiffening edge 61 and the lower pressure expansion body 4 are gradually filled, and the integral hourglass spring, particularly the middle section of the hourglass spring, is shortened, compacted and thickened, so that the vertical stiffness and the horizontal stiffness of the hourglass spring are increased. This increase in stiffness is a stiffening of the hourglass spring and, conversely, a weakening of the hourglass spring. The upper stiffening side 51 of the upper stiffening tray 5 and the lower stiffening side 61 of the lower stiffening tray 6 are provided, so that the stiffening becomes nonlinear stiffening to cope with the impact force in a certain direction instantaneously received by the hourglass spring.

However, even if the hourglass spring is momentarily subjected to impact forces in a certain direction, such non-linear stiffness should be avoided as much as possible to ensure the smoothness of the vehicle operation and the comfort of the passengers. Therefore, the inner side surfaces of the upper stiffening edge 51 and the lower stiffening edge 61 are both arc-shaped inner concave surfaces so as to prevent the inner side surfaces from forming a break angle, and the diameter of the whole edge base I52 is smaller than that of the whole edge base I53, and the diameter of the whole edge base II 62 is smaller than that of the whole edge base II 63, so that the included angle between the inner side surfaces of the upper stiffening edge 51 and the lower stiffening edge 61 and the horizontal plane is reduced, and the nonlinear stiffening becomes nonlinear mild stiffening.

The present invention is further described below.

As shown in fig. 1, a non-linear moderate-stiffness hourglass spring includes an upper damping block 1 having an upper elastic body with an upper stiffening member for non-linear moderate stiffness and a lower damping block 2 having a lower elastic body with a lower stiffening member for non-linear moderate stiffness; the upper damping unit 1 and the lower damping unit 2 are connected up and down to form a damping body having a nonlinear stiffness reducing function.

As shown in fig. 2, the upper elastic body further has an upper pressure expander 3 at the upper part, the upper stiffening member is an upper stiffening tray 5 with an upward disk mouth, and the outer periphery of the upper stiffening tray 5 is an annular upper stiffening edge 51; the bottom of the upper pressure expander 3 is connected with the upper stiffening tray 5 in the upper stiffening edge 51; the lower elastic body is also provided with a lower pressure expansion body 4 at the lower part, the lower stiffening member is a lower stiffening tray 6 with a downward disk opening, and the periphery of the lower stiffening tray 6 is an annular lower stiffening edge 61; the bottom of the lower expander 4 is connected to the lower rigidifying tray 6 within the lower rigidifying rim 61. The upper rigidifying tray 5 and the upper rigidifying side 51 thereof, and the lower rigidifying tray 6 and the lower rigidifying side 61 thereof are provided in order to restrict the upper dilators 3 and the lower dilators 4 from being pushed out to the outer circumference, thereby causing nonlinear rigidification of the upper dilators 3 and the lower dilators 4. In practice, the upper stiffening side 51 of the upper stiffening tray 5 is made integral with the upper stiffening tray 5, and the lower stiffening side 61 of the lower stiffening tray 6 is also made integral with the lower stiffening tray 6.

As shown in fig. 5, an upper bulge space 32 is formed between the upper stiffening edge 51 and the outer periphery of the lower part of the upper bulge 3; the lower stiffening edge 61 and the outer periphery of the upper part of the lower bulge 4 form a lower bulge space 42. The upper pressure expansion space 32 is a space occupied by the pressure expansion extrusion of the upper pressure expansion body 3, and is also a controllable space which is not linearly rigid. Likewise, the effect of the lower bulge space 42 on the lower bulge 4 is also the same.

2-4, the upper stiffening edge 51 has a first edge 52 and a first edge 53, with a height difference between the first edge 52 and the first edge 53; the outer edge surface of the upper stiffening edge 51 is an inverted cone-shaped surface; an upper intrados surface 54, of which the inner side surface of the upper stiffened edge 51 is concave from the edge bottom one 52 to the edge one 53; the lower stiffening edge 61 is provided with a second edge base 62 and a second edge 63, and a height difference exists between the second edge base 62 and the second edge 63; the outer side surface of the lower stiffening edge 61 is a conical surface; the inner side surface of the lower rigidifying edge 61 is a concave arc-shaped lower intrados surface 64 from the second edge 62 to the second edge 63. The arrangement is to form a slope surface from bottom to top and from inside to outside on the inner side surface of the upper stiffening side 51, and in practical application, the included angle between the slope surface and the horizontal plane is small, so as to facilitate implementing nonlinear mild stiffening. The inner edge surface is arranged by adopting a concave arc-shaped cambered surface, so that the inner edge surface is prevented from forming a break angle, and nonlinear mild stiffening is also implemented. The inner edge surface of the lower stiffener 61 is also arranged to be the same as the inner edge surface of the upper stiffener 51.

The upper intrados 54 is divided into an unloaded expansion section I55, a fully loaded expansion section I56 and an overloaded expansion section I57 from the edge bottom I52 to the edge I53 in sequence; the lower intrados 64 is divided into a no-load expansion section II 65, a full-load expansion section II 66 and an overload expansion section II 67 from the bottom II 62 to the edge II 63 in sequence.

The significance of the above arrangement is that:

no load: as shown in fig. 2 and 5, when the train car is in an empty or low-passenger condition, the upper inflatable body 3 is inflated and extruded out of the upper inflatable space 32 and completely presses the empty inflatable section one 55. Similarly, the lower pressure body 4 is pressed and extruded toward the lower pressure space 42 and presses the second unloaded pressure section 65 completely.

Under the condition, if the train runs on uneven roads, after the train sinks, the bogie suddenly rises to enable the hourglass spring to be instantly stressed by strong pressure applied by the carriage, and the upper pressure expansion body 3 is further pressed and expanded towards the upper pressure expansion space 32 to be extruded out, so that the vertical rigidity of the upper pressure expansion body is enhanced. However, the bulge extrusion process is limited by the gradual rise of the upper intrados 54, which forces the upper bulge 3 to become non-linearly rigid. As described above, since the ascending slope of the upper intrados surface 54 is gentle, the nonlinear stiffening is a nonlinear gradual stiffening.

Under the condition, if the train enters a curve or is suddenly braked and decelerated, the carriage applies a horizontal force to the upper pressure expansion body 3, and the upper pressure expansion body 3 is extruded towards the stressed direction. Also, this bulge extrusion process is limited by the gradual rise of the upper intrados 54, resulting in a responsive non-linear and non-linear gradual stiffening of the upper bulge 3. This process also produces the same non-linear mild stiffening of the lower dilators 4 as the upper dilators 3.

Full load: as shown in fig. 2 and 6, when the train car is in a full condition, the upper expander 3 is extruded toward the upper expander space 32 and presses a full expander section 56 partially or completely. Similarly, the lower pressure body 4 is pressed and extruded toward the lower pressure space 42 and presses the second full pressure section 66 completely.

Under the condition, if the train runs on uneven roads, after the train sinks, the bogie suddenly rises to enable the hourglass spring to be instantly subjected to strong pressure applied by the carriage, and the upper pressure expansion body 3 is further pressed, expanded and extruded to the upper pressure expansion space 32 to enhance the vertical rigidity of the upper pressure expansion body. This bulge extrusion process is limited by the gradual rise of the upper intrados 54, forcing the upper bulge 3 to become non-linearly rigid. As described above, since the ascending slope of the intrados is still gentle, the nonlinear stiffening is still gentle. The same is true of the lower dilators 4.

Under the condition, if the train enters a curve or is suddenly braked and decelerated, the carriage applies a horizontal force to the upper pressure expansion body 3, and the upper pressure expansion body 3 is extruded towards the stressed direction. Again, this bulge extrusion process is limited by the gradual rise of the upper intrados 54, resulting in a responsive non-linear stiffening of the upper bulge 3, and still a non-linear gradual stiffening. This process also produces the same non-linear mild stiffening of the lower dilators 4 as the upper dilators 3.

Overload: as shown in fig. 2 and 7, when the train car is overloaded, such as during an early peak condition, the upper inflatable body 3 is inflated and extruded out of the upper inflatable space 32 and presses a portion 57 of the overloaded inflated section partially or completely. Similarly, the lower pressure body 4 is pressed and extruded toward the lower pressure space 42 and presses the second full pressure section 66 completely.

Under the condition, if the train runs on uneven roads, after the train sinks, the bogie suddenly rises to enable the hourglass spring to be instantly subjected to strong pressure applied by the carriage, and the upper pressure expansion body 3 is further pressed, expanded and extruded to the upper pressure expansion space 32 to enhance the vertical rigidity of the upper pressure expansion body. This bulge extrusion process continues to be limited by the gradual rise of the upper intrados 54, forcing the upper bulge 3 to become non-linearly rigid. The degree of this non-linear stiffening is less gradual since the rising slope of the upper intrados 54 is no longer gradual. The same is true of the lower dilators 4.

Under the condition, if the train enters a curve or is suddenly braked and decelerated, the carriage applies a horizontal force to the upper pressure expansion body 3, and the upper pressure expansion body 3 is extruded towards the stressed direction. Also, this bulge extrusion process is limited by the gradual rise of the upper intrados 54, resulting in a responsive non-linear stiffening of the upper bulge 3, which is less gradual since the rising intrados slope is no longer gradual. The same is true of the lower dilators 4.

As shown in fig. 1 and 2, the upper vibration damping module 1 further includes a limit upper stop disc 7 with an upward disc opening, an annular upper stop flange 71 is arranged on the periphery of the upper stop disc 7, and an upper stiffening tray 5 at the bottom of the upper elastic body is fixedly connected with the upper stop flange 7 in the upper stop flange 71; the lower vibration damping assembly 2 further comprises a limit limiting lower stop disc 8 with a downward disc opening, an annular lower stop edge 81 is arranged on the periphery of the lower stop disc 8, and the lower stiffening tray 6 at the top of the lower elastic body is fixedly connected with the lower stop disc 8 in the lower stop edge 81. The hourglass spring mainly implements strong stopping under the condition of vertical and horizontal limit stress in the overload condition so as to ensure the safety of train operation.

An upper limit stiffening space 9 is arranged between the upper stop rib 71 and the upper stiffening rib 51; the lower stop edge 81 and the lower stiffening edge 61 have a limiting lower stiffening space 10 therebetween. Therefore, the upper stiffening edge 51 still has a stiffening space for pressing, expanding and extruding the upper stopping edge 71 when the vertical and horizontal forces are applied under the overload condition.

As shown in fig. 3 and 4, the thickness of the first edge 52 of the upper stiffened edge 51 is greater than that of the first edge 53; the thickness of the bottom two 62 of the lower stiffened edge 61 is greater than the thickness of the edge two 63. The arrangement is that the thickness of the stiffened edge of the overload bulging section one 57 close to the edge one 53 is thinned, so that the stiffened edge can deform outwards when stressed, and the vertical and horizontal non-linear stiffness of the upper bulge body 3 under the overload condition is alleviated. The same applies to the lower stiffening edge 61, as does its function.

2-4, the outer side surface of the upper stiffening edge 51 is a convex arc-shaped upper camber surface 58 from the edge base one 52 to the edge one 53; the outer side surface of the lower stiffening edge 61 is a convex lower outer arc surface 68 from the second edge 62 to the second edge 63.

As shown in fig. 2, the inner edge surface of the upper stop rib 71 is a ramp-shaped upper limit stiffening surface 72 from inside to outside; the inner edge surface of the lower stop edge 81 is a downward slope-shaped lower-limit stiffening surface 82 from inside to outside. The above-described arrangement is a preferable arrangement for further reducing the nonlinear stiffness in the overload condition as much as possible.

As shown in fig. 2 and 8, according to the above arrangement, when the vehicle bumps seriously due to the road irregularity in the overload state, the hourglass spring receives the limit pressure of the vehicle compartment, the upper dilatator 3 instantaneously presses the upper stiffening rib 51 to the upper stop rib 71 through the limit upper stiffening space 9, and the upper dilatator 3 is subjected to the hard stop by the upper stop rib 71. At the same time, the lower dilatator 4 instantaneously presses the lower stiffening rib 61 against the lower stop rib 81 through the lower stiffening space 10, and the lower dilatator 4 is hard stopped by the lower stop rib 81. Although the time is short, the relevant arrangement still plays an important role in the vertical nonlinear gradual stiffening.

As shown in fig. 2 and 9, according to the above arrangement, when the train enters a curve or a sudden speed change such as an emergency brake occurs in an overload situation, the hourglass spring receives a limit pressure in one direction applied by the train car, the upper dilatator 3 instantaneously presses the upper stiffening side 51 against the upper stop rib 71 in one direction through the limit upper stiffening space 9, and the upper dilatator 3 is hard stopped by the upper stop rib 71. At the same time, the lower dilatator 4 instantaneously presses the lower stiffening rib 61 against the lower stopping rib 81 in one direction through the lower stiffening space 10, and the lower dilatator 4 is hard stopped by the lower stopping rib 81. This process, although short in time, still plays an important role in the level of non-linear relaxation and stiffness.