CN114211921A - Double-cross-arm independent suspension system for ultra-heavy vehicle - Google Patents
Double-cross-arm independent suspension system for ultra-heavy vehicle Download PDFInfo
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- CN114211921A CN114211921A CN202111431638.7A CN202111431638A CN114211921A CN 114211921 A CN114211921 A CN 114211921A CN 202111431638 A CN202111431638 A CN 202111431638A CN 114211921 A CN114211921 A CN 114211921A
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- pin shaft
- cross arm
- spring
- arm
- cross
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- 239000000725 suspension Substances 0.000 title claims abstract description 36
- 238000009792 diffusion process Methods 0.000 claims abstract description 11
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- 238000007789 sealing Methods 0.000 claims description 43
- 239000002184 metal Substances 0.000 claims description 12
- 229910052751 metal Inorganic materials 0.000 claims description 12
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 3
- 229920000459 Nitrile rubber Polymers 0.000 claims description 3
- 229910052802 copper Inorganic materials 0.000 claims description 3
- 239000010949 copper Substances 0.000 claims description 3
- 230000001050 lubricating effect Effects 0.000 description 11
- 239000004519 grease Substances 0.000 description 10
- 230000009191 jumping Effects 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000009977 dual effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 102100024059 A-kinase anchor protein 8-like Human genes 0.000 description 1
- 101000833668 Homo sapiens A-kinase anchor protein 8-like Proteins 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 238000010009 beating Methods 0.000 description 1
- 230000003749 cleanliness Effects 0.000 description 1
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- JEIPFZHSYJVQDO-UHFFFAOYSA-N iron(III) oxide Inorganic materials O=[Fe]O[Fe]=O JEIPFZHSYJVQDO-UHFFFAOYSA-N 0.000 description 1
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G3/00—Resilient suspensions for a single wheel
- B60G3/18—Resilient suspensions for a single wheel with two or more pivoted arms, e.g. parallelogram
- B60G3/20—Resilient suspensions for a single wheel with two or more pivoted arms, e.g. parallelogram all arms being rigid
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
- B60G11/26—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs
- B60G11/27—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs wherein the fluid is a gas
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
- B60G11/26—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs
- B60G11/28—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs characterised by means specially adapted for attaching the spring to axle or sprung part of the vehicle
Abstract
The invention relates to a double-cross-arm independent suspension system for an extra-heavy vehicle, wherein a lower cross arm assembly comprises a first support arm and a second support arm which are oppositely arranged, the first support arm is connected with the second support arm into a whole through an arm shoulder, the end part of the first support arm and the end part of the second support arm are respectively provided with a pin shaft hole, the two pin shaft holes are coaxially arranged, a second cross arm pin shaft penetrates through the pin shaft holes to hinge the lower cross arm assembly on a vehicle frame, an oil inlet channel is drilled in the cross arm pin shaft along the axial direction, oil outlet channels penetrating through the first cross arm pin shaft and the second cross arm pin shaft along the radial direction are respectively drilled on the outer peripheral walls of the first cross arm pin shaft and the second cross arm pin shaft, the oil outlet channels are communicated with the oil inlet channels, annular diffusion grooves are respectively formed in the circumferential directions of the first cross arm pin shaft and the second cross arm pin shaft, and are communicated with oil outlets at two sides of the oil outlet channels. The invention is suitable for the chassis of the ultra-heavy vehicle and effectively solves the problem that the cross arm pin shaft is difficult to lubricate and disassemble.
Description
Technical Field
The invention relates to the technical field of vehicle suspensions, in particular to a double-cross-arm independent suspension system for an ultra-heavy vehicle.
Background
The double-cross arm independent suspension system comprises an upper cross arm assembly and a lower cross arm assembly. The upper cross arm assembly and the lower cross arm assembly are main bearing structural parts of a suspension system, and have the functions and effects of connecting wheels and a frame, determining the kinematics law of up-and-down jumping of the wheels and bearing lateral loads, longitudinal loads and partial vertical loads transmitted from the ground to the frame. The lower cross arm assembly is a lower guide mechanism of the suspension, and the outer side of the lower cross arm assembly is connected with the lower connecting inner side of a steering knuckle of the wheel set and the frame. The hydro-pneumatic spring is connected between the lower cross arm and the frame and bears all the sprung mass. The lower cross arm assembly has large bearing capacity, and has higher requirement on the strength of the lower cross arm assembly under the overload working condition, the sharp turning working condition and the emergency braking working condition. In addition, the load of the cross arm pin shaft of the lower cross arm assembly and the frame, and the load of the cross arm pin shaft of the lower cross arm assembly and the hydro-pneumatic spring are large, lubricating grease is difficult to fill at the cross arm pin shaft of the lower cross arm assembly and the frame, and the cross arm pin shaft is difficult to disassemble and assemble after long-term running.
Disclosure of Invention
The invention innovatively provides a double-cross-arm independent suspension system for an extra-heavy vehicle, which is applicable to an extra-heavy vehicle chassis and effectively solves the problems of difficult lubrication and disassembly and assembly of a cross-arm pin shaft.
In order to solve the problems in the prior art, the invention provides a double-cross arm independent suspension system for an extra-heavy vehicle, which comprises an upper cross arm assembly, a lower cross arm assembly and an oil-gas spring, wherein the inner end of the upper cross arm assembly is hinged with a vehicle frame through a first cross arm pin shaft, the inner end of the lower cross arm assembly is hinged with the vehicle frame through a second cross arm pin shaft, the outer ends of the upper cross arm assembly and the lower cross arm assembly are respectively connected with a wheel set through spherical hinges, the upper end of the oil-gas spring is connected with the vehicle frame through an upper spring pin shaft, the lower end of the oil-gas spring is connected with the lower cross arm assembly through a lower spring pin shaft, the lower cross arm assembly comprises a first support arm and a second support arm which are arranged oppositely, the first support arm is connected with the second support arm into a whole through an arm shoulder, and the end part of the first support arm and the end part of the second support arm are both provided with a pin shaft hole, the two pin shaft holes are arranged coaxially, the second cross arm pin shaft penetrates through the pin shaft holes to hinge the lower cross arm assembly on the frame, oil inlet channels are drilled in the first cross arm pin shaft and the second cross arm pin shaft along the axial direction, oil outlet channels penetrating through the cross arm pin shaft are drilled in the outer peripheral walls of the first cross arm pin shaft and the second cross arm pin shaft along the radial direction, the oil outlet channels are communicated with the oil inlet channels, annular diffusion grooves are formed in the outer peripheral walls of the first cross arm pin shaft and the second cross arm pin shaft along the circumferential direction, and the annular diffusion grooves are communicated with oil outlets on two sides of the oil outlet channels.
Furthermore, the invention relates to a double-wishbone independent suspension system for an extra-heavy vehicle, wherein a first bimetal bearing and a sealing ring are arranged in a pin shaft hole, the first bimetal bearing is in interference fit with the pin shaft hole, the sealing ring is coaxially arranged at the outer end of the first bimetal bearing, a first metal gasket is arranged at the outer end of the sealing ring, and the first metal gasket is fixed on a first support arm or a second support arm through a first fixing pin.
Furthermore, the double-cross-arm independent suspension system for the ultra-heavy vehicle comprises a sealing ring body, a first sealing lip and a second sealing lip which are integrally formed, wherein the first sealing lip and the second sealing lip are both annular and are coaxially arranged on the same end face of the sealing ring body, the cross section shapes of the first sealing lip and the second sealing lip are both triangular, the first sealing lip tilts towards the inner side of the sealing ring body, and the second sealing lip tilts towards the outer side of the sealing ring body.
Furthermore, the double-cross-arm independent suspension system for the ultra-heavy vehicle is characterized in that the sealing ring is made of nitrile rubber, and the Shore hardness of the sealing ring is HA 70.
Further, the present invention provides a double wishbone independent suspension system for an extra heavy vehicle, wherein the oil outlet passage is cylindrical in shape and has an internal diameter of 8 mm.
Further, the invention relates to a double-cross-arm independent suspension system for an extra-heavy vehicle, wherein a spring mounting hole is formed in the middle of the arm shoulder, and the lower end of the hydro-pneumatic spring is connected in the spring mounting hole through a lower spring pin shaft.
Furthermore, the invention relates to a double-wishbone independent suspension system for an extra-heavy vehicle, wherein a spring mounting hole penetrates through the lower end face of an arm shoulder from the upper end face of the arm shoulder, a spring pin shaft hole penetrating through the spring mounting hole is drilled in the outer side wall of the arm shoulder, the spring pin shaft hole is intersected with the spring mounting hole and is in a cross shape, the spring pin shaft hole is divided into a first spring pin shaft hole and a second spring pin shaft hole by the spring mounting hole, the lower end of an oil-gas spring is located in the spring mounting hole, and a lower spring pin shaft penetrates through the first spring pin shaft hole, the lower end of the oil-gas spring and the second spring pin shaft hole in sequence to connect the lower end of the oil-gas spring in the spring mounting hole.
Further, the invention relates to a double-wishbone independent suspension system for an extra-heavy vehicle, wherein a second double-metal bearing is installed in the first spring pin hole, and a third double-metal bearing is installed in the second spring pin hole.
Further, the invention relates to a double-wishbone independent suspension system for an extra-heavy vehicle, wherein the cross-sectional shape of the spring mounting hole is a runway shape with a rectangular middle and arc-shaped two sides.
Further, the invention relates to a double-wishbone independent suspension system for an extra-heavy vehicle, wherein the first double-metal bearing, the second double-metal bearing and the third double-metal bearing are all made of copper.
Compared with the prior art, the double-cross-arm independent suspension system for the ultra-heavy vehicle has the following advantages: the lower cross arm assembly comprises a first support arm and a second support arm which are oppositely arranged. The first support arm is connected with the second support arm into a whole through an arm shoulder, pin shaft holes which are coaxially arranged are formed in the end portion of the first support arm and the end portion of the second support arm, the second cross arm pin shaft penetrates through the pin shaft holes to hinge the lower cross arm assembly on the frame, oil inlet channels are axially drilled in the first cross arm pin shaft and the second cross arm pin shaft, oil outlet channels penetrating through the first cross arm pin shaft and the second cross arm pin shaft are radially drilled in the outer peripheral walls of the first cross arm pin shaft and the second cross arm pin shaft, the oil outlet channels are communicated with the oil inlet channels, annular diffusion grooves are circumferentially formed in the outer peripheral walls of the first cross arm pin shaft and the second cross arm pin shaft, and the annular diffusion grooves are communicated with oil outlets on two sides of the oil outlet channels. The lubricating grease can be added into an oil inlet channel of the cross arm pin shaft, the lubricating grease enters from the oil inlet channel, flows out from an oil outlet channel and is diffused through the annular diffusion groove, the purposes of abrasion resistance and lubrication are achieved, and the problem that the first cross arm pin shaft and the second cross arm pin shaft are difficult to lubricate and disassemble is effectively solved.
Drawings
FIG. 1 is a schematic structural diagram of a dual wishbone independent suspension system for an extra-heavy vehicle of the present invention;
FIG. 2 is a schematic structural diagram of a lower cross arm assembly in a double-cross arm independent suspension system for an extra-heavy vehicle according to the present invention;
FIG. 3 is an enlarged view of a portion A of FIG. 2;
FIG. 4 is a schematic structural view of a first cross arm pin (also a second cross arm pin) in a dual cross arm independent suspension system for an extra heavy vehicle in accordance with the present invention;
fig. 5 is a schematic cross-sectional view of a first cross arm pin (also a second cross arm pin) in a double cross arm independent suspension system for an extra-heavy vehicle according to the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention clearer and more obvious, the present invention is further described below with reference to the accompanying drawings and the detailed description. It is to be understood that the described embodiments are merely exemplary of the invention, and not restrictive of the full scope of the invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
As shown in fig. 1, 2, 4 in combination with fig. 5, the present invention relates to a double wishbone independent suspension system for an extra heavy vehicle, which specifically comprises an upper wishbone assembly 1, a lower wishbone assembly 2 and a hydro-pneumatic spring 3. The inner end of the upper cross arm assembly 1 is hinged with the frame 5 through a first cross arm pin shaft 51, the inner end of the lower cross arm assembly 2 is hinged with the frame 5 through a second cross arm pin shaft 52, the outer ends of the upper cross arm assembly 1 and the lower cross arm assembly 2 are respectively connected with the wheel sets 6 through spherical hinges 61, and up-and-down jumping and left-and-right steering movement of the wheels are achieved. The upper end of the hydro-pneumatic spring 3 is connected with the frame 5 through an upper spring pin shaft 31, and the lower end of the hydro-pneumatic spring 3 is connected with the lower cross arm assembly 2 through a lower spring pin shaft 32, so that impact force generated when the vehicle jumps is buffered. More specifically, the lower cross arm assembly 2 in the present embodiment specifically includes a first arm 21 and a second arm 22 which are oppositely arranged. The first arm 21 is connected with the second arm 22 through the arm shoulder 23, that is, the first arm 21, the second arm 22 and the arm shoulder 23 are integrally formed, so as to improve the bearing capacity. The end of the first support arm 21 and the end of the second support arm 22 are both provided with a pin shaft hole 24, the two pin shaft holes 24 are coaxially arranged, and the second cross arm pin 52 passes through the pin shaft holes 24 to hinge the lower cross arm assembly 2 on the frame 5 (namely, the second cross arm pin 52 is respectively arranged on the pin shaft holes 24 on the first support arm 21 and the second support arm 22 of the lower cross arm assembly 2, and is hinged with the frame 5 through the two second cross arm pins 52), so that the connection between the lower cross arm assembly 2 and the frame 5 is realized. The first cross arm pin shaft 51 and the second cross arm pin shaft 52 are identical in structure, in order to improve the lubricating effect, oil inlet channels 41 are drilled in the first cross arm pin shaft 51 and the second cross arm pin shaft 52 along the axial direction, oil outlet channels 42 penetrating through the first cross arm pin shaft 51 and the second cross arm pin shaft 52 are drilled in the outer peripheral walls of the first cross arm pin shaft 51 and the second cross arm pin shaft 52 along the radial direction, more specifically, the oil outlet channels 42 are cylindrical, and the inner diameter of each oil outlet channel 42 is 8mm, so that the circulation resistance of lubricating grease is reduced. The oil outlet channel 42 is communicated with the oil inlet channel 41, the annular diffusion grooves 43 are formed in the peripheral walls of the first cross arm pin shaft 51 and the second cross arm pin shaft 52 along the circumferential direction, the annular diffusion grooves 43 are communicated with oil outlets on two sides of the oil outlet channel 42, oil outlet resistance can be reduced by the annular diffusion grooves 43, the matching positions of the first cross arm pin shaft 51 and the second cross arm pin shaft 52 with other parts are lubricated more fully, the connection activity can be kept from being locked even if a vehicle runs for a long time, and follow-up disassembly and assembly are facilitated.
In fig. 3, taking the second xarm pin 52 as an example, in order to reduce the friction loss of the second xarm pin 52 and prevent dirt from entering the gap at the fitting position of the second xarm pin 52, the first bimetal bearing 7 and the seal ring 8 may be arranged in the pin shaft hole 24, and the first bimetal bearing 7 is in interference fit with the pin shaft hole 24, so that the second xarm pin 52 is indirectly assembled with the first support arm 21 or the second support arm 22 through the first bimetal bearing 7, so that the second xarm pin 52 is directly contacted with the first bimetal bearing 7, and the first bimetal bearing 7 has good wear resistance, and the friction loss of the second xarm pin 52 can be obviously reduced, and the service life can be prolonged. The seal ring 8 is coaxially disposed at the outer end of the first bimetal bearing 7 (the opposite side walls of the first arm 21 and the second arm 22 are inner, and vice versa, more specifically, as shown in fig. 2, taking the first arm 21 as an example, the outer end of the first bimetal bearing 7 is the upper end of the first arm 21, and taking the second arm 22 as an example, the outer end of the first bimetal bearing 7 is the lower end of the second arm 22), the outer end of the seal ring 8 is provided with a metal gasket 9 (the outer end of the seal ring 8 is in the same direction as the outer end of the first bimetal bearing 7), and the metal gasket 9 is fixed on the first arm 21 or the second arm 22 by a first fixing pin 91. The sealing ring 8 can play a role in sealing, so that the leakage of lubricating grease can be prevented, and foreign matters such as external dust or water can be prevented from entering between the first bimetal bearing 7 and the second cross arm pin shaft 52. The metal gasket 9 can protect the seal ring 8 and prevent the seal ring 8 from falling off. Through the design, the part matched with the second cross arm pin shaft 52 is isolated from the external environment through the sealing ring 8, so that the cleanliness of the matched part of the second cross arm pin shaft 52 can be fully ensured, and the problem that the second cross arm pin shaft 52 is difficult to disassemble due to dirt is prevented.
As shown in fig. 3, as a more specific example, the seal ring 8 used in the present embodiment specifically includes a seal ring body 81, a first seal lip 82, and a second seal lip 83 which are integrally formed. The first sealing lip 82 and the second sealing lip 83 are both annular and coaxially arranged on the same end face of the sealing ring body 81, the cross sections of the first sealing lip 82 and the second sealing lip 83 are both triangular, and the first sealing lip 82 tilts towards the inner side of the sealing ring body 81 to ensure the sealing performance of the inner side of the sealing ring 8; the second sealing lip 83 is tilted towards the outer side of the sealing ring body 81 to ensure the sealing performance of the outer side of the sealing ring 8, and through the above double-side sealing design, the internal environment of the part protected by the sealing ring can be effectively ensured, so that the subsequent disassembly and assembly are facilitated. More specifically, the sealing ring 8 in this embodiment is specifically made of nitrile rubber, and has better low-temperature performance and stronger sealing performance compared with polyurethane. The sealing ring of HA95 and the cooperation between second xarm round pin axle 52 are comparatively inseparable for whole lubricated oil circuit forms a confined space, when beating lubricating grease from oil feed passageway 41 of second xarm round pin axle 52, the confined space of oil circuit is compressed, causes lubricating grease to squeeze into, in this embodiment sets up sealing ring 8's shore hardness to HA70, and its hardness is lower relatively, and lubricating grease can be extruded from first seal lip 82, so that lubricating grease reachs the cross arm round pin axle and the cooperation of sealing ring 8, makes to add lubricating grease more laborsaving.
As shown in fig. 2, in order to facilitate the detachment between the hydro-pneumatic spring 3 and the lower cross arm assembly 2, a spring mounting hole 231 is formed in the middle of the arm shoulder 23 in the present embodiment, and the lower end of the hydro-pneumatic spring 3 is connected to the spring mounting hole 231 through a spring lower pin 32. More specifically, the spring mounting hole 231 runs through the lower end face of the arm shoulder 23 from the upper end face of the arm shoulder 23, a spring pin shaft hole running through the spring mounting hole 231 is drilled on the outer side wall of the arm shoulder 23, the spring pin shaft hole intersects with the spring mounting hole 231 and is cross-shaped, the spring pin shaft hole is divided into a first spring pin shaft hole 232 and a second spring pin shaft hole 233 by the spring mounting hole 231, so that the first spring pin shaft hole 232 is located on the outer side of the hole wall of the spring mounting hole 231, the second spring pin shaft hole 233 is located on the inner side of the hole wall of the spring mounting hole 231, the lower end of the hydro-pneumatic spring 3 is located in the spring mounting hole 231, the spring lower pin shaft 32 sequentially runs through the first spring pin shaft hole 232, and the lower end of the hydro-pneumatic spring 3 and the second spring pin shaft hole 233 connect the lower end of the hydro-pneumatic spring 3 in the spring mounting hole 231. A second bimetallic bearing 234 is mounted in the first spring pin bore 232 and a third bimetallic bearing 235 is mounted in the second spring pin bore 233. Above design can avoid under the spring round pin axle 32 and spring mounting hole 231 steel to the steel contact, or because of round pin axle 32 and spring mounting hole 231 cooperation department wearing and tearing, rust under the spring after long-time sports car, the round pin axle 32 dismouting difficulty problem under the spring that causes.
In order to increase stability, a small swing space is reserved for the hydro-pneumatic spring 3, and the cross section of the spring mounting hole 231 is designed to be in a runway shape with rectangular middle and arc-shaped two sides, so that the swing amplitude of the hydro-pneumatic spring 3 during wheel jumping is met.
It should be noted that the first bimetallic bearing 7, the second bimetallic bearing 234 and the third bimetallic bearing 235 in the above embodiments are all made of copper bimetallic bearings with higher stability and stronger wear resistance.
In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting of the invention. It should be noted that, if directional indication is involved in the embodiment of the present invention, the directional indication is only used for explaining the relative positional relationship, the motion situation, and the like between the components in a certain posture, and if the certain posture is changed, the directional indication is changed accordingly.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.
The above embodiments are merely descriptions of the preferred embodiments of the present invention, and do not limit the scope of the invention as claimed, and various modifications made by those skilled in the art according to the technical solutions of the present invention should fall within the scope of the invention defined by the claims without departing from the spirit of the present invention.
Claims (10)
1. A double-cross-arm independent suspension system for an ultra-heavy vehicle comprises an upper cross arm assembly (1), a lower cross arm assembly (2) and a hydro-pneumatic spring (3), wherein the inner end of the upper cross arm assembly (1) is hinged with a vehicle frame (5) through a first cross arm pin shaft (51), the inner end of the lower cross arm assembly (2) is hinged with the vehicle frame (5) through a second cross arm pin shaft (52), the outer ends of the upper cross arm assembly (1) and the lower cross arm assembly (2) are respectively connected with a wheel set (6) through ball hinges (61), the upper end of the hydro-pneumatic spring (3) is connected with the vehicle frame (5) through an upper spring pin shaft (31), the lower end of the hydro-pneumatic spring (3) is connected with the lower cross arm assembly (2) through a lower spring pin shaft (32), and the double-cross-arm independent suspension system is characterized in that the lower cross arm assembly (2) comprises a first support arm (21) and a second support arm (22) which are arranged oppositely, the first support arm (21) is connected with the second support arm (22) into a whole through an arm shoulder (23), the end part of the first support arm (21) and the end part of the second support arm (22) are both provided with a pin shaft hole (24), the two pin shaft holes (24) are coaxially arranged, the second cross arm pin shaft (52) penetrates through the pin shaft hole (24) to hinge the lower cross arm assembly (2) on the frame (5), oil inlet channels (41) are drilled in the first cross arm pin shaft (51) and the second cross arm pin shaft (52) along the axial direction, oil outlet channels (42) penetrating through the cross arm are drilled on the outer peripheral walls of the first cross arm pin shaft (51) and the second cross arm pin shaft (52) along the radial direction, the oil outlet channels (42) are communicated with the oil inlet channels (41), annular diffusion grooves (43) are formed in the outer peripheral walls of the first cross arm pin shaft (51) and the second cross arm pin shaft (52) along the circumferential direction, the annular diffusion groove (43) is communicated with oil outlets on two sides of the oil outlet channel (42).
2. The double wishbone independent suspension system for an extra-heavy vehicle according to claim 1, characterized in that a first bimetal bearing (7) and a sealing ring (8) are arranged in the pin shaft hole (24), the first bimetal bearing (7) is in interference fit with the pin shaft hole (24), the sealing ring (8) is coaxially arranged at the outer end of the first bimetal bearing (7), the outer end of the sealing ring (8) is provided with a metal gasket (9), and the metal gasket (9) is fixed on the first support arm (21) or the second support arm (22) by a first fixing pin (91).
3. The double wishbone independent suspension system for an extra-heavy vehicle according to claim 2, characterized in that the seal ring (8) comprises an integrally formed seal ring body (81), a first seal lip (82) and a second seal lip (83), the first seal lip (82) and the second seal lip (83) are both annular and are coaxially arranged on the same end face of the seal ring body (81), the cross-sectional shapes of the first seal lip (82) and the second seal lip (83) are both triangular, the first seal lip (82) is raised to the inner side of the seal ring body (81), and the second seal lip (83) is raised to the outer side of the seal ring body (81).
4. A double wishbone independent suspension system for extra heavy vehicles according to claim 2, characterised in that the seal ring (8) is made of nitrile rubber and the shore hardness of the seal ring (8) is HA 70.
5. The double wishbone independent suspension system for extra-heavy vehicles according to claim 1, wherein said oil outlet passage (42) is cylindrical in shape and the internal diameter of said oil outlet passage (42) is 8 mm.
6. The double wishbone independent suspension system for extra-heavy vehicles according to claim 2, characterized in that the middle of the arm shoulder (23) is provided with a spring mounting hole (231), and the lower end of the hydro-pneumatic spring (3) is attached within the spring mounting hole (231) by means of a lower spring pin (32).
7. A double wishbone independent suspension system for an extra-heavy vehicle according to claim 6, characterized in that the spring mounting hole (231) penetrates through the lower end surface of the arm shoulder (23) from the upper end surface of the arm shoulder (23), the outer side wall of the arm shoulder (23) is drilled with a spring pin shaft hole which penetrates through a spring mounting hole (231), the spring pin shaft hole is crossed with the spring mounting hole (231) and is in a cross shape, the spring pin shaft hole is divided into a first spring pin shaft hole (232) and a second spring pin shaft hole (233) by the spring mounting hole (231), the lower extreme of hydro-pneumatic spring (3) is located spring mounting hole (231), round pin axle (32) are in proper order passed first spring round pin shaft hole (232), the lower extreme and second spring round pin shaft hole (233) of hydro-pneumatic spring (3) and are connected the lower extreme of hydro-pneumatic spring (3) in spring mounting hole (231) under the spring.
8. The double wishbone independent suspension system for an extra-heavy vehicle according to claim 7, characterized in that a second bimetallic bearing (234) is mounted in said first spring pin bore (232) and a third bimetallic bearing (235) is mounted in said second spring pin bore (233).
9. The double wishbone independent suspension system for extra-heavy vehicles according to claim 6, wherein said spring mounting hole (231) is racetrack shaped with a rectangular center and arc sides in cross-section.
10. A double wishbone independent suspension system for extra heavy vehicles according to claim 8, characterised in that the first (7), second (234) and third (235) bimetallic bearings are all made of copper.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111431638.7A CN114211921A (en) | 2021-11-29 | 2021-11-29 | Double-cross-arm independent suspension system for ultra-heavy vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111431638.7A CN114211921A (en) | 2021-11-29 | 2021-11-29 | Double-cross-arm independent suspension system for ultra-heavy vehicle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN114211921A true CN114211921A (en) | 2022-03-22 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111431638.7A Pending CN114211921A (en) | 2021-11-29 | 2021-11-29 | Double-cross-arm independent suspension system for ultra-heavy vehicle |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114211921A (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB0128256D0 (en) * | 2000-12-15 | 2002-01-16 | Meritor Heavy Vehicle Tech | Independent suspension |
| CN105856996A (en) * | 2016-03-30 | 2016-08-17 | 北京航天发射技术研究所 | Independent suspension system for super-heavy chassis |
| CN107116985A (en) * | 2017-05-03 | 2017-09-01 | 北京航天发射技术研究所 | A kind of big stroke suspension system for multi-axle heavy type vehicle |
| CN107984998A (en) * | 2017-12-28 | 2018-05-04 | 东风商用车有限公司 | A kind of commercial car independent suspension rack front axle assembly |
| CN112032186A (en) * | 2020-08-28 | 2020-12-04 | 东风汽车股份有限公司 | Lubricated round pin axle limit structure of equipartition formula |
-
2021
- 2021-11-29 CN CN202111431638.7A patent/CN114211921A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB0128256D0 (en) * | 2000-12-15 | 2002-01-16 | Meritor Heavy Vehicle Tech | Independent suspension |
| CN105856996A (en) * | 2016-03-30 | 2016-08-17 | 北京航天发射技术研究所 | Independent suspension system for super-heavy chassis |
| CN107116985A (en) * | 2017-05-03 | 2017-09-01 | 北京航天发射技术研究所 | A kind of big stroke suspension system for multi-axle heavy type vehicle |
| CN107984998A (en) * | 2017-12-28 | 2018-05-04 | 东风商用车有限公司 | A kind of commercial car independent suspension rack front axle assembly |
| CN112032186A (en) * | 2020-08-28 | 2020-12-04 | 东风汽车股份有限公司 | Lubricated round pin axle limit structure of equipartition formula |
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