WO2012171411A1 - 油气悬挂机构及具有该悬挂机构的工程车辆 - Google Patents

油气悬挂机构及具有该悬挂机构的工程车辆 Download PDF

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Publication number
WO2012171411A1
WO2012171411A1 PCT/CN2012/074207 CN2012074207W WO2012171411A1 WO 2012171411 A1 WO2012171411 A1 WO 2012171411A1 CN 2012074207 W CN2012074207 W CN 2012074207W WO 2012171411 A1 WO2012171411 A1 WO 2012171411A1
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WO
WIPO (PCT)
Prior art keywords
hinge
oil
ball joint
suspension mechanism
cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2012/074207
Other languages
English (en)
French (fr)
Inventor
陈林
皮秋生
李安强
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hunan Sany Intelligent Control Equipment Co Ltd
Sany Automobile Hoisting Machinery Co Ltd
Original Assignee
Hunan Sany Intelligent Control Equipment Co Ltd
Sany Automobile Hoisting Machinery Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hunan Sany Intelligent Control Equipment Co Ltd, Sany Automobile Hoisting Machinery Co Ltd filed Critical Hunan Sany Intelligent Control Equipment Co Ltd
Publication of WO2012171411A1 publication Critical patent/WO2012171411A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
    • B60G13/001—Arrangements for attachment of dampers
    • B60G13/003—Arrangements for attachment of dampers characterised by the mounting on the vehicle body or chassis of the damper unit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
    • B60G13/001—Arrangements for attachment of dampers
    • B60G13/005—Arrangements for attachment of dampers characterised by the mounting on the axle or suspension arm of the damper unit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/20—Type of damper
    • B60G2202/24—Fluid damper
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/10—Mounting of suspension elements
    • B60G2204/12—Mounting of springs or dampers
    • B60G2204/128—Damper mount on vehicle body or chassis
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/10—Mounting of suspension elements
    • B60G2204/12—Mounting of springs or dampers
    • B60G2204/129—Damper mount on wheel suspension or knuckle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/43—Fittings, brackets or knuckles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
    • B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
    • B60G2206/40—Constructional features of dampers and/or springs
    • B60G2206/41—Dampers

Definitions

  • the present invention relates to the field of vehicle suspension systems, and in particular to an oil and gas suspension mechanism and an engineering vehicle having the suspension mechanism.
  • the oil and gas suspension cylinder is a buffer device connecting the axle and the frame. The function is to reduce the impact of the ground on the axle when the vehicle is driving, and to increase the comfort of the whole vehicle.
  • a damping hole is added to the oil and gas suspension to rapidly attenuate the vibration.
  • the commonly used oil and gas suspension cylinders are installed in the pin shaft, that is, the upper and lower ends of the suspension cylinder are respectively provided with the upper ball head 1 and the lower ball head 2, and one frame is left on the frame and the axle.
  • the upper and lower ends of the oil and gas suspension cylinder are connected to the frame and the axle through respective pin shafts.
  • the oil and gas suspension cylinder adopting the structure has a radial force applied to the joint hinge or the universal joint, and has high requirements on the bearing force of the hinge or the universal joint, and the joint joint is arranged at both ends of the cylinder.
  • the arrangement of the cylinder is limited to a certain extent.
  • the mounting points on the cylinder need to be placed on the upper end of the frame as much as possible to increase the design difficulty.
  • the cylinders are required to be arranged on both sides of the frame.
  • the object of the present invention is to provide an oil and gas suspension mechanism and an engineering vehicle having the same, to solve the problem that when the oil and gas suspension system of the existing engineering vehicle is matched with the double tire axle, the distance between the axle tire and the frame is small, Technical problems in the difficulty of arranging oil and gas suspension cylinders.
  • an oil and gas suspension mechanism comprising: a ball joint having an inner spherical surface and a joint for connecting to the frame; a suspension cylinder, Mounted on the ball joint, wherein: the middle portion of the cylinder of the suspension cylinder has a spherically convex ball joint, the ball joint cooperates with the inner spherical surface of the ball joint to constitute a hinge mechanism; the extension of the piston rod of the suspension cylinder The outlet has a hinge that is hinged to the axle.
  • the ball joint includes a first half hinge and a second half hinge which are engaged with each other, and the connecting portion is disposed on the first half hinge or the second half hinge.
  • first half joint and the second half hinge seat are respectively provided with a first abutting portion and a second abutting portion, and the first butting portion and the second butting portion are provided with cooperating connecting screw holes.
  • the abutting surface of the first half hinge and the second half hinge is coplanar with the largest section of the ball joint in the horizontal direction, and the first butting portion is the first horizontal ring panel disposed on the outer circumference of the first half hinge
  • the second butt joint is a second horizontal ring panel disposed on the outer circumference of the second half hinge.
  • first horizontal ring panel includes a plurality of first screw holes disposed equidistantly along the first circumference
  • second horizontal ring panel includes a plurality of second screw holes equally spaced along the second circumference, wherein The first circumference and the second circumference are coaxial with the same radius, and the number and radius of the first screw hole and the second screw hole are the same.
  • the outer circumference of the first horizontal ring panel or the second horizontal ring panel is provided with a ring portion extending outward in the horizontal direction, and the outer diameter of the ring portion is larger than the outer diameter of the horizontal ring panel opposite thereto to form a connecting portion on the connecting portion
  • a third screw hole uniformly distributed in the circumferential direction is provided.
  • an inner side of the ball joint is provided with an oil storage ring groove
  • an outer side of the ball joint is provided with a fuel hole which communicates with the oil ring groove and points to the center of the ball joint.
  • a fueling screw plug is disposed in the oiling hole. Wrap angle arc.
  • a telescopic dust jacket is disposed between the hinge portion of the piston rod and the lower end of the cylinder.
  • the suspension cylinder is connected to the frame through a ball joint seat disposed in the middle of the cylinder block, thereby lowering the upper connection point of the suspension cylinder, thereby effectively reducing the height of the vehicle, lowering the center of gravity, and increasing the stability of the vehicle; in addition, due to the installation of the suspension cylinder At the bottom of the frame, rather than the side of the frame, it is possible to effectively avoid the problem that the suspension cylinder cannot be installed due to insufficient spacing between the side of the frame and the tire.
  • Figure 1 is a schematic view showing the structure of a conventional oil and gas suspension cylinder
  • FIG. 2 is a schematic view showing a mounting structure of an oil and gas suspension mechanism on a vehicle according to a preferred embodiment of the present invention
  • Figure 3 is a schematic cross-sectional view of a cylinder block in accordance with a preferred embodiment of the present invention.
  • FIG. 4 is a schematic structural view showing a combination of a suspension cylinder and a ball joint according to a preferred embodiment of the present invention
  • FIG. 5 is a plan view showing a first half hinge and a first butt joint according to a preferred embodiment of the present invention
  • Figure 6 is a bottom plan view showing the second half hinge, the second butt joint and the connecting portion of the preferred embodiment of the present invention.
  • Figure ⁇ is a schematic cross-sectional view of a first half hinge and a second half hinge of a preferred embodiment of the present invention.
  • Figure 8 is a schematic view showing the swing angle of a suspension cylinder in accordance with a preferred embodiment of the present invention.
  • an oil and gas suspension mechanism includes a suspension cylinder, and a central portion of the cylinder 11 of the suspension cylinder has a spherically convex ball joint.
  • the lower bottom plate 20 of the frame is provided with a ball joint 30, and the inner surface of the ball joint 30 is matched with the outer circumference of the ball joint portion 11a, so that the ball joint portion can be mounted on the ball joint portion 11a.
  • the ball joint 11a and the ball joint 30 constitute a hinge mechanism, and the cylinder 11 can be swung by the ball joint 30 as a support.
  • the ball joint 30 is provided with a joint for connecting to the lower floor 20 of the frame; the projecting end of the piston rod 13 of the suspension cylinder has a hinge portion 13a hinged to the axle 40.
  • the ball joint 30 may include a first half hinge 31 and a second half hinge 32 that are engaged with each other, and a connection portion for connecting to the lower bottom plate 20 of the frame may be disposed at The first half hinge seat 31 may also be disposed on the second half hinge seat 32.
  • the first half hinge seat 31 and the second half hinge seat 32 in order to enable the first half hinge seat 31 and the second half hinge seat 32 to be fastened together, and to be able to adapt to the impact during running of the vehicle, the first half hinge seat 31 and the second half hinge seat
  • the first abutting portion 31 1 and the second abutting portion 321 are respectively disposed on the 32, and the first butting portion 311 and the second butting portion 321 are provided with matching screw holes.
  • first half hinge 31 and the second half hinge 32 are sleeved on the ball joint portion 11 a of the cylinder 11 , and then the first butt joint 311 and the second butt joint portion 321 are The mating connecting screw holes are aligned, and finally the first half hinge seat 31 and the second half hinge seat 32 are fastened together by bolts.
  • the first half hinge seat 31 and the second half hinge seat 32 may be snapped together in the horizontal direction or may be snapped together in the vertical direction.
  • the first half hinge seat 31 and the second half hinge seat 32 are fastened together in the horizontal direction, that is, the abutting faces of the first half hinge seat 31 and the second half hinge seat 32 and the ball joint portion 11a
  • the largest cross section in the horizontal direction is coplanar
  • the first butting portion 311 is a first horizontal ring panel disposed on the outer circumference of the first hinge half 31
  • the second butting portion 321 is a second horizontal portion disposed on the outer circumference of the second hinge half 32. Ring panel. That is, the first half hinge seat 31 passes downward from the upper end of the cylinder block 11, and the second half hinge seat 32 passes upwardly from the lower end of the cylinder block 11 to be engaged with the first half hinge seat 31.
  • the first horizontal ring panel can be A plurality of pairs of screw holes which are matched with each other are disposed on the first horizontal joint portion 311 and the second horizontal ring panel (second butted portion 321), and are fastened by a plurality of bolts.
  • a plurality of first screw holes 31 3 may be equally spaced along the first circumference on the first horizontal ring panel, and a plurality of second screws may be equally spaced along the second circumference on the second horizontal ring panel
  • the outer circumference of the first horizontal ring panel or the second horizontal ring panel is provided with a ring portion extending outward in the horizontal direction, and the outer diameter of the ring portion is larger than that of the horizontal ring panel opposite thereto
  • the outer diameter is to form the connecting portion.
  • the connecting portion for connecting to the lower floor 20 of the frame may be a third horizontal ring panel 324 extending outward in the radial direction of the second horizontal ring panel, and the outer diameter of the third horizontal ring panel 324 is larger than
  • the outer diameter of the first horizontal ring panel is such that the third horizontal ring panel 324 can be directly coupled to the lower floor 20 of the frame without sandwiching the first horizontal ring panel.
  • a plurality of third screw holes 325 arranged at equal intervals in the circumferential direction may be disposed on the third horizontal ring panel 324, and the third screw holes 325 may be used to implement the ball joint 30 and the vehicle The purpose of the lower bottom plate 20 of the frame is connected.
  • the third horizontal ring panel 324 is integrated with the second horizontal ring panel, and there is no obvious dividing line, but for the sake of distinction, the third horizontal ring panel 324 and the second horizontal ring panel are dashed by a broken line in FIG. Separate, just for ease of understanding.
  • the ball joint 30 An oil reservoir groove 34 is disposed on the inner side, and an oil supply hole 35 communicating with the oil storage ring groove 34 and directed to the center of the ball joint 30 is disposed on the outer side of the ball joint 30, and a fuel filler screw 36 is disposed in the oil hole 35.
  • the design of the cylinder should meet the need of such relative motion, that is, the swing amplitude of the cylinder 11 swinging with the ball joint 30 as a fulcrum. It needs to be determined according to the size of the vehicle design and the required passing ability, that is, to meet the requirements of the vehicle.
  • the arc angle of the ball joint portion 11a along the axial direction of the cylinder block 11 is larger than that of the ball joint.
  • the angle of the seat 30 along the axial direction of the cylinder 11 is arc. It can also be said that the two ends of the ball joint portion 11a are reserved with a reserved arc portion which is not covered by the ball joint 30, and the arc length of the reserved arc portion becomes larger as the maximum swing angle of the cylinder 11 becomes larger. That is, the arc length of the reserved arc portion of the ball joint portion 11a can be changed in accordance with the change in the maximum swing angle of the cylinder block 11 of the suspension cylinder.
  • ⁇ ⁇ ( ⁇ 1, ⁇ 2) where ⁇ is the maximum swing angle of the suspension cylinder, and the angle ⁇ 1 and the angle ⁇ 2 are respectively the upper end and the lower end of the ball joint portion 11a. If the angle corresponding to the arc portion is reserved, if ⁇ 1 and ⁇ 2 are smaller than the maximum swing angle required for the suspension cylinder, the length of the reserved arc portion of the upper end and the lower end of the ball joint 30 should be increased (or, should be reduced)
  • the first half hinge 31 and the second half hinge 32 have an arc length, and the arc length of the wrap angle is reduced while satisfying the force requirement of the ball joint 30.
  • a retractable, elastic boot may be provided between the hinge portion 13a of the piston rod 13 and the lower end of the cylinder 11. 50.
  • an engineering vehicle in which a frame and an axle of the construction vehicle can be connected by the above-described oil and gas suspension mechanism.
  • the lower end of the suspension cylinder is connected to the axle, and the connection point at the upper end moves to the middle of the cylinder.
  • the connection between the cylinder and other components is bolted. After the cylinder is installed, the upper end can be hidden inside the frame of the frame. About the height of the chassis of the vehicle.
  • the suspension cylinder can be arranged inside the frame of the frame, which effectively utilizes the space of the whole vehicle, which facilitates the arrangement of other components, and at the same time, can prevent the dust from contaminating the cylinder to a certain extent due to the inside of the casing.
  • the cylinder line can be arranged from the inside of the box to make the whole car more beautiful.
  • the cylinder suspension mechanism provided by the present invention is most suitable.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

一种油气悬挂机构及具有该悬挂机构的工程车辆。油气悬挂机构包括，球铰座（30），具有内球面以及用于与车架相连的连接部，悬挂油缸，安装在球铰座（30）上，其中悬挂油缸的缸体（11）的中部具有呈球形凸出的球铰部（11a），球铰部（11a）与球铰座（30）的内球面相配合以构成铰接机构，悬挂油缸的活塞杆（13）的伸出端具有与车桥铰接的铰接部（13a）。该油气悬挂机构的悬挂油缸通过设置在缸体（11）中部的球铰座（30）与车架相连，将悬挂油缸的上连接点降低，进而能够有效地降低整车高度，降低重心，增加整车稳定性。

Description

油气悬挂机构及具有该悬挂机构的工程车辆 本申请要求于 2011 年 06 月 14 日提交中国专利局、 申请号为 201110159432.3、 发明名称为"油气悬挂机构及具有该悬挂机构的工程车 辆"的中国专利申请的优先权， 其全部内容通过引用结合在本申请中。
技术领域
本发明涉及车辆悬挂系统领域， 特别地， 涉及一种油气悬挂机构及具 有该悬挂机构的工程车辆。
背景技术
对于一般的油缸， 为了能让油缸在一定范围内摆动， 在油缸两端采用 球铰或万向节， 球铰或万向节承受径向力作用。 如油气悬挂油缸， 其为连 接车桥与车架的緩沖装置， 作用是减轻汽车行驶时地面对车桥的沖击传递 到车架， 增加整车的舒适性。 同时， 为防止过多的振荡， 在油气悬挂内加 有阻尼孔， 以迅速的衰减振动。
如图 1所示， 常用的油气悬挂油缸的安装方式为销轴安装， 即悬挂油 缸上、 下两端分别设置有上球头 1和下球头 2 , 同时在车架及车桥上留有 一支座， 油气悬挂油缸上、 下两端通过分别通过各自的销轴与车架和车桥 连接。 采用该结构的油气悬挂油缸， 对其连接铰链或万向节而言， 受力为 径向力， 对铰链或万向节的承力要求较高， 而且， 连接关节布置在油缸的 两端， 从一定程度上限制了油缸的布置。 为了降低整车重心， 油缸上安装 点需要尽量布置在车架上端， 增加设计难度。 同时， 油缸要求布置在车架 两边， 当车架宽度大于车桥油缸安装点宽度时， 需要对车架进行较大的改 动才能布置悬架油缸。
因此， 有必要提供一种能有效的降低整车高度， 增加整车稳定性， 并 且安装方式灵活且易于安装油气悬挂油缸机构。
发明内容
本发明目的在于提供一种油气悬挂机构及具有该悬挂机构的工程车 辆， 以解决现有工程车辆的油气悬挂系统与双胎车桥匹配使用时， 由于车 桥轮胎与车架之间间距小， 油气悬挂油缸难以布置的技术问题。
为实现上述目的，根据本发明的一个方面，提供了一种油气悬挂机构， 包括， 球铰座， 具有内球面以及用于与车架相连的连接部； 悬挂油缸， 安 装在球铰座上， 其中： 悬挂油缸的缸体的中部具有呈球形凸出的球铰部， 球铰部与球铰座的内球面相配合以构成铰接机构； 悬挂油缸的活塞杆的伸 出端具有与车桥铰接的铰接部。
进一步地， 球铰座包括相互扣合的第一半铰座和第二半铰座， 连接部 设置于第一半铰座或第二半铰座上。
进一步地， 第一半铰座和第二半铰座上分别设置有第一对接部和第二 对接部， 第一对接部和第二对接部上设置有相互配合的连接螺孔。
进一步地， 第一半铰座和第二半铰座的对接面与球铰部的沿水平方向 的最大截面共面，第一对接部为设置于第一半铰座外周的第一水平环面板， 第二对接部为设置于第二半铰座外周的第二水平环面板。
进一步地， 第一水平环面板上包括沿第一圓周等间距地设置的多个第 一螺孔，第二水平环面板上包括沿第二圓周等间距地设置的多个第二螺孔， 其中， 第一圓周与第二圓周同轴同半径， 且第一螺孔和第二螺孔的数量和 半径均相同。
进一步地， 第一水平环面板或第二水平环面板的外周设置沿水平方向 向外延伸的环部， 环部的外径大于与其相对的水平环面板的外径以形成连 接部， 连接部上设置有沿圓周方向均布的第三螺孔。
进一步地， 球铰座的内侧设置有储油环槽， 球铰座的外侧设置有与储 油环槽连通且指向球铰座的中心的加油孔。所述加油孔内设置有加油螺塞。 包角弧度。
进一步地，活塞杆的铰接部与缸体的下端之间设置有可伸缩的防尘套。 根据本发明的另一方面， 还提供了一种工程车辆， 该工程车辆的车架 与车桥之间通过上述油气悬挂机构连接。
本发明具有以下有益效果：
悬挂油缸通过设置在缸体中部的球铰座与车架相连， 将悬挂油缸的上 连接点降低， 进而能够有效地降低整车高度， 降低重心， 增加整车稳定性； 另外， 由于悬挂油缸安装在车架底部， 而非车架侧面， 因而可以有效的避 免由于车架侧面与轮胎间距不足导致无法安装悬挂油缸的问题。
除了上面所描述的目的、 特征和优点之外， 本发明还有其它的目的、 特征和优点。 下面将参照图， 对本发明作进一步详细的说明。
附图说明
构成本申请的一部分的附图用来提供对本发明的进一步理解， 本发明 的示意性实施例及其说明用于解释本发明，并不构成对本发明的不当限定。 在附图中：
图 1是现有油气悬挂油缸结构示意图；
图 2 是本发明优选实施例的油气悬挂机构在车辆上的安装结构示意 图；
图 3是本发明优选实施例的缸体剖面结构示意图；
图 4是本发明优选实施例的悬挂油缸与球铰座的组合结构示意图； 图 5 是本发明优选实施例的第一半铰座及第一对接部的俯视结构示 意；
图 6是本发明优选实施例的第二半铰座、 第二对接部和连接部的仰视 结构示意图；
图 Ί是本发明优选实施例的第一半铰座和第二半铰座的剖面结构示意 图； 以及
图 8是本发明优选实施例的悬挂油缸摆动角度示意图。
具体实施方式
以下结合附图对本发明的实施例进行详细说明， 但是本发明可以由权 利要求限定和覆盖的多种不同方式实施。
如图 2和图 3所示， 根据本发明的一个方面， 提供了一种油气悬挂机 构，该油气悬挂机构包括悬挂油缸， 悬挂油缸的缸体 11的中部具有呈球形 凸出的球铰部 l la。 相应地， 车架的下底板 20上设置有球铰座 30 , 该球铰 座 30的内表面与球铰部 11a的外周相匹配，这样，球铰部可以安装在与球 铰部 11 a的形状相适应的球铰座 30中， 以使球铰部 11 a与球铰座 30构成 铰接机构，进而使缸体 11以球铰座 30为支承座可摆动。球铰座 30上设置 有用于与车架的下底板 20相连的连接部； 悬挂油缸的活塞杆 13的伸出端 具有与车桥 40铰接的铰接部 13a。
为了便于球铰座 30的拆装， 球铰座 30可以包括相互扣合的第一半铰 座 31和第二半铰座 32 , 用于与车架的下底板 20相连的连接部可以设置在 第一半铰座 31上， 也可以设置在第二半铰座 32上。
如图 4所示，为了使第一半铰座 31和第二半铰座 32能够扣合在一起， 并能够适应车辆行驶过程中的沖击， 第一半铰座 31和第二半铰座 32上分 别设置有第一对接部 31 1和第二对接部 321 , 第一对接部 311和第二对接 部 321上设置有相互配合的连接螺孔。 安装球铰座 30时， 将第一半铰座 31和第二半铰座 32套设在缸体 11的球铰部 11 a上，然后将第一对接部 311 和第二对接部 321上的相互配合的连接螺孔对齐， 最后利用螺栓将第一半 铰座 31和第二半铰座 32扣合在一起。
第一半铰座 31和第二半铰座 32可以沿水平方向扣合在一起， 也可以 沿竖直方向扣合在一起。 优选地， 第一半铰座 31和第二半铰座 32沿水平 方向扣合在一起， 也就是说， 第一半铰座 31和第二半铰座 32的对接面与 球铰部 11a的沿水平方向的最大截面共面， 第一对接部 311为设置于第一 半铰座 31外周的第一水平环面板， 第二对接部 321 为设置于第二半铰座 32外周的第二水平环面板。 也就是说， 第一半铰座 31从缸体 11的上端向 下穿过， 第二半铰座 32从缸体 11的下端向上穿过与第一半铰座 31扣合。
如图 5和图 6所示， 为了使第一半铰座 31和第二半铰座 32能够紧密 地扣合，并能承受车辆行驶过程中的各种沖击，可以在第一水平环面板（第 一对接部 311 )和第二水平环面板（第二对接部 321 )上设置多对相互配合 的螺纹孔， 再用多个螺栓进行紧固。 优选地， 可在第一水平环面板上沿第 一圓周等间距地设置有多个第一螺孔 31 3 , 在第二水平环面板上沿第二圓 周等间距地设置有多个第二螺孔 323 , 其中， 第一圓周与第二圓周的同轴 同半径， 第一螺孔 313和第二螺孔 323的数量和半径均相同。
为了节约安装空间， 筒化油气悬挂机构的结构， 第一水平环面板或第 二水平环面板的外周设置沿水平方向向外延伸的环部， 环部的外径大于与 其相对的水平环面板的外径以形成所述连接部。 优选地， 用于与车架的下 底板 20 相连的连接部可以是沿第二水平环面板的径向向外伸出的第三水 平环面板 324 , 且第三水平环面板 324的外径大于第一水平环面板的外径， 以使第三水平环面板 324能够与车架的下底板 20直接相连，而不会将第一 水平环面板夹在中间。 可以在第三水平环面板 324上设置多个沿圓周方向 等间距布置的第三螺孔 325 , 第三螺孔 325可以用于实现将球铰座 30与车 架的下底板 20相连的目的。
实际上， 第三水平环面板 324与第二水平环面板为一体的面板， 并没 有明显的分界线， 但是为了进行区分， 图 6中采用虚线将第三水平环面板 324与第二水平环面板区分开， 仅为了便于理解。
如图 Ί所示， 由于球铰座 30与缸体 11的球铰部 11a之间能够产生相 对运动， 为了提高球铰座 30与球铰部 11 a之间的润滑性， 球铰座 30的内 侧设置有储油环槽 34 , 球铰座 30的外侧设置有与储油环槽 34连通且指向 球铰座 30的中心的加油孔 35 , 并且加油孔 35内设置有加油螺塞 36。
整车行驶时， 车桥 40与车架之间存在相对运动， 因此， 油缸的设计应 能满足这种相对运动的需要， 也就是说， 缸体 11以球铰座 30为支点摆动 的摆动幅度需要根据整车设计的尺寸及要求的通过能力来决定， 即要满足 整车要求。
如图 8所示， 为了避免运行中缸体 11与第一半铰座 31和第二半铰座 32之间发生干涉， 球铰部 11a的沿缸体 11轴向的包角弧度大于球铰座 30 沿缸体 11轴向的包角弧度。也可以说，球铰部 11a的两端预留有未被球铰 座 30覆盖的预留弧部， 预留弧部的弧长随缸体 11的最大摆动角度的变大 而变大，也就是说，可以根据悬挂油缸的缸体 11的最大摆动角度的变化而 改变球铰部 11 a的预留弧部的弧长。 换一个角度看， 也可以利用公式 α ηΰη (Φ 1， Φ 2)来表示， 其中， α为悬挂油缸的最大摆角， 角 Φ 1 和角 Φ 2 分别为球铰部 11a的上端和下端的预留弧部所对应的角度， 若 Φ 1、 Φ 2小 于悬挂油缸所需的最大摆角 ,则应该增加球铰座 30的上端和下端的预留 弧部的长度（或者说，应减小第一半铰座 31和第二半铰座 32的包角弧长， 且减小包角弧长的同时还要能够满足球铰座 30的受力要求 )。
为了防止灰尘通过随活塞杆 1 3的伸缩运动而进入缸体 11内， 可以在 活塞杆 1 3的铰接部 1 3a与缸体 1 1的下端之间设置可伸缩的、 具有弹性的 防尘套 50。
根据本发明的另一个方面， 还提供了一种工程车辆， 该工程车辆的车 架和车桥之间可以通过上述的油气悬挂机构连接。 悬挂油缸的下端与车桥 的连接方式不变， 上端的连接点移动到油缸的中间位置。 油缸与其它部件 的 连接采用螺栓连接， 油缸安装好之后， 上端可隐藏在车架箱体内部， 节 约整车底盘的高度。
悬挂油缸可以布置在车架箱体的内部， 有效利用了整车空间， 利于其 它零部件的布置， 同时由于在箱体内， 可以在一定程度上防止灰尘对油缸 的污染。 油缸管路可以从箱体内部布置， 使整车更加美观。
当总布置时， 车架宽度大于车桥上油缸安装支架的宽度时， 采用本发 明提供的油缸悬挂机构最为适合。
以上所述仅为本发明的优选实施例而已， 并不用于限制本发明， 对于 本领域的技术人员来说， 本发明可以有各种更改和变化。 凡在本发明的精 神和原则之内， 所作的任何修改、 等同替换、 改进等， 均应包含在本发明 的保护范围之内。

Claims

权 利 要 求
1、 一种油气悬挂机构， 其特征在于，
球铰座（30 ), 具有内球面以及用于与车架相连的连接部；
悬挂油缸， 安装在所述球铰座（30 )上， 其中：
所述悬挂油缸的缸体（11 ) 的中部具有呈球形凸出的球铰部 （11a ), 所述球铰部 （11a ) 与所述球铰座（30 ) 的内球面相配合构成铰接机构。
2、根据权利要求 1所述的油气悬挂机构， 其特征在于， 所述悬挂油缸 的活塞杆 ( 1 3 ) 的伸出端具有与车桥（ 40 )铰接的铰接部 （ 1 )。
3、根据权利要求 2所述的油气悬挂机构，其特征在于，所述球铰座（ 30 ) 包括相互扣合的第一半铰座（ 31 )和第二半铰座（ 32 ),所述第一半铰座（ 31 ) 和所述第二半铰座（ 32 )上分别设置有第一对接部 （ 311 )和第二对接部 ( 321 ), 所述第一对接部 （ 311 )和所述第二对接部 （ 321 )上设置有相互 配合的连接螺孔。
4、 根据权利要求 3所述的油气悬挂机构， 其特征在于， 所述连接部 设置于所述第一半铰座（ 31 )或所述第二半铰座（ 32 )上。
5、根据权利要求 4所述的油气悬挂机构， 其特征在于， 所述第一半铰 座（ 31 )和所述第二半铰座（ 32 )的对接面与所述球铰部（ 11a )的沿水平 方向的最大截面共面，所述第一对接部（ 311 )为设置于所述第一半铰座（ 31 ) 外周的第一水平环面板， 所述第二对接部（ 321 )为设置于所述第二半铰座 ( 32 )外周的第二水平环面板。
6、根据权利要求 5所述的油气悬挂机构， 其特征在于， 所述第一水平 环面板上包括沿第一圓周等间距地设置的多个第一螺孔（31 3 ), 所述第二 水平环面板上包括沿第二圓周等间距地设置的多个第二螺孔（ 323 ),其中， 所述第一圓周与所述第二圓周同轴同半径， 且所述第一螺孔（ 31 3 )和所述 第二螺孔（ 323 ) 的数量和半径均相同。
7、根据权利要求 6所述的油气悬挂机构， 其特征在于， 所述第一水平 环面板或所述第二水平环面板的外周设置沿水平方向向外延伸的环部， 所 述环部的外径大于与其相对的水平环面板的外径以形成所述连接部， 所述 连接部上设置有沿圓周方向均布的第三螺孔（ 325 )。
8、 根据权利要求 1至 7中任一项所述的油气悬挂机构， 其特征在于， 所述球铰座（ 30 )的内侧设置有储油环槽（ 34 ), 所述球铰座（ 30 )的外侧 设置有与所述储油环槽（34)连通且指向所述球铰座（30) 的中心的加油 孔（ 35 )。 所述加油孔（ 35 ) 内设置有加油螺塞（ 36 )。
9、 根据权利要求 8 所述的油气悬挂机构， 其特征在于， 所述球铰部 ( 11a )的沿所述缸体（ 11 )轴向的包角弧度大于所述球铰座（ 30 )沿所述 缸体（11 )轴向的包角弧度。
10、 根据权利要求 8所述的油气悬挂机构， 其特征在于， 所述活塞杆 ( 13)的铰接部（ 13a )与所述缸体（ 11 )的下端之间设置有可伸缩的防尘 套（50)。
11、 一种工程车辆， 具有车架和车桥， 其特征在于， 所述车架和所述 车桥之间通过权利要求 1至 10中任一项所述的油气悬挂机构连接。
PCT/CN2012/074207 2011-06-14 2012-04-17 油气悬挂机构及具有该悬挂机构的工程车辆 Ceased WO2012171411A1 (zh)

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