Classifications

• • 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
  • B60G11/265—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs hydraulic springs
• • 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
  • B60G3/00—Resilient suspensions for a single wheel
  • B60G3/02—Resilient suspensions for a single wheel with a single pivoted arm
  • B60G3/04—Resilient suspensions for a single wheel with a single pivoted arm the arm being essentially transverse to the longitudinal axis of the vehicle
  • B60G3/06—Resilient suspensions for a single wheel with a single pivoted arm the arm being essentially transverse to the longitudinal axis of the vehicle the arm being rigid
• • 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
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G7/00—Pivoted suspension arms; Accessories thereof
  • B60G7/001—Suspension arms, e.g. constructional features
  • B60G7/003—Suspension arms, e.g. constructional features of adjustable length
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
  • B62D—MOTOR VEHICLES; TRAILERS
  • B62D5/00—Power-assisted or power-driven steering
  • B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
  • B62D—MOTOR VEHICLES; TRAILERS
  • B62D7/00—Steering linkage; Stub axles or their mountings
  • B62D7/06—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins
  • B62D7/08—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in a single plane transverse to the longitudinal centre line of the vehicle
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
  • B62D—MOTOR VEHICLES; TRAILERS
  • B62D7/00—Steering linkage; Stub axles or their mountings
  • B62D7/06—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins
  • B62D7/14—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering
  • B62D7/142—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering specially adapted for particular vehicles, e.g. tractors, carts, earth-moving vehicles, trucks
  • B62D7/144—Steering linkage; Stub axles or their mountings for individually-pivoted wheels, e.g. on king-pins the pivotal axes being situated in more than one plane transverse to the longitudinal centre line of the vehicle, e.g. all-wheel steering specially adapted for particular vehicles, e.g. tractors, carts, earth-moving vehicles, trucks for vehicles with more than two axles
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B66—HOISTING; LIFTING; HAULING
  • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
  • B66C9/00—Travelling gear incorporated in or fitted to trolleys or cranes
• • 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
  • B60G13/02—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally
  • B60G13/06—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type
  • B60G13/08—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type hydraulic
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G15/00—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type
  • B60G15/08—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having fluid spring
  • B60G15/12—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having fluid spring and fluid damper
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
  • B60G21/02—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected
  • B60G21/04—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically
  • B60G21/05—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically between wheels on the same axle but on different sides of the vehicle, i.e. the left and right wheel suspensions being interconnected
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G2200/00—Indexing codes relating to suspension types
  • B60G2200/10—Independent suspensions
  • B60G2200/14—Independent suspensions with lateral arms
  • B60G2200/142—Independent suspensions with lateral arms with a single lateral arm, e.g. MacPherson type
• • 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
  • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
  • B60G2204/416—Ball or spherical joints
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G2300/00—Indexing codes relating to the type of vehicle
  • B60G2300/06—Cranes

Definitions

• the invention relates to the technical field of engineering machinery, and in particular to an independent suspension system and a crane having the same. Background technique
• a conventional rigid bridge is commonly used.
• the left and right wheels of the non-independent suspension are mounted on an integral rigid shaft or a non-breaking transaxle axle housing.
• the independent suspension does not have a rigid beam or a non-disconnected axle connection between the left and right wheels.
• the left and right wheels are connected "independently" to the frame or the body, that is, to form a disconnected vehicle. bridge. Based on the structural characteristics of the two, the suspension structure of the existing all-terrain crane chassis is gradually transformed into an independent suspension structure.
• FIG. 1 is a schematic structural view of a typical independent suspension system in the prior art
• FIG. 2 is a lateral schematic view of FIG.
• the suspension system is a disconnected axle that transmits power to the two side rims via two universal joint shafts 10, respectively.
• the guide sleeve of the suspension cylinder 20 is fixed on the frame 30, and the lower end of the piston rod is connected with the wheel wheel edge to support the frame and buffer the bridge jump.
• the frame of the frame is fixedly connected with the frame, and the universal joint shaft is connected with the wheel edge to realize the transmission of force;
• the rocker arm 50 of the steering mechanism is mounted on the suspension cylinder guide sleeve, Rolling bearings are installed between them, which can rotate relative to each other.
• the boosting cylinder drives the steering rocker to rotate, and the steering rocker drives the rotation of the trapezoidal arm that is fixed to the wheel to realize the steering of the wheel.
• the existing independent suspension system has the following disadvantages: First, the side of the suspension cylinder guide sleeve is connected to the frame, the lower end of the piston rod is connected to the wheel wheel edge, and the weight of the body and the ground are applied to the tire. All the reaction forces act on the suspension cylinder, which is subject to large forces and is prone to wear and affect the service life.
• the whole steering mechanism is installed above the final drive, and the knuckle arm is fixed outside the cylinder sleeve, so that the minimum clearance between the final drive and the ground cannot be effectively controlled, and the passing passability is poor.
• the present invention provides an independent suspension system, which can reduce or even completely avoid the destructive influence of the suspension cylinder through structural improvement, thereby reliably achieving independent movement of the left and right wheels and making full use of the adhesion conditions of the road surface. , greatly improve the handling stability of the whole machine. Based on this, the present invention also provides a crane having the independent suspension system.
• the independent suspension system comprises: two suspension cylinders respectively disposed between the wheel sides of the wheels on both sides and the frame; a steering mechanism for driving the wheels on both sides under the driving of the steering assist cylinder;
• the utility model comprises two swinging rods corresponding to the wheels on both sides, one side end of each of the swinging rods is hinged to the wheel side of the corresponding side wheel by a ball hinge, and the other side end is passed back and forth by two ball hinges The direction is hinged to a fixing member fixed to the underside of the frame.
• the method further includes two accumulators, wherein the oil port of the first accumulator is in communication with the rodless cavity of the suspension cylinder on the left side and the rod cavity of the suspension cylinder on the right side, the second accumulator The port is connected to the rodless cavity of the suspension cylinder on the right side and the rod cavity of the suspension cylinder on the left side.
• the suspension cylinder includes a matching piston and a cylinder; and further includes: an inner protective casing, disposed on an outer side of the cylinder, and one end of the inner protective casing and a piston rod of the piston An outlet end fixedly connected, the other end having a radially outwardly extending inner limiting portion; and an outer protective casing disposed on an outer side of the inner protective casing, one end of the outer protective casing and the bottom of the cylinder a fixed connection, the other end has a radially inwardly extending outer limiting portion, the outer limiting portion is slidably engaged with the outer wall of the inner protective casing; and the hanging cylinder is located at a maximum working stroke, the inner side
• the limiting portion and the outer limiting portion are axially phased by four.
• the protruding end of the piston rod of the suspension cylinder is fixedly connected to the frame through a flange end cover, and a buffer is disposed between the protruding end of the piston rod and the flange end cover Elastic padding.
• the elastic pad is spherical
• the flange end cap has a concave curved surface matching the outer surface of the elastic pad
• the protruding end of the piston rod has the elastic pad
• An outer convex curved surface adapted to the inner surface, and extending axially from the outer convex curved surface to form an insertion portion sequentially passing through the elastic pad and the flange end cover, the end portion of the insertion portion being fixed
• a cover plate is disposed, and the cover plate and the flange end cover are arc-faced.
• the end of the piston rod has a rigid connecting member, and the outer convex curved surface and the inserting portion which are matched with the inner surface of the elastic pad are formed on the rigid connecting member.
• the cover plate and the rigid connector are bolted to the end of the piston rod.
• the steering mechanism comprises: two steering rocker arms, one end of each of the steering rocker arms is fixedly connected with the wheel side of the corresponding side wheel; two knuckle arms, each The knuckle arm is pivotally connected to a steering pin fixed to a lower plane of the frame, and one end is respectively used for articulating with a steering assist cylinder; two steering trapezoidal rods, each of the steering trapezoidal rods are hinged to a corresponding side The other end of the steering rocker arm and the other end of the steering knuckle arm And a steering rod hinged between the two knuckle arms for simultaneous steering on both sides; and the knuckle arm, the steering trapezoidal tie rod and the steering rod are located at the front side or the rear of the fixing member side.
• each of the knuckle arms is pivotally coupled to the steering pin of the respective side by an in-line bearing.
• the fixing member is specifically a speed reducer, and an upper surface thereof is fixedly connected to a bottom surface of the frame; two universal joint shafts corresponding to the two sides of the wheel are respectively hinged to the output end of the speed reducer and Between the wheel reducers of the respective side wheels.
• the swing lever is a "V"-shaped swing lever, and both ends of the rod separation of the "V"-shaped swing lever are hinged to the outer casing of the reducer.
• the crane provided by the present invention comprises a wheeled chassis, and the wheels on both sides of each shaft of the chassis are connected to the frame through a suspension system; the wheels on both sides of each shaft respectively adopt an independent suspension system as described above.
• the independent suspension system provided by the present invention is provided with two swing bars, which are respectively arranged corresponding to the wheels on both sides. Specifically, one end of the swing bar is hinged to the wheel side of the corresponding side wheel by a ball hinge, and the other end is hinged by a ball hinge in a front-rear direction and a fixing member fixed under the final reducer respectively. .
• the swing rod itself can achieve a certain rotation around the forward direction of the vehicle and the vertical ground direction, thereby realizing the positioning of the tire mounted on the wheel side, and ensuring that the movement of the tire during the running of the crane meets the design requirements.
• the two pendulum rods can play the dual role of positioning the tire and withstanding the reaction force from the road surface, ensuring that the wheel track remains consistent when the wheel is bouncing up and down, and at the same time, only the ground support is supported during the expansion and contraction of the suspension cylinder.
• the force and force state are effectively improved, and the lateral stiffness of the suspension is improved.
• the piston rod between the suspension cylinder and the cylinder can avoid the severe wear caused by the radial force.
• the wheel gauge of the whole vehicle can be reliably controlled within the allowable range, which can effectively reduce the lateral direction of the tire.
• the independent suspension system has the characteristics of low unsprung mass, the impact load received by the suspension and transmitted to the vehicle body is small, and the jumping of the left and right side wheels does not directly affect each other, and the vehicle body can be greatly reduced.
• the control principle of the suspension cylinder is optimized, and the oil port of the first accumulator is connected to the rodless cavity of the left suspension cylinder and the rod cavity of the right suspension cylinder, and the second storage
• the oil port of the energy device is connected to the rodless cavity of the right suspension cylinder and the rod cavity of the left suspension cylinder.
• the hydraulic oil is replenished, so that the rodless cavity of the right suspension cylinder is compressed, and the right side suspension cylinder without the rod chamber hydraulic oil enters the right accumulator, and the right accumulator hydraulic oil pressure also increases; to maintain balance, right side
• the accumulator replenishes the hydraulic fluid with the rod cavity to the shocked left suspension cylinder, and the suspension cylinders on both sides pass through, so that the vibration generated by the impact of the wheel is rapidly attenuated, and the attenuation is not required by the suspension cylinder of complicated structure.
• the hydraulic fluid on the impact side enters the rod cavity of the other side of the suspension cylinder, which can improve the roll stiffness of the whole machine and reduce the roll angle of the whole machine, especially in the turning process.
• the specific structure of the suspension cylinder is further optimized.
• the suspension cylinder further includes: an inner protective casing, which is disposed on the inner side of the cylinder, outside the piston rod, and one end of the inner protective shell and the piston rod protruding end of the piston Fixed connection, the other end has an outwardly extending inner limiting portion; an outer protective casing is disposed on the outer side of the inner protective casing, one end of the outer protective casing is fixedly connected with the bottom of the cylinder tube, and the other end has an inward extension
• the outer limiting portion specifically, the sliding engagement between the outer limiting portion and the outer wall of the inner protective shell realizes the guiding action of the suspension cylinder, and the piston rod and the cylinder tube are matched
• the oil passage of the suspension cylinder is realized to realize the function of the suspension system; and when the suspension cylinder is at the maximum working stroke, the inner limiting portion and the outer limiting portion axially abut each other.
• Another preferred embodiment of the present invention further optimizes the application of the transaxle, and the reducer is directly fixedly connected to the lower surface of the frame, and the minimum ground clearance of the whole machine is effectively increased, thereby significantly improving the vehicle passing property; especially when the suspension cylinder is When the machine is extended, the reducer can be raised synchronously with the frame, and the passability of the whole machine is significantly improved.
• reduce the spatial angle of the arrangement of the whole drive system realize the minimum change of the angle of the drive shaft during the whole vehicle up and down, and improve the reliability of the transmission system.
• the trapezoidal tie rods that connect the left and right side wheel edges and realize the synchronous corner relationship of the left and right tires adopt a disconnected structure, that is, the two steering trapezoidal pull rods respectively realize the assist of the steering cylinder and the synchronous rotation angle of the left and right tires, and the knuckle arm,
• the steering trapezoidal pull rod and the steering pull rod are both located on the front side or the rear side of the fixing member. This arrangement can further reduce the distance between the reducer and the lower surface of the frame, and improve the passability of the whole machine.
• the independent suspension system provided by the present invention is suitable for use in any form of construction machinery chassis, particularly for cranes.
• FIG. 1 is a schematic structural view of a typical independent suspension system in the prior art
• FIG. 2 is a side view of FIG.
• FIG. 3 is a front view of an independent suspension system according to an embodiment of the present invention.
• FIG. 4 is a top plan view of an independent suspension system according to an embodiment of the present invention.
• Figure 5 is a schematic side view showing the "V"-shaped pendulum of the independent suspension system according to the embodiment of the present invention.
• Figure 6 is a plan view of the "V"-shaped pendulum shown in Figure 6;
• Figure 7 is a side elevational view of the independent suspension system shown in Figure 3;
• FIG. 8 is a schematic diagram of the axial measurement of the suspension cylinder of the independent suspension system according to an embodiment of the present invention.
• Figure 9 is a cross-sectional view of the suspension cylinder shown in Figure 8.
• Suspension cylinder 1 piston 11, piston rod 111, convex curved surface 1111, insertion portion 1112, rigid connecting member 1113, flange end cover 112, concave curved surface 1122, elastic gasket 113, cover plate 114, bolt 115 , cylinder 12, connecting flange 121, inner protective shell 13, inner limiting portion 131, outer protective shell 14, outer limiting portion 141, leakage chamber 15, wheel edge 21, wheel reducer 22, steering mechanism 3.
• the invention provides an independent suspension system, which reduces the radial load on the suspension cylinder and ensures the independent movement of the left and right wheels, thereby improving the handling stability of the whole machine and reducing the maintenance cost.
• FIG. 3 is a front view of an independent suspension system according to an embodiment of the present invention, which is a view formed from a front-rear direction
• FIG. 4 is an independent suspension system according to an embodiment of the present invention. Top view.
• the two suspension cylinders 1 of the independent suspension system are arranged on the sides of the wheels on both sides of the wheel 21 and the frame
• the upper hinge point of the suspension cylinder 1 is coupled to the support on the frame, and the lower hinge point is coupled to the ball hinge point on the wheel edge 21 to absorb vertical vibration and mitigate the impact.
• the steering mechanism 3 is used to drive the steering of the wheels on both sides under the drive of a steering assist cylinder (not shown). In this scheme, it corresponds to the wheels on both sides.
• the speed reducer 5 fixed to the underside of the frame is hinged by a ball hinge.
• the speed reducer 5 is an axle final drive of the chassis, and its upper surface is fixedly connected to the bottom surface of the frame 8.
• the specific structure of the "ball hinge" is not limited to the structural form shown in the drawing, as long as the relative rotation of the two spherical members around the common center can be realized, and the relative movement of the three directions is restricted in the present application. Within the scope of protection.
• the rod connecting end of the "V"-shaped pendulum rod refers to the joint connecting portion of the two rod bodies constituting the "V” shape; accordingly, the rod ends of the "V"-shaped pendulum rod are separated at both ends
• the part refers to a non-joined connection portion of two rods constituting a "V” shape, that is, an open end.
• FIG. 5 is a schematic view of the shaft side of the "V"-shaped pendulum rod in the embodiment
• FIG. 6 is a plan view of the "V"-shaped pendulum rod.
• the two "V"-shaped pendulum rods 4 can play the dual role of positioning the tire and withstanding the reaction force from the road surface, ensuring that the wheel track remains consistent when the wheel is bouncing up and down, and at the same time, stretching and contracting on the suspension cylinder In the process, only the ground reaction force is received, and the force state is effectively improved.
• this solution is not limited to the transaxle, that is, the "V"-shaped pendulum 4 is applied to the suspension system and can be applied to non-drive axles.
• the axle is a load-bearing bridge
• a fixing member directly fixed to the lower surface of the frame is used, so as to be an articulated joint member at both ends of the rod of the swinging rod, which corresponds to the bearing connection of the outer casing of the reducer effect.
• the speed reducer of the present embodiment has the function of carrying a "V"-shaped pendulum rod 4.
• the "V"-shaped pendulum rod is taken as an example to describe in detail the function of positioning the tire on the wheel side.
• the pendulum rod can also adopt other forms, as long as the pendulum rod is One side end passes through a ball hinge and the wheel of the corresponding side wheel The side hinge is hinged, and the other end portion thereof is respectively hinged by a two ball hinge in a front-rear direction and a fixing member fixed under the main reducer.
• the power transmission output mode as the transaxle can be realized by the prior art, and the two universal joint shafts 6 corresponding to the wheels on both sides are respectively hinged to the output end of the speed reducer 5 and the wheel side reducer of the corresponding side wheel. Between 22.
• the steering mechanism for achieving the steering operation can be further optimized to achieve better overall machine throughput.
• the figure is a side elevational view of the independent suspension system of Figure 3 with one side of the wheel omitted to clearly illustrate the steering mechanism.
• the trapezoidal tie rod of the steering mechanism which realizes the synchronous angle relationship between the two sides of the tire adopts a disconnected structure, and is disposed corresponding to the wheels on both sides.
• the first ends of the two steering rocker arms 31 are respectively hinged with the wheel edges 21 of the respective side wheels, so that the steering driving force acts on the wheels;
• the two knuckle arms 32 are respectively fixed to the lower plane fixed to the frame 8
• the pin shaft 33 is pivotally connected, and the first end is respectively used for articulating with a steering assist cylinder (not shown);
• the two steering trapezoidal rods 34 are respectively hinged to the second end of the corresponding side steering rocker arm 31 and the knuckle arm Between the second ends of 32, thereby achieving a connection of each side wheel mechanism;
• a steering tie rod 35 is hinged between the two knuckle arms 32 for simultaneous steering on both sides; and the knuckle arm 32, the steering trapezoidal pull rod 34 and the steering
• each knuckle arm 32 is pivotally connected to the corresponding side of the steering pin shaft 33 by an in-line bearing (not shown), and the steering mechanism rolling action is achieved during assembly of the steering mechanism, the bearing being assembled on the steering pin shaft 33 On the top, it is possible to rotate the trapezoidal mechanism when turning.
• the control of the suspension cylinders on both sides in this solution can also be optimized.
• the oil port of the first accumulator 71 communicates with the rodless cavity of the left suspension cylinder 1 and the rod cavity of the right suspension cylinder 1, and the second accumulator 72 The port is connected to the rodless cavity of the right suspension cylinder 1 and the rod cavity of the left suspension cylinder 1.
• the right-hand suspension cylinder without rod cavity hydraulic oil enters the right accumulator, and the right accumulator hydraulic oil pressure also increases; to maintain balance, the right accumulator
• the left side suspension cylinder that is subjected to the impact is supplemented with hydraulic oil by the rod cavity, and the suspension cylinders on both sides pass through, so that the vibration formed by the impact of the wheel is rapidly attenuated, and the attenuation is not required by the suspension cylinder of complicated structure.
• the hydraulic fluid on the impact side enters the rod cavity of the other side suspension cylinder, which can improve the roll stiffness of the whole machine and reduce the roll angle of the whole machine.
• the oil and gas suspension control can be matched with the independent suspension axle. Combined, the quality of the unsprung load is greatly reduced, thereby improving the smoothness of the whole machine.
• FIG. 8 is a schematic view showing the suspension of the suspension cylinder in the embodiment
• FIG. 9 is a cross-sectional view of the suspension cylinder shown in FIG.
• the suspension cylinder 1 is double-layered with a further enhanced damping function.
• the inner protective shell 13 is sleeved on the outer side of the cylinder tube 12.
• One end of the inner protective shell 13 is fixedly connected with the protruding end of the piston rod 111 of the piston 11, and can move axially with the piston rod 111, and the other end
• the inner limiting portion 131 has a radially outwardly extending portion;
• the outer protective shell 14 is disposed on the outer side of the inner protective shell 13, and one end of the outer protective shell 14 is fixedly connected with the bottom of the cylinder tube 12, that is, the two are relatively fixed
• the other end has a radially inwardly extending outer limiting portion 141.
• the outer limiting portion 141 is slidably engaged with the outer wall of the inner protective casing 13, that is, when the inner protective casing 13 is displaced synchronously with the piston rod 111, the outer protective casing 14 and the cylinder tube 12 are relatively fixed. Without moving, the outer limiting portion 141 on the upper side and the outer wall of the inner protective casing 13 slide relative to each other, so that the guiding action is matched with the piston rod of the suspension cylinder to achieve reliable positioning of the tires on both sides.
• the inner limiting portion 131 and the outer limiting portion 141 are respectively formed in a radial direction, so that the inner protective shell 13 and the outer protective shell 14 are spaced apart from each other to form a leakage chamber 15 for accommodating oil leakage, which can be further improved.
• the inner limiting portion 131 and the outer limiting portion 141 are axially phased by four, thereby having the function of limiting the position, and the force state of the head of the piston 11 at the extreme position can be improved. .
• one end of the piston rod of the suspension cylinder 1 is fixedly connected to the frame 8 through the flange end cover 112, and the 12-end end of the cylinder tube is also fixedly connected to the wheel edge 21 through the connecting flange 121.
• a cushioning elastic gasket 113 may be disposed between the protruding end of the piston rod 111 and the flange end cover 112 to prevent the suspension cylinder 1 from jumping up and down due to the axle. Wear caused by lateral forces.
• the elastic pad 113 has a spherical shape
• the flange end cover 112 has a concave curved surface 1122 adapted to the outer surface of the elastic pad 113.
• the protruding end of the piston rod 111 has a resilient pad 113.
• An outer convex curved surface 1111 adapted to the inner surface, and extending axially from the outer convex curved surface 1111 to form an insertion portion 1112 sequentially passing through the elastic mattress 113 and the flange end cover 112, the end of the insertion portion 1112
• the cover portion 114 is fixedly disposed, and the cover plate 114 and the flange end cover 112 are arc-faced to accommodate the displacement of the suspension cylinder 1 relative to the frame.
• the elastic pad 113 is deformed to avoid friction between the piston rod of the suspension cylinder 1 and the guide sleeve due to the tire runout.
• the outer convex curved surface 1111 and the insertion portion 1112 may be formed on the body of the piston rod 111, that is, integrally formed; or a rigid connecting member 1113 may be formed at the end of the piston rod 111, and the elastic gasket 113
• the inner convex surface 1111 and the insertion portion 1112 which are adapted to the inner surface are formed on the rigid connecting member 1113, thereby reducing the processing difficulty and the processing cost.
• the cover plate 114 and the rigid connecting member 1113 are fixed to the end of the piston rod 111 by bolts 115.
• the two-chamber oil passages of the suspension cylinder 1 are all disposed on the piston rod 111, wherein the piston has a rod chamber oil passage A and a piston rod-free chamber slide channel B respectively connected to the two chambers, which can be realized by using the prior art, Let me repeat.
• the present embodiment also provides an application of the independent suspension system.
• the cranes on both sides of each wheel of the wheeled chassis are connected to the frame through the aforementioned independent suspension system to realize the independent movement of the left and right tires, fully utilizing the adhesion conditions of the road surface, and improving the handling stability of the whole machine.
• the chassis structure, electrical system, hoisting system, power system and other functional components of the crane can be implemented by using the prior art, and thus will not be described herein.

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• Mechanical Engineering (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Transportation (AREA)
• Vehicle Body Suspensions (AREA)
• Steering-Linkage Mechanisms And Four-Wheel Steering (AREA)

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• 2014
  • 2014-01-27 CN CN201410040359.1A patent/CN103738136B/zh active Active
  • 2014-04-03 RU RU2016119018A patent/RU2647115C2/ru active
  • 2014-04-03 WO PCT/CN2014/074735 patent/WO2015109659A1/zh not_active Ceased
  • 2014-04-03 US US15/035,126 patent/US9796233B2/en active Active
  • 2014-04-03 CA CA2926583A patent/CA2926583C/en active Active
  • 2014-04-03 EP EP14879594.1A patent/EP3100881B1/en active Active
  • 2014-04-03 AU AU2014379036A patent/AU2014379036B2/en active Active

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