CN112744039A - Independent rocker arm vehicle chassis suspension system of amphibious vehicle - Google Patents
Independent rocker arm vehicle chassis suspension system of amphibious vehicle Download PDFInfo
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- CN112744039A CN112744039A CN202110191622.7A CN202110191622A CN112744039A CN 112744039 A CN112744039 A CN 112744039A CN 202110191622 A CN202110191622 A CN 202110191622A CN 112744039 A CN112744039 A CN 112744039A
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- bevel gear
- transmission
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G3/00—Resilient suspensions for a single wheel
- B60G3/02—Resilient suspensions for a single wheel with a single pivoted arm
- B60G3/12—Resilient suspensions for a single wheel with a single pivoted arm the arm being essentially parallel to the longitudinal axis of the vehicle
- B60G3/14—Resilient suspensions for a single wheel with a single pivoted arm the arm being essentially parallel to the longitudinal axis of the vehicle the arm being rigid
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D3/00—Steering gears
- B62D3/02—Steering gears mechanical
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- 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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2200/00—Indexing codes relating to suspension types
- B60G2200/10—Independent suspensions
- B60G2200/13—Independent suspensions with longitudinal arms only
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2500/00—Indexing codes relating to the regulated action or device
- B60G2500/30—Height or ground clearance
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Steering-Linkage Mechanisms And Four-Wheel Steering (AREA)
Abstract
The invention relates to an independent rocker arm vehicle chassis suspension system of an amphibious vehicle, which comprises an independent rocker arm tensioner arranged on a vehicle body frame or a vehicle bottom frame, wherein the independent rocker arm tensioner comprises a body frame connecting fixing disc, a front rocking disc and a rear rocking disc which enclose an internal cavity space, a synchronizer, a bevel gear reducing wheel I and a bevel gear reducing wheel II are arranged on an extended driving transmission shaft, a front rocking arm annular spring, a rear rocking arm annular spring, a front rocking arm hydraulic spring push-pull device and a rear rocking arm hydraulic spring push-pull device are further arranged. The swing arm moves around the tension through ring spring drives to realize the regulation of vehicle ground clearance, the vehicle bears a burden the back and is used for adjusting the terrain clearance of the automobile body when different road surfaces travel that establish, and can realize the independent shock attenuation of single round, effectively reduces the jolt sense of vehicle when the indiscriminate sign indicating number of pit traveles, can effectively improve the automobile body height through the waters, guarantees normally traveling on the road surface of wading.
Description
Technical Field
The invention belongs to the technical field of automobile suspension accessories, and particularly relates to an independent rocker arm vehicle chassis suspension system of an amphibious vehicle.
Background
The traditional automobile suspension system mainly comprises three types, namely a Macpherson suspension, a five-link rod or a cross arm, which have characteristics and advantages but have disadvantages respectively, and the three types of automobile suspensions have the problems of common use and large influence, namely, the trafficability is limited by a rotating shaft, and the problems of difficulty in realizing relatively independent driving of wheels during vehicle using and difficulty in adjusting the ground clearance of the vehicle are solved. And the three chassis suspension systems can not be applied to amphibious vehicles, the problem of waterlogging in Chinese cities is more and more prominent in recent years, and the normal running of the vehicles on a flooded road is greatly influenced, so that the vehicle capable of realizing certain amphibious is an option for relieving the problem.
Disclosure of Invention
In order to solve the problems, the invention provides the independent rocker arm vehicle chassis suspension system of the amphibious vehicle, which occupies less chassis space, is simple to rotate, has adjustable ground clearance and can be driven independently.
The utility model provides an amphibious vehicle's independent rocking arm vehicle chassis suspension, includes power take off's driving transmission shaft, still including installing the independent rocking arm tensioner on automobile body frame or vehicle bottom frame, independent rocking arm tensioner includes that fixed ear and automobile body frame or vehicle bottom frame fixed connection's automobile body frame connection fixed disk is connected through automobile body frame, and automobile body frame connection fixed disk both sides are rotated respectively and are installed preceding rocking disc and back rocking disc, and body frame connection fixed disk, preceding rocking disc and back rocking disc enclose into an interior cavity space, driving transmission shaft extends into in this space, and installs the synchronous ware on the driving transmission shaft that extends into.
And bevel gear speed reducing wheels I are arranged on driving transmission shafts in the front swing disc and bevel gear speed reducing wheels II are symmetrically arranged on driving transmission shafts in the rear swing disc on two sides of the synchronizer.
Preceding rocking disc is kept away from the initiative transmission shaft terminal surface and has been seted up preceding rocking arm adapter sleeve, installs transmission conveying shaft I in the preceding rocking arm adapter sleeve, and transmission conveying shaft I one end extends into preceding rocking disc and installs transmission bevel gear I, and transmission bevel gear I meshes with bevel gear reduction gear I.
The rear swing disc is far away from the end face of the driving transmission shaft and is symmetrical to the front swing arm connecting sleeve, a rear swing arm connecting sleeve is arranged, a transmission conveying shaft II is arranged in the rear swing arm connecting sleeve, one end of the transmission conveying shaft II extends into the rear swing disc and is provided with a transmission bevel gear II, and the transmission bevel gear II is meshed with the bevel gear reducing wheel II.
The body frame is connected with a fixed disc, a front swing disc and a rear swing disc to enclose an internal cavity space, and a front swing arm annular spring, a rear swing arm annular spring, a front swing arm hydraulic spring push-pull device and a rear swing arm hydraulic spring push-pull device are further installed in the internal cavity space.
The front swing arm annular spring is arranged in a space on one side of the front swing disc, the front swing arm annular spring is of a torsion spring structure, one end of the front swing arm annular spring is fixedly connected with the front swing disc, the other end of the front swing arm annular spring is connected with a front swing arm hydraulic spring push-pull device, and the front swing arm hydraulic spring push-pull device is arranged on the body frame connecting fixing disc; the back swing arm annular spring is arranged in a space on one side of the back swing disc, the back swing arm annular spring is of a torsion spring structure, one end of the back swing arm annular spring is fixedly connected with the back swing disc, the other end of the back swing arm annular spring is connected with a back swing arm hydraulic spring push-pull device, and the back swing arm hydraulic spring push-pull device is arranged on the body frame connecting fixing disc.
Further, preferably, the end, far away from the front swing disc, of the front swing arm connecting sleeve is connected with a hollow front swing arm, and the transmission conveying shaft I extends into the front swing arm.
Further, it is preferable that the steering gear further comprises a transmission steering assist device, the transmission steering assist device comprises a steering arm, and the steering arm is connected with the front swing arm through a rotating hollow mechanism capable of realizing rotation and ensuring power transmission.
A movable transmission rod is arranged in the steering arm in a rotating mode, one end of the movable transmission rod extends into the rotating hollow mechanism, and the rotating hollow mechanism drives the movable transmission rod to rotate.
The other end of the movable transmission rod extends into the steering arm and is provided with a movable bevel gear II, a fixed transmission bevel gear II capable of being meshed with the movable bevel gear II is rotatably arranged in the steering arm, a transmission output rod is arranged in a direction vertical to the front swing arm, the transmission output rod extends into the steering arm, the extending end is provided with a transmission output bevel gear capable of being meshed with the fixed transmission bevel gear II, and the transmission output rod is connected with the rotating wheel core; the outside of the steering arm is far away from the wheel end and is hinged with a hydraulic steering push-pull rod.
Further, it is preferred that rotatory cavity mechanism is including fixing the connection revolving rack I on preceding rocking arm, connect revolving rack I through the pivot that sets up from top to bottom with connect II rotational connections of revolving rack, it is fixed with the steering arm to connect revolving rack II, transmission transport axle I passes and connects I extension of revolving rack and goes into the cavity mechanism of changeing, installs power transmission bevel gear on it, install fixed transmission bevel gear I in the pivot, transmission bevel gear and the meshing of fixed transmission bevel gear I, the activity transmission pole passes and connects II extensions of revolving rack and go into the cavity mechanism of changeing, install movable bevel gear I on it, movable bevel gear I and the meshing of fixed transmission bevel gear I.
Further, preferably, the telescopic end of the hydraulic steering push-pull rod is rotatably connected with the steering arm through a rod end connecting ball head.
Furthermore, it is preferred that the other end in preceding rocking disc corresponding to drive bevel gear I is provided with location bevel gear I, location bevel gear I is the same with the meshing of bevel gear deceleration wheel I.
Further, it is preferable that a positioning bevel gear II is arranged at the other end of the rear swing disc corresponding to the transmission bevel gear II, and the positioning bevel gear II is meshed with the bevel gear reducer II.
Further, it is preferred that the front wobble plate and the rear wobble plate are rotatably connected to the frame connecting fixing plate through a cylindrical ball positioning bearing.
The invention has the beneficial effects that:
1. the swing arm moves around the tension through ring spring drives to realize the regulation of vehicle ground clearance, the vehicle bears a burden the back and is used for adjusting the terrain clearance of the automobile body when different road surfaces travel that establish, and can realize the independent shock attenuation of single round, effectively reduces the jolt sense of vehicle when the indiscriminate sign indicating number of pit traveles, can effectively improve the automobile body height through the waters, guarantees normally traveling on the road surface of wading.
2. The two-wheel drive and four-wheel drive state can be adjusted quickly, and power transmission can be guaranteed.
3. The traditional steering gear and steering pull rod structures are not used any more in the rotating process, the hydraulic steering push-pull rod is controlled by a computer to push the steering arm, the rotating process is realized under the condition that the power is smoothly transmitted, the rapid steering can be realized, and the steering in a smaller steering radius can be realized if the front and the back are simultaneously provided with transmission steering assistance.
Drawings
Fig. 1 is a first power take-off mounting configuration of the independent swing arm vehicle chassis suspension system of the present invention when mounted on an amphibian.
Fig. 2 is a front view of the independent rocker tensioner of the present invention mounted on a vehicle body frame.
FIG. 3 is a cross-sectional view of the independent rocker arm tensioner of the present invention wherein the body frame attachment mounting plate, front and rear swing plates, etc. are half-sectioned to show the internal components thereof.
Fig. 4 is a cross-sectional view of the independent rocker arm tensioner of the present invention, wherein the body frame attachment mounting plate, the front swing plate, the rear swing plate, etc. are shown in half-section to show the internal components thereof, and the synchronizer and the bevel gear reduction gear are shown in partial section.
Fig. 5 is a front view of the independent rocker arm tensioner of the present invention showing the rear rocker arm ring spring and rear rocker arm hydraulic spring push-pull mounting arrangement.
FIG. 6 is a top cross-sectional view of the driven steering assist of the present invention with the steering arm, front swing arm, etc. in section.
Fig. 7 is a sectional view a-a in fig. 6.
Fig. 8 is a side view of the rod end connecting bulb of fig. 6 connected to the steering arm.
Fig. 9 shows a power take-off mounting combination configuration of the independent swing arm vehicle chassis suspension system of the present invention when mounted on an amphibian.
Fig. 10 is a power take-off mounting combination configuration three achieved when the independent swing arm vehicle chassis suspension system of the present invention is mounted on an amphibian.
In the upper diagram: 100-a vehicle body frame, 201 a motor, 202-a middle gearbox, 203-a differential, 204-a front power, 205-a driving transmission shaft, 206-an inert gas spring damping and shock absorbing device, 207-a brake caliper, 208-a brake disc and 209-a rotating wheel core;
1-independent rocker arm tensioner, 10-vehicle body frame connecting fixed disc, 1001-vehicle body frame connecting fixed lug, 1002-annular spring mounting separation plate, 20-front rocking disc, 2001-transmission shaft I, 2002-transmission bevel gear I, 2003-positioning bevel gear I, 2004-bevel gear reducer I, 2005-front rocking arm connecting sleeve, 2006-front rocking arm, 30-synchronizer, 3001-four gear shift fork, 40-rear rocking disc, 4001-transmission shaft II, 4002-transmission bevel gear II, 4003-positioning bevel gear II, 4004-bevel gear reducer II, 4005-rear rocking arm connecting sleeve, 4006-rear rocking arm, 5001-ball positioning bearing, 5002-rotary low friction bearing, 5003-ball positioning bearing, 5004-waterproof sliding copper ring, 6001-front swing arm ring spring, 6002-rear swing arm ring spring, 6003-front swing arm hydraulic spring push-pull, 6004-rear swing arm hydraulic spring push-pull;
2-transmission steering assistor, 70-hydraulic steering push-pull rod, 7001-rod end connecting ball head, 80-rotating hollow mechanism, 8001-connecting rotating frame I, 8002-connecting rotating frame II, 8003-rotating shaft, 8004-fixed transmission bevel gear I, 8005-bearing, 8006-power transmission bevel gear, 8007-movable bevel gear I, 90-steering arm, 9001-movable bevel gear II, 9002-movable transmission rod, 9003-steering transmission positioning bevel gear, 9004-fixed transmission bevel gear II, 9005-transmission output rod and 9006-transmission output bevel gear.
Detailed Description
In order to make the technical problems and technical solutions solved by the present invention more clearly apparent, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
Example 1:
as shown in fig. 1 and 2, an independent rocker arm vehicle chassis suspension system of an amphibious vehicle comprises an independent rocker arm tensioner 1 mounted on a vehicle body frame 100, although the independent rocker arm tensioner 1 can also be mounted on a vehicle bottom frame, which are all equivalent technologies of the present technical characteristics.
The active drive shaft 205 can be directly connected to the motor 201, and a power source can be provided to the active drive shaft 205 through the motor 201.
As shown in fig. 3 to 5, the independent rocker tensioner 1 includes a body frame connecting fixing plate 10 fixedly connected to the body frame 100 through a body frame connecting fixing lug 1001, a front swing plate 20 and a rear swing plate 40 are rotatably mounted on two sides of the body frame connecting fixing plate 10, the front swing plate 20 and the rear swing plate 40 enclose an inner cavity space, and the front swing plate 20 and the rear swing plate 40 are rotatably connected to the body frame connecting fixing plate 10 through a cylindrical ball positioning bearing 5001.
The driving transmission shaft 205 extends into the space, that is, the driving transmission shaft 205 is perpendicular to the large surface of the front swing plate 20, passes through the front swing plate 20 and extends into the front swing plate, a synchronizer 30 is installed in the middle of the driving transmission shaft 205, that is, the frame connecting fixing plate 10, and the synchronizer 30 is provided with a four-gear shift fork 3001 in a matching way.
On both sides of the synchronizer 30, a bevel gear reducer I2004 is mounted on the driving transmission shaft 205 in the front swing plate 20, and a bevel gear reducer II 4004 is symmetrically mounted on the driving transmission shaft 205 in the rear swing plate 40.
The end face, far away from the driving transmission shaft 205, of the front swing plate 20 is provided with a front swing arm connecting sleeve 2005, a transmission conveying shaft I2001 is installed in the front swing arm connecting sleeve 2005 through a ball positioning bearing 5003, one end of the transmission conveying shaft I2001 extends into the front swing plate 20 and is provided with a transmission bevel gear I2002, the transmission bevel gear I2002 is meshed with a bevel gear reduction wheel I2004, the other end, corresponding to the transmission bevel gear I2002, of the front swing plate 20 is provided with a positioning bevel gear I2003, and the positioning bevel gear I is meshed with the bevel gear reduction wheel I2004 to guarantee the transmission stability of the bevel gear reduction wheel I2004.
The end, far away from the front swing disc 20, of the front swing arm connecting sleeve 2005 is connected with a hollow front swing arm 2006, the transmission conveying shaft I2001 extends into the front swing arm 2006, and a plurality of ball positioning bearings 5003 for ensuring the position of the transmission conveying shaft I are mounted in the front swing arm 2006.
The rear swing plate 40 is far away from the end face of the driving transmission shaft 205, the front swing arm connecting sleeve 2005 is symmetrical and provided with a rear swing arm connecting sleeve 4005, a transmission conveying shaft II 4001 is arranged in the rear swing arm connecting sleeve 4005 through a ball positioning bearing 5003, one end of the transmission conveying shaft II 4001 extends into the rear swing plate 40 and is provided with a transmission bevel gear II 4002, the transmission bevel gear II 4002 is meshed with a bevel gear reduction gear II 4004, a positioning bevel gear II 4003 is arranged at the other end in the rear swing plate 40 corresponding to the transmission bevel gear II 4002, and the positioning bevel gear II 4003 is also meshed with the bevel gear reduction gear II 4004 to guarantee the stability of transmission of the bevel gear reduction gear II 4004.
The end, far away from the front and rear swing disc 40, of the rear swing arm connecting sleeve 4005 is connected with a hollow rear swing arm 4006, the transmission conveying shaft II 4001 extends into the rear swing arm 4006, and a plurality of ball positioning bearings 5003 for ensuring the position of the transmission conveying shaft II 4001 are arranged in the rear swing arm 4006.
A front swing arm annular spring 6001, a rear swing arm annular spring 6002, a front swing arm hydraulic spring push-pull device 6003 and a rear swing arm hydraulic spring push-pull device 6004 are further arranged in an internal cavity space surrounded by the frame connecting fixed disc 10, the front swing disc 20 and the rear swing disc 40; as shown in fig. 3, 4 and 5, the front swing arm annular spring 6001 is installed in a space on one side of the front swing plate 20, the front swing arm annular spring 6001 is a torsion spring structure, one end of the front swing arm annular spring 6001 is fixedly connected to the front swing plate 20, the other end of the front swing arm annular spring 6003 is connected to the front swing arm hydraulic spring push-pull device 6003, and the front swing arm hydraulic spring push-pull device 6003 is installed on the body frame connection fixing plate 10; similarly, the rear swing arm annular spring 6002 is installed in a space on one side of the rear swing disc 40, the rear swing arm annular spring 6002 is of a torsion spring structure, one end of the rear swing arm annular spring 6002 is fixedly connected with the rear swing disc 40, the other end of the rear swing arm annular spring 6002 is connected with the rear swing arm hydraulic spring push-pull device 6004, and the rear swing arm hydraulic spring push-pull device 6004 is installed on the frame connection fixing disc 10; the front swing arm annular spring 6001 and the rear swing arm annular spring 6002 are installed in opposite directions, the front swing plate 20 and the rear swing plate 40 are driven to rotate by the twisting tension of the front swing arm annular spring 6001 and the rear swing arm annular spring 6002, namely, the twisting amount of the front swing arm annular spring 6001 and the rear swing arm annular spring 6002 is changed by the stretching of a push rod of the front swing arm hydraulic spring push-pull device 6003 and the rear swing arm hydraulic spring push-pull device 6004, so that the front swing arm annular spring 6001 and the rear swing arm annular spring 6002 drive the front swing plate 20 and the rear swing plate 40 to rotate by a certain angle (alpha angle shown in the figure), thereby realizing the adjustment of the distance between the front and the rear wheels of the vehicle, realizing the adjustment of the gap between the vehicle body and the ground, simultaneously realizing the independent damping of a single wheel, and effectively reducing the bumping sense of the vehicle when.
The synchronizer 30 is controlled by a four-gear shifting fork 3001 to realize the conversion control of two-drive and four-drive; which is different from the traditional transfer case type transfer case.
The front swing arm 2006 is designed on the inner side of the vehicle body frame 100, and mainly provides a necessary steering space for a front wheel during steering, the front swing arm 2006 mainly provides driving and steering functions for the front wheel, and further an inert gas spring damping and shock absorption device 206 can be installed on a steering knuckle.
Example 2:
the present embodiment is different from embodiment 1 in that the present embodiment further includes a power steering assist device 2, as shown in fig. 1 and 6, which is connected to the power steering assist device 2 to change the direction of the vehicle when the front swing arm 2006 is steered.
The steer-by-wire assist 2 includes a steering arm 90, the steering arm 90 being connected to the front swing arm 2006 by a rotating hollow mechanism 80 that allows rotation while providing power transmission.
As shown in fig. 6 and 7, the rotary hollow mechanism 80 comprises a connecting rotary stand i 8001 fixed on a front swing arm 2006, the connecting rotary stand i 8001 is rotatably connected with a connecting rotary stand ii 8002 through a rotating shaft 8003 arranged up and down, the connecting rotary stand ii 8002 is fixed with a steering arm 90, a transmission conveying shaft i 2001 extends into the rotary hollow mechanism 80 through the connecting rotary stand i 8001, a force transmission bevel gear 8006 is installed on the transmission conveying shaft 8001, a fixed transmission bevel gear i 8004 is installed on the rotating shaft 8003, the transmission bevel gear 8006 is meshed with the fixed transmission bevel gear i 8004 and drives the fixed transmission bevel gear i 8004 to rotate, a movable transmission rod 9002 is rotatably arranged in the steering arm 90, the movable transmission rod 9002 extends into the rotary hollow mechanism 80 through the connecting rotary stand ii 8002, a movable bevel gear i 8007 is installed on the movable bevel gear i 8007, the movable bevel gear i 8007 is meshed with the fixed transmission bevel gear i 8004, namely, the fixed transmission bevel gear 8004 is driven to rotate by the transmission bevel gear 8006, the fixed transmission bevel gear I8004 drives the movable bevel gear I8007 to further drive the movable transmission rod 9002 to rotate.
The other end of the movable transmission rod 9002 extends into the steering arm 90 and is provided with a movable bevel gear II 9001, the steering arm 90 is internally and rotatably provided with a fixed transmission bevel gear II 9004 capable of being meshed with the movable bevel gear II 9001, a transmission outlet rod 9005 is vertically arranged in the direction of the front swing arm 2006, the transmission outlet rod 9005 extends into the steering arm 90, the extension inlet end is provided with a transmission output bevel gear 9006 capable of being meshed with the fixed transmission bevel gear II 9004, namely the movable bevel gear II 9001 rotates to drive the fixed transmission bevel gear II 9004 to rotate so as to drive the transmission output rod 9005 to rotate, in order to ensure the stability of the rotation output, the steering arm 90 is further internally and rotatably provided with a steering transmission positioning bevel gear 9003 through a bearing, the transmission outlet rod 9005 is connected with a rotating wheel core 209 and drives the wheel to move in a shaft transmission mode, the rotating wheel core 209 is externally provided with a brake caliper 207 and a brake disc, the brake caliper 207 is fixed to the steering gear.
The steering arm 90 is hinged with a hydraulic steering push-pull rod 70 at the end far away from the wheel on the outer side, and the telescopic end of the hydraulic steering push-pull rod 70 is rotatably connected with the steering arm 90 through a rod end connecting ball 7001, as shown in fig. 8.
Further, can design spacing tightening belt on steering arm 90, drive tape winder or winding draw pulley through the motor, prevent through spacing tightening belt that the swing arm downstream is excessive.
Example 3:
as shown in fig. 9, the present embodiment differs from the first and second embodiments in that the drive shaft 205 can be connected to the centrally located transmission 203 for transmission to a power source.
Example 4:
as shown in fig. 10, the present embodiment differs from the first and second embodiments in that the drive shaft 205 can be connected to the front power source 204 through the differential 203, but of course can be connected to the rear-to-power source through the differential 203.
The present invention has been described in detail with reference to the specific and preferred embodiments, but it should be understood by those skilled in the art that the present invention is not limited to the embodiments described above, and any modifications, equivalents and the like, which are within the spirit and principle of the present invention, should be included in the scope of the present invention.
Claims (8)
1. An independent rocker arm vehicle chassis suspension system for an amphibian comprising a power take off drive shaft (205), characterized in that: the automobile body frame tensioner comprises an automobile body frame connecting fixed disc (10), an independent rocker arm tensioner (1) and a synchronous device (30), wherein the independent rocker arm tensioner (1) is arranged on an automobile body frame (100) or an automobile bottom frame, the automobile body frame connecting fixed disc (10) is fixedly connected with the automobile body frame (100) or the automobile bottom frame through an automobile body frame connecting fixed lug (1001), a front swing disc (20) and a rear swing disc (40) are respectively rotatably arranged on two sides of the automobile body frame connecting fixed disc (10), the front swing disc (20) and the rear swing disc (40) enclose an internal cavity space, a driving transmission shaft (205) extends into the space, and the synchronizer (30) is arranged on the extending driving transmission shaft (205);
bevel gear reduction gears I (2004) are mounted on a driving transmission shaft (205) in the front swing disc (20) on two sides of the synchronizer (30), and bevel gear reduction gears II (4004) are mounted on the driving transmission shafts (205) in the symmetrical rear swing disc (40);
a front swing arm connecting sleeve (2005) is arranged on the end face, away from the driving transmission shaft (205), of the front swing plate (20), a transmission conveying shaft I (2001) is installed in the front swing arm connecting sleeve (2005), one end of the transmission conveying shaft I (2001) extends into the front swing plate (20) and is provided with a transmission bevel gear I (2002), and the transmission bevel gear I (2002) is meshed with a bevel gear reduction wheel I (2004);
a rear swing arm connecting sleeve (4005) is arranged on the end face, far away from the driving transmission shaft (205), of the rear swing disc (40) and symmetrical to the front swing arm connecting sleeve (2005), a transmission conveying shaft II (4001) is installed in the rear swing arm connecting sleeve (4005), one end of the transmission conveying shaft II (4001) extends into the rear swing disc (40) and is provided with a transmission bevel gear II (4002), and the transmission bevel gear II (4002) is meshed with a bevel gear reducing gear II (4004);
a front swing arm annular spring (6001), a rear swing arm annular spring (6002), a front swing arm hydraulic spring push-pull device (6003) and a rear swing arm hydraulic spring push-pull device (6004) are further arranged in an internal cavity space surrounded by the body frame connecting fixed disc (10), the front swing disc (20) and the rear swing disc (40);
the front swing arm annular spring (6001) is arranged in a space on one side of the front swing disc (20), the front swing arm annular spring (6001) is of a torsion spring structure, one end of the front swing arm annular spring is fixedly connected with the front swing disc (20), the other end of the front swing arm annular spring is connected with a front swing arm hydraulic spring push-pull device (6003), and the front swing arm hydraulic spring push-pull device (6003) is arranged on the body frame connecting fixing disc (10); the rear swing arm annular spring (6002) is arranged in a space on one side of the rear swing disc (40), the rear swing arm annular spring (6002) is of a torsion spring structure, one end of the rear swing arm annular spring is fixedly connected with the rear swing disc (40), the other end of the rear swing arm annular spring is connected with a rear swing arm hydraulic spring push-pull device (6004), and the rear swing arm hydraulic spring push-pull device (6004) is arranged on the body frame connecting and fixing disc (10).
2. An amphibious vehicle independent rocker arm vehicle chassis suspension system as claimed in claim 1, characterised in that: the end, far away from the front swing plate (20), of the front swing arm connecting sleeve (2005) is connected with a hollow front swing arm (2006), and the transmission conveying shaft I (2001) extends into the front swing arm (2006).
3. An amphibious vehicle independent rocker arm vehicle chassis suspension system as claimed in claim 2, characterised in that: the power transmission steering assisting device is characterized by further comprising a transmission steering assisting device (2), wherein the transmission steering assisting device (2) comprises a steering arm (90), and the steering arm (90) is connected with the front swing arm (2006) through a rotating hollow mechanism (80) capable of realizing rotation and ensuring power transmission;
a movable transmission rod (9002) is rotatably arranged in the steering arm (90), one end of the movable transmission rod (9002) extends into the rotary hollow mechanism (80), and the rotary hollow mechanism (80) drives the movable transmission rod (9002) to rotate;
the other end of the movable transmission rod (9002) extends into the steering arm (90) and is provided with a movable bevel gear II (9001), the steering arm (90) is internally and rotatably provided with a fixed transmission bevel gear II (9004) capable of being meshed with the movable bevel gear II (9001), a transmission output rod (9005) is arranged in the direction vertical to the front swing arm (2006), the transmission output rod (9005) extends into the steering arm (90), the extension end is provided with a transmission output bevel gear (9006) capable of being meshed with the fixed transmission bevel gear II (9004), and the transmission output rod (9005) is connected with the rotating wheel core (209); the steering arm (90) is hinged with a hydraulic steering push-pull rod (70) at the outer side far away from the wheel end.
4. An amphibious vehicle independent rocker arm vehicle chassis suspension system as claimed in claim 3, characterised in that: rotatory cavity mechanism (80) are including fixing connection revolving rack I (8001) on preceding rocking arm (2006), it is connected through pivot (8003) that sets up from top to bottom to connect revolving rack I (8001) and connect revolving rack II (8002) and rotate and be connected, it is fixed with steering arm (90) to connect revolving rack II (8002), transmission is carried axle I (2001) and is passed and is connected revolving rack I (8001) and extend into in changeing cavity mechanism (80), install powerful transmission bevel gear (8006) on it, install fixed transmission bevel gear I (8004) on pivot (8003), transmission bevel gear (8006) and fixed transmission bevel gear I (8004) mesh, activity transmission pole (9002) pass and connect revolving rack II (8002) and extend into in changeing cavity mechanism (80), install movable bevel gear I (8007) on it, activity bevel gear I (8007) and fixed transmission bevel gear I (8004) mesh.
5. An amphibian independent swing arm vehicle chassis suspension system as claimed in claim 3 or claim 4 wherein: the telescopic end of the hydraulic steering push-pull rod (70) is rotatably connected with the steering arm (90) through a rod end connecting ball head (7001).
6. An amphibious vehicle independent rocker arm vehicle chassis suspension system as claimed in claim 1, characterised in that: and a positioning bevel gear I (2003) is arranged at the other end of the front swing plate (20) corresponding to the transmission bevel gear I (2002), and the positioning bevel gear I (2003) is also meshed with a bevel gear reducer I (2004).
7. An amphibious vehicle independent rocker arm vehicle chassis suspension system as claimed in claim 1, characterised in that: and a positioning bevel gear II (4003) is arranged at the other end in the rear swing disc (40) corresponding to the transmission bevel gear II (4002), and the positioning bevel gear II (4003) is also meshed with a bevel gear speed reducing gear II (4004).
8. An amphibious vehicle independent rocker arm vehicle chassis suspension system as claimed in claim 1, characterised in that: the front swing disc (20) and the rear swing disc (40) are rotatably connected with the body frame connecting fixed disc (10) through cylindrical ball positioning bearings (5001).
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| CN202110191622.7A CN112744039B (en) | 2021-02-20 | 2021-02-20 | Independent rocker arm vehicle chassis suspension system of amphibious vehicle |
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| CN202110191622.7A CN112744039B (en) | 2021-02-20 | 2021-02-20 | Independent rocker arm vehicle chassis suspension system of amphibious vehicle |
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| CN112744039B CN112744039B (en) | 2022-01-04 |
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| KR20070063154A (en) * | 2005-12-14 | 2007-06-19 | 현대자동차주식회사 | Synchronizer of manual transmission |
| US20110148066A1 (en) * | 2009-12-20 | 2011-06-23 | William James Beaujon | Vehicle suspension, steering, damping and anti-roll system with linear wheel travel |
| CN108583159A (en) * | 2018-03-13 | 2018-09-28 | 北京航空航天大学 | A kind of single hydraulic cylinder power-assisted steering drive axle adjusting arm using underneath type |
| CN209226311U (en) * | 2018-11-07 | 2019-08-09 | 杭州千和精密机械有限公司 | A kind of servo tensioner |
| CN211568082U (en) * | 2020-01-20 | 2020-09-25 | 郑州宇通重工有限公司 | Steering power cut-off device, disconnectable steering transmission system and vehicle |
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2021
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| JPH10288227A (en) * | 1997-04-15 | 1998-10-27 | Toyota Motor Corp | Synchronizer |
| CN1450268A (en) * | 2002-04-11 | 2003-10-22 | 倪诗茂 | Suspension type scroll fluid compressor with omnibearing complying structure |
| KR20070063154A (en) * | 2005-12-14 | 2007-06-19 | 현대자동차주식회사 | Synchronizer of manual transmission |
| US20110148066A1 (en) * | 2009-12-20 | 2011-06-23 | William James Beaujon | Vehicle suspension, steering, damping and anti-roll system with linear wheel travel |
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|---|---|
| CN112744039B (en) | 2022-01-04 |
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