CN203528295U - Improved hub motor hydraulic drive system - Google Patents
Improved hub motor hydraulic drive system Download PDFInfo
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- CN203528295U CN203528295U CN201320733953.XU CN201320733953U CN203528295U CN 203528295 U CN203528295 U CN 203528295U CN 201320733953 U CN201320733953 U CN 201320733953U CN 203528295 U CN203528295 U CN 203528295U
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Abstract
The utility model provides an improved hub motor hydraulic drive system which comprises an engine, a power takeoff, a hydraulic control valve group, a hydraulic pump, hydraulic motors and a controller. The improved hub motor hydraulic drive system is characterized in that one end of the power takeoff is connected with an output shaft of a drive accessory of the engine, the other end of the power takeoff is connected with the hydraulic pump mounted on a frame, the hydraulic pump passes the hydraulic control valve group and constitutes a hydraulic closed main oil line with the two hydraulic motors mounted in a front-wheel hub. The controller can realize forward rotation, reversal rotation and inoperation of the hydraulic motors by adjusting different positions of the control valve groups. With the adoption of the system, driving force of a vehicle driving in the bad pavement is increased, the work efficiency of the hub motor hydraulic drive system is further improved, and simultaneously, influences of gear shifting and abrasion of a gearbox to the system are prevented.
Description
Technical field
The utility model relates to a kind of hydrostatic propons assistant drive system, is a set of fluid power system that hydraulic hub motor is housed in the front-wheel hub of heavy-duty vehicle specifically.
Background technology
Can load a large amount of manpower labours' of weight saving commercial vehicle/comm..vehicle, heavy duty truck and engineering truck and in national modernization construction, play the part of important role, people have also proposed more and more higher requirement to them simultaneously.This class vehicle often can run into the smooth road such as the non-firm ground such as road surface, mine, die Dorfstrasse, building ground and mud, ice and snow in the process of moving, and the adhesion value on this class ground is generally less, also has once in a while great slope.
Skidding may appear in traditional single shaft driving automobile in these cases drive wheel, and the crossing ability of automobile is poor.A deficiency that has overcome traditional single shaft-driven vehicle of entirely driving, can effectively utilize adhesive weight, obtains maximum propulsive effort, can obviously strengthen it and pass through performance on severe road surface.But, the operating environment more complicated of car for common engineering, although sometimes have wet-skid road surface or abrupt slope, most of still in smooth good hard surfacing.If entirely driven, on speed and fuel economy, just seem outstanding not in good road surface situation.And, an easy parasitic horsepower that produces of entirely driving, the load that this not only increases Parts for Power Train, makes tire because of the accelerated wear test of too much sliding, and has also reduced driving efficiency and drawbar efficiency simultaneously.
Another kind of solution is on non-driving wheel, to increase a set of electronic assistant drive system.The 4 wheel driven system of similar timesharing, when automobile travels in good road surface, adopts traditional back-wheel drive, and electronic assistant drive system is not used; When running into above-mentioned bad road surface, enable electronic assistant drive system, automobile front and back wheel drives automobile jointly, until close electronic assistant drive system after rolling bad road surface away from.Adopt electric drive system to cancel the parts such as diff, transmission shaft, be not only conducive to realize the lightweight of automobile, also make structurally flexible arrangement of automobile, easily realize energy regeneration braking function.But adopting electric drive wheel to drive needs the parts such as motor, battery, these parts not only price are high, and service life is not long.Meanwhile, electric drive wheel is integrated parts such as motor, drg, the mass penalty that causes non-spring to carry is larger, worsens the Vertical performance of vehicle.
Both need to be under severe road environment for those, the heavy-duty commercial vehicle that need to work on good hard surfacing again, Chinese invention patent application CN102358163A proposes the comprehensive hub hydraulic motor driving system that solves this class Vehicle Driving Cycle problem.It provides a kind of technical scheme that is arranged on the hub hydraulic motor driving system of front-wheel (non-driving wheel), only in the situation that increasing very little cost, can improve significantly automobile and pass through performance on bad road surface.In the system that patent CN102358163A proposes, power takeoff is arranged on transmission countershaft rear end, the power of driving engine output is through the transmission of change speed gear box, a part passes to trailing wheel through transmission shaft, another part power passes to Hydraulic Pump through power takeoff, Hydraulic Pump pumps high pressure oil, drive installation, in the HM Hydraulic Motor work of front-wheel, drives front-wheel.In this case, due to the deceleration effort of change speed gear box, controllable capacity pump often can turn round under slow speed of revolution.
For example, it is example that the vapour J6 heavy-duty commercial vehicle of take adopts the hub hydraulic motor driving system that this patent application provides, and rotating speed during its engine operation is generally:
Ne=700-1900r/min
And this system is all generally to use in the situation that automobile speed is very low, automobile uses when 1,2 gears travel.Change speed gear box 1 gear that J6 heavy-duty commercial vehicle is used and the transmitting ratio of 2 gears are respectively:
ig1=12.1 ig2=9.41
Due to the tween drive shaft mechanical connection of power takeoff and change speed gear box, and its converter speed ratio is 1.So when the residing gear of change speed gear box is 1 gear, the range of speed of controllable capacity pump is:
Nb=Ne/ig1=57.9-157.0r/min
When change speed gear box is in 2 gear, the range of speed of controllable capacity pump is:
Nb=Ne/ig2=74.4-202.0r/min
Comprehensive above two kinds of situations, rotating speed during known controllable capacity pump work is generally at 57.9～202.0r/min
Yet for the heavy goods vehicles that adopts shaft orientation plunger variable pump, the working speed of maintenance Hydraulic Pump good lubrication effect need to be more than 600r/min.Hydraulic Pump lubricant effect is bad not only causes the work efficiency of controllable capacity pump low, the wearing and tearing of aggravation controllable capacity pump, the service life of greatly reducing system, and even may not work, and this will affect the use of heavy-duty vehicle greatly.
In addition, also there is following shortcoming from change speed gear box power taking in Hydraulic Pump: 1) when car brakeing, lock torque can instead drag change speed gear box, drive Hydraulic Pump to continue pump oil simultaneously, give front wheel torque output, thereby increased the lock torque of front-wheel, affect the distribution of the lock torque of conventional truck; 2) when there is gear wear or damaging in change speed gear box, can affect the displacement control of Hydraulic Pump, also affect the transmission efficiency of fluid power system, increased mechanical drive loss.
Therefore, a kind ofly can increase the propulsive effort of heavy-duty vehicle when bad road traveling, can strengthen again the service life of controllable capacity pump to strengthen the serviceability of heavy-duty vehicle, the fluid power system that simultaneously improves car load driving efficiency has good development prospect.
Utility model content
The purpose of this utility model is to keep, on the advantage of former hub hydraulic motor driving system, overcoming its existing problem in the use, extending the service life of system, guaranteeing traffic safety, improving car load driving efficiency simultaneously.
The technical solution adopted in the utility model is as follows:
A follow-on hub hydraulic motor driving system, comprises driving engine, power takeoff, fluid control valve group, Hydraulic Pump, HM Hydraulic Motor and controller, and wherein, described fluid control valve group is connected with described Hydraulic Pump; One end of described power takeoff is connected with the mouth of the driving annex of described driving engine, and the other end is connected with the Hydraulic Pump being arranged on vehicle frame;
Described Hydraulic Pump, by fluid control valve group, forms hydraulic closed working connection with 2 HM Hydraulic Motor that are arranged in front-wheel hub.
Described control cock group comprises electromagnetic valve and 2 by pass valves.
Described electromagnetic valve is three-position four-way valve, and the P mouth of wherein said three-position four-way valve is connected by pressure piping with the outlet of the high pressure oil of described Hydraulic Pump; The T mouth of described three-position four-way valve is connected by low pressure pipeline with the low pressure oil import of described Hydraulic Pump; The A mouth of described three-position four-way valve and B mouth be being connected by pressure piping into and out of hydraulic fluid port through by pass valve and HM Hydraulic Motor respectively.
Described controller is connected by electric signal with described Hydraulic Pump, described driving engine, described electromagnetic valve respectively.
Described Hydraulic Pump is the inner axial plunger type high voltage controllable capacity pump with slippage pump, and its operation pressure is 0-40MPa.
Described HM Hydraulic Motor is two radial plunger type fixed displacement motors that structure is identical, and its rotor shaft adopts mechanical bolt to be connected with the wheel hub of front-wheel.
Follow-on hub hydraulic motor driving system of the present utility model, Hydraulic Pump is from the additional output shaft end power taking of engine drive, by pump-motor hydraulic circuit by transmission of power to front-wheel; By controlling the diverse location of hydraulic valve, can realize HM Hydraulic Motor forward, quit work and reverse function, can realize vehicle in the low function that increases propulsive effort while adhering to road traveling, there is multi-state comformability.Simultaneously, power takeoff adopts spline pair to be connected with the driving annex output shaft of driving engine, transmitting ratio is 1, the rotating speed of Hydraulic Pump equates with the rotating speed of driving engine, and the vapour J6 heavy-duty commercial vehicle of take is example, the range of speed Nb=700-1900r/min of Hydraulic Pump, within like this adjustment of rotational speed of Hydraulic Pump being arrived to rational scope, actv. has changed its lubrication circumstances in the course of the work, has extended system service life, has guaranteed traffic safety.
In addition, the power that driving engine passes to Hydraulic Pump does not pass through the transmission of change speed gear box, has improved machinery driving efficiency, has reduced mechanical horsepower loss; Hydraulic Pump is from the driving annex output shaft power taking of driving engine, avoided the impact on hydraulic pump works such as the gearshift of change speed gear box and wearing and tearing.Under extreme case, when change speed gear box or transmission shaft occur damaging can not use time, Hydraulic Pump can work on, and vehicle is travelled slowly with f-w-d form.
Accompanying drawing explanation
Fig. 1 is the structural representation of follow-on hub hydraulic motor driving system of the present utility model;
Fig. 2 is follow-on hub hydraulic motor driving system of the present utility model energy transfer route schematic diagram when the independent drive pattern of driving engine;
Fig. 3 is follow-on hub hydraulic motor driving system of the present utility model energy transfer route schematic diagram when associating drive pattern;
Fig. 4 is for adopting the overall control FB(flow block) of follow-on hub hydraulic motor driving system of the present utility model;
Fig. 5 is for adopting the energy transfer route schematic diagram of follow-on hub hydraulic motor driving system of the present utility model under extreme case;
Fig. 6 is the diagram of curves that adopts the vehicle tractive force raising of follow-on hub hydraulic motor driving system of the present utility model;
Fig. 7 is the diagram of curves that adopts the vehicle climbable gradient power raising of follow-on hub hydraulic motor driving system of the present utility model.
(description of reference numerals)
1 driving engine, 2 controllers, 3 power-transfer clutchs, 4 change speed gear boxs, 5 transmission shafts, 6 rear driving axles, 7 semiaxis, 8 trailing wheels, 9 power takeoffs, the driving annex of 10 driving engines, 11 Hydraulic Pumps, 12 fluid control valve groups, 13 HM Hydraulic Motor, 14 front-wheels, 15 electromagnetic valves, 16 by pass valves
The specific embodiment
Below in conjunction with accompanying drawing, the specific embodiment of the present utility model is elaborated.
With reference to figure 1, follow-on hub hydraulic motor driving system of the present embodiment, comprises driving engine 1, controller 2, power-transfer clutch 3, change speed gear box 4, transmission shaft 5, rear driving axle 6, semiaxis 7, trailing wheel 8, power takeoff 9, the driving annex 10 of driving engine, Hydraulic Pump 11, fluid control valve group 12, HM Hydraulic Motor 13, front-wheel 14, electromagnetic valve 15, by pass valve 16.In figure, heavy line represents mechanical connection, and thick dashed line represents that pressure piping connects, and fine dotted line represents that low pressure pipeline connects.
With reference to figure 1, power takeoff 9 one end adopt spline pair to be connected with the output shaft of the driving annex 10 of driving engine, and one end adopts spline pair to be connected with the rotor shaft of Hydraulic Pump 11; Hydraulic Pump 11, by fluid control valve group 12, forms Hydraulic Main oil circuit with 2 HM Hydraulic Motor 13.
In system described in the utility model, fluid control valve group 12 comprises electromagnetic valve 15 and 2 by pass valves 16, preferably electromagnetic valve 15 can adopt and can keep the motionless three position four-way electromagnetic valve that commutates for a long time, 4 hole: P of three-position four-way valve represent pressure oil oil inlet, T represents the oil suction of logical fuel tank or oil pump, and A, B represent the actuator port of the actuating units such as logical oil cylinder or oil motor.Three-position four-way valve has three control positioies, and spool is pushed left side to, and P and B are logical, and T and A are logical; Spool is pushed right side to, and P and A are logical, and T and B are logical.Spool is placed in midway location, different Median Functions, and the connection situation of each hydraulic fluid port is different, and for " O " type three-position four-way valve, each hydraulic fluid port A, B, P, T are not connected.
The P mouth of the electromagnetic valve 15 in system described in the utility model adopts pressure piping to be connected with the outlet of the high pressure oil of Hydraulic Pump 11, the low pressure oil outlet of T mouth and Hydraulic Pump 11 adopts low pressure pipeline to be connected, and A and B mouth be being connected into and out of hydraulic fluid port employing pressure piping by by pass valve 16 and HM Hydraulic Motor 14 respectively.
In the utility model, Hydraulic Pump 11 can adopt Volumetric efficiency high, smooth running, and discharge uniformity is good, and noise is low, the shaft orientation plunger variable pump that operation pressure is high, HM Hydraulic Motor 13 adopts radial plunger fixed displacement motor.
In the utility model, driving engine 1 is as car load power unit, its power can directly be passed to trailing wheel 8 by machine driven system (comprising power-transfer clutch 3, change speed gear box 4, transmission shaft 5, rear driving axle 6 and semiaxis 7), also can pass to Hydraulic Pump 11 by power takeoff 9, Hydraulic Pump 11 pumps high pressure oil and drives HM Hydraulic Motor 13 work, by transmission of power to front-wheel 14.
System described in the utility model in normal vehicle operation situation, mode of operation can be the independent drive pattern of driving engine and associating drive pattern.Two kinds of mode of operations are as shown in the table:
● represent that power-transfer clutch engages, motor operations
Zero represents disengaging of clutch, motor idle running
Particularly, two kinds of mode of operations are described below:
(1) the independent drive pattern of driving engine: refer to that automobile travels on normal road surface, now drive wheel is non-slip, the required torque of automotive operation is provided separately by driving engine 1, the state of HM Hydraulic Motor 13 in idle running, power reaches trailing wheel 8 by driving engine 1 through power-transfer clutch 3, change speed gear box 4, transmission shaft 5, rear driving axle 6 and semiaxis 7.
Fig. 2 is follow-on hub hydraulic motor driving system of the present utility model energy transfer route schematic diagram when the independent drive pattern of driving engine.In figure, heavy line represents mechanical connection, and thick dashed line represents that pressure piping connects, and fine dotted line represents that low pressure pipeline connects.As shown in Figure 2, when driving engine 1 independent drive pattern, power-transfer clutch 3 engages, and the power output of driving engine, through the output shaft of change speed gear box 4, is delivered to rear driving axle 6 from transmission shaft 5, through semiaxis 7, pass to trailing wheel 8 and drive automobile, now electromagnetic valve 15 spools are positioned at meta, and four-hole all seals, HM Hydraulic Motor 13 is in idling conditions, and hydraulic efficiency pressure system does not obtain energy.Power transmission line is as shown in the arrow in Fig. 2.
(2) associating drive pattern: when running car during on bad road surface drive wheel skid, start hub hydraulic motor driving system, wheel hub HM Hydraulic Motor 13 enters mode of operation, Hydraulic Pump 11 obtains a part of power of driving engine 1 by power takeoff 9, the HM Hydraulic Motor 13 that is arranged on front-wheel 14 wheel hubs for giving provides high pressure oil, and HM Hydraulic Motor 13 drives front-wheel; Other a part of power of driving engine 1 reaches trailing wheel 8 by power-transfer clutch 3, change speed gear box 4, transmission shaft 5, rear driving axle 6 and semiaxis 7, thereby become front and back wheel, jointly drives vehicle.Controller 2 is controlled the discharge capacity of Hydraulic Pump 11 to offer the propulsive effort that wheel hub HM Hydraulic Motor 13 is suitable according to the travel conditions of vehicle.
Fig. 3 is follow-on hub hydraulic motor driving system of the present utility model energy transfer route schematic diagram when associating drive pattern.In figure, heavy line represents mechanical connection, and thick dashed line represents that pressure piping connects, and fine dotted line represents that low pressure pipeline connects.As shown in Figure 3, when associating drive pattern, power-transfer clutch 3 engages, electromagnetic valve 15 spools are positioned at right side (being positioned at left side when vehicle backing travels), connect P-A and T-B passage, driving engine 1, the common vehicle that drives of HM Hydraulic Motor 13, car load becomes 4 wheel drive by 2 wheel drive.The output of the power of driving engine 1 reaches trailing wheel 8 by power-transfer clutch 3, change speed gear box 4, transmission shaft 5, rear driving axle 6 and semiaxis 7 successively on the one hand, and the output of the power of driving engine 1 is arrived front-wheel 14 by power takeoff 9, Hydraulic Pump 11, fluid control valve group 12, HM Hydraulic Motor 13 successively on the other hand.Transfer route is as shown in the arrow in Fig. 3.
When carry out associating drive pattern recited above, when 2 front-wheels 15 enter hydraulic-driven pattern, and this need to judge according to conditions such as road surface, the speed of a motor vehicle, judges flow process as shown in Figure 4.
Fig. 4 is for adopting the overall control FB(flow block) of follow-on hub hydraulic motor driving system of the present utility model.With reference to figure 4, the switch key from the gauge panel of operator's compartment starts;
When opening switch, if parking return, if not, see the fine or not situation on road surface and be divided into Hao Luhehuai road;
Two kinds of road surface situation control flows are consistent, such as: while being a good road surface, first according to the rotary speed direction after the rotating speed of driving engine and change speed gear box, judging and advance or fall back, if direction unanimously advance, otherwise, fall back.
When car advances or fall back, control flow class, such as: when advancing, if occur, emergency braking does not enter hydraulic-driven pattern, and it is 0 that free air capacity is controlled.
Finally judge in the vehicle speed range whether current vehicle speed can use in system and (because hydraulic efficiency pressure system is used when high speed, be easy to generate heat), when the speed of a motor vehicle satisfies condition, illustrate that hydraulic efficiency pressure system can be used.When foregoing condition all reaches satisfied, controller regulates the aperture of pump in real time according to car load real time running state, makes front wheel rotation speed follow rear wheel rotation speed.Until the speed of a motor vehicle surpasses threshold values or chaufeur is closed liquid drive system.
Consider heavy-duty vehicle operating condition more complicated, machine driven system serious wear.Under extreme case, when the change speed gear box of vehicle or transmission shaft occur damaging and can not work time, with reference to figure 5, system described in the utility model can work on, and makes vehicle continue to travel slowly with the form of f-w-d.
Under this extreme case, change speed gear box or transmission shaft are unavailable, and now cut-off clutch, disconnects driving engine and machine driven system.The power of driving engine 1 passes to Hydraulic Pump 11 through power takeoff 9, and high pressure oil is pumped in Hydraulic Pump 11 work, and HM Hydraulic Motor 13 work through working connection drive installation on front-wheel 14, drive front-wheel 14.Now vehicle is that front-wheel drives separately, and power transfer path as shown in Figure 5.
Fig. 6 is the diagram of curves that adopts the vehicle tractive force raising of follow-on hub hydraulic motor driving system of the present utility model.As shown in Figure 6, when vehicle is when fully loaded 100 tons, one grade speed ratio is 12.1, calculating it increases the ratio that can improve tractive force after hydraulic-driven pattern.Wherein, abscissa is adhesion value, ordinate is that tractive force increases ratio (%), Ftf is the propulsive effort (t) that front-wheel 15 can improve, FtR is the propulsive effort (t) that driving engine 1 is passed to trailing wheel 6, Ftf+FtR is total propulsive effort of vehicle, and it is that Ftf obtains with respect to FtR that tractive force increases proportional curve.
Fig. 7 is the diagram of curves that adopts the vehicle climbable gradient power raising of follow-on hub hydraulic motor driving system of the present utility model.When vehicle is when fully loaded 100 tons, one grade speed ratio is 12.1, calculating it increases the ratio that can improve climbable gradient after hydraulic-driven pattern.Wherein, abscissa is adhesion value, ordinate is that tractive force increases ratio (%), Ftf is the propulsive effort (t) that front-wheel 15 can improve, FtR is the propulsive effort (t) that driving engine 1 is passed to trailing wheel 6, GradR is the climbable gradient (%) of vehicle under the propulsive effort of FtR, and GradFR is the climbable gradient (%) of vehicle under FtR and the common propulsive effort of Ftf, and it is that GradR is with respect to the ratio of the climbable gradient of GradFR increase that climbable gradient increases proportional curve.
Utilize the curve shown in Fig. 6 and 7, after adopting follow-on hydraulic booster system of the present utility model, compare with conventional truck, multi-state is adaptable, can significantly improve dynamic property, crossing ability and the hill climbing ability of vehicle, on the road surface between coefficient of road adhesion 0.34-0.57, improve tractive force ratio and be about 10%～23%, climbable gradient raising ratio is about 13%～25%.
To sum up, when follow-on hub hydraulic motor driving system described in the utility model travels on bad road surface of vehicle, improve on the basis of its propulsive effort, actv. has changed its lubrication circumstances in the course of the work, extend system service life, guaranteed traffic safety.Meanwhile, improve machinery driving efficiency, reduced mechanical horsepower loss; Avoided the impact on hydraulic pump works such as the gearshift of change speed gear box and wearing and tearing.Under extreme case, when change speed gear box or transmission shaft occur damaging can not use time, Hydraulic Pump can work on, and vehicle is travelled slowly with f-w-d form.
Claims (6)
1. a follow-on hub hydraulic motor driving system, it is characterized in that, comprise driving engine, power takeoff, fluid control valve group, Hydraulic Pump, HM Hydraulic Motor and the controller that entire system is controlled, wherein, described fluid control valve group is connected with described Hydraulic Pump;
One end of described power takeoff is connected with the mouth of the driving annex of described driving engine, and the other end is connected with the Hydraulic Pump being arranged on vehicle frame;
Described Hydraulic Pump, by fluid control valve group, forms hydraulic closed working connection with 2 HM Hydraulic Motor that are arranged in front-wheel hub.
2. follow-on hub hydraulic motor driving system according to claim 1, is characterized in that, described control cock group comprises electromagnetic valve and 2 by pass valves.
3. follow-on hub hydraulic motor driving system according to claim 2, is characterized in that, described electromagnetic valve is three-position four-way valve, and the P mouth of wherein said three-position four-way valve is connected by pressure piping with the outlet of the high pressure oil of described Hydraulic Pump; The T mouth of described three-position four-way valve is connected by low pressure pipeline with the low pressure oil import of described Hydraulic Pump; The A mouth of described three-position four-way valve and B mouth be being connected by pressure piping into and out of hydraulic fluid port through by pass valve and HM Hydraulic Motor respectively.
4. follow-on hub hydraulic motor driving system according to claim 3, is characterized in that, described controller is connected by electric signal with described Hydraulic Pump, described driving engine, described electromagnetic valve respectively.
5. according to the follow-on hub hydraulic motor driving system described in claim 1 to 4 any one, it is characterized in that, described Hydraulic Pump is the inner axial plunger type high voltage controllable capacity pump with slippage pump, and its operation pressure is 0-40MPa.
6. according to the follow-on hub hydraulic motor driving system described in claim 1 to 4 any one, it is characterized in that, described HM Hydraulic Motor is two radial plunger type fixed displacement motors that structure is identical, and its rotor shaft adopts mechanical bolt to be connected with the wheel hub of front-wheel.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320733953.XU CN203528295U (en) | 2013-11-19 | 2013-11-19 | Improved hub motor hydraulic drive system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320733953.XU CN203528295U (en) | 2013-11-19 | 2013-11-19 | Improved hub motor hydraulic drive system |
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| CN203528295U true CN203528295U (en) | 2014-04-09 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105150770A (en) * | 2015-09-25 | 2015-12-16 | 武汉神骏专用汽车制造股份有限公司 | Combined hydraulic suspension trailer having auxiliary driving function |
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2013
- 2013-11-19 CN CN201320733953.XU patent/CN203528295U/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105150770A (en) * | 2015-09-25 | 2015-12-16 | 武汉神骏专用汽车制造股份有限公司 | Combined hydraulic suspension trailer having auxiliary driving function |
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Granted publication date: 20140409 |