CN111483284B - Hydraulic suspension system, lifting control method and multi-axis flat car - Google Patents
Hydraulic suspension system, lifting control method and multi-axis flat car Download PDFInfo
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- CN111483284B CN111483284B CN202010484725.8A CN202010484725A CN111483284B CN 111483284 B CN111483284 B CN 111483284B CN 202010484725 A CN202010484725 A CN 202010484725A CN 111483284 B CN111483284 B CN 111483284B
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- 239000000725 suspension Substances 0.000 title claims abstract description 131
- 238000000034 method Methods 0.000 title claims abstract description 29
- 239000003921 oil Substances 0.000 claims description 295
- 238000013016 damping Methods 0.000 claims description 24
- 238000006073 displacement reaction Methods 0.000 claims description 18
- 239000010720 hydraulic oil Substances 0.000 claims description 10
- 230000008929 regeneration Effects 0.000 claims description 8
- 238000011069 regeneration method Methods 0.000 claims description 8
- 230000009471 action Effects 0.000 claims description 6
- 230000005484 gravity Effects 0.000 claims description 5
- 230000001105 regulatory effect Effects 0.000 claims description 4
- 230000008859 change Effects 0.000 claims description 3
- 230000007246 mechanism Effects 0.000 claims description 3
- 230000001174 ascending effect Effects 0.000 claims description 2
- 230000008569 process Effects 0.000 abstract description 16
- 230000005540 biological transmission Effects 0.000 abstract description 2
- 239000007788 liquid Substances 0.000 description 6
- 244000261422 Lysimachia clethroides Species 0.000 description 3
- 239000013589 supplement Substances 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000003208 petroleum Substances 0.000 description 2
- 238000005381 potential energy Methods 0.000 description 2
- 239000002699 waste material Substances 0.000 description 2
- 229910000851 Alloy steel Inorganic materials 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000001172 regenerating effect Effects 0.000 description 1
- 230000035945 sensitivity Effects 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 230000001502 supplementing effect Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
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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
- 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
- B60G17/015—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 the regulating means comprising electric or electronic elements
- B60G17/0152—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 the regulating means comprising electric or electronic elements characterised by the action on a particular type of suspension unit
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D63/00—Motor vehicles or trailers not otherwise provided for
- B62D63/06—Trailers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D63/00—Motor vehicles or trailers not otherwise provided for
- B62D63/06—Trailers
- B62D63/08—Component parts or accessories
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
-
- 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
-
- 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
- B60G2500/302—Height or ground clearance using distributor valves
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Analytical Chemistry (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
The invention belongs to the technical field of hydraulic transmission and control, and particularly relates to a hydraulic suspension system, a lifting control method and a multi-axis flat car, wherein the hydraulic suspension system comprises an oil tank, a load sensitive variable pump, at least one suspension hydraulic cylinder, a load port independent control valve group with the number corresponding to that of the suspension hydraulic cylinders, a first two-position three-way electromagnetic reversing valve, a second two-position three-way electromagnetic reversing valve and a constant delivery pump; the load port independent control valve group comprises a control valve block, a first two-position two-normally-open electro-hydraulic proportional valve, a second two-position two-normally-open electro-hydraulic proportional valve, a three-position four-way electro-hydraulic reversing valve, a shuttle valve and a two-position two-normally-closed electro-hydraulic proportional valve. The invention adopts the load sensitive variable pump to supply oil in the process of 'integral lifting', and adopts the constant delivery pump to supply oil in the process of 'integral falling', thereby reducing the use frequency of the load sensitive variable pump, and the output power of the constant delivery pump is lower in the process of 'integral falling', so that the system has certain energy-saving characteristic.
Description
Technical Field
The invention belongs to the technical field of hydraulic transmission and control, and particularly relates to a hydraulic suspension system, a lifting control method and a multi-axis flat car.
Background
The multi-axis flat car is mainly applied to transportation of heavy, large, high and special-shaped structures, has the advantages of flexible use, convenient loading and unloading, load capacity of more than 50000 tons under the condition of multi-car mechanical assembly or free combination, and wide application in engineering fields such as equipment manufacturing industry, petroleum, chemical industry, offshore petroleum, bridge construction and the like. The multi-axis flat car mainly comprises a frame wheel axle, a suspension system, a steering system, a hydraulic system, a braking system, a power system, a control system and other equipment. The frame adopts a welding structure of a high-strength alloy steel box section and comprises a main beam, an auxiliary beam, a cross beam, an inclined support and an end beam. The wheel axle is arranged at the bottom of the frame, the wheel axles which can independently steer are longitudinally arranged along the two sides of the frame, and each wheel axle is provided with 2 tires. A typical flatbed has 2-10 axes per column, 2 suspension systems per axis, 2 axles, 4 tires.
The suspension system of the multi-axis flat car is supported on the auxiliary beam, plays a role in supporting and connecting the wheel axle, and comprises a rotary support, a suspension pivot, a suspension large arm, a suspension small arm, a swinging shaft, a suspension hydraulic cylinder, wheels and the like, and the suspension hydraulic cylinder of the multi-axis flat car simultaneously extends and retracts, so that the integral lifting function of the flat car body can be realized. The suspension hydraulic cylinder is driven, a combination mode of the load-sensitive variable pump and the load-sensitive multi-way valve is generally adopted, the displacement of the load-sensitive variable pump and the number of the load-sensitive multi-way valves are correspondingly increased according to the number of the suspension hydraulic cylinders, and if the axes of the flat car are too many, the power of the engine is required to be increased, so that the power requirement of a suspension system is met.
The load port independent control technology is a novel hydraulic system which utilizes a plurality of control valves to respectively control an inlet oil way and an outlet oil way of a hydraulic actuator, and corresponding control logic can be designed according to the number and the functions of the control valves, so that the functions of flow regeneration, independent control of inlet and outlet, pressure control and the like can be realized, and the performance of the traditional hydraulic system is improved. In the process of 'integral landing', the oil supply requirement of the multi-axis flat car is very small due to the action of gravity, and in order to control the landing speed, the traditional load sensitive system still needs to supply oil to the suspension system, and the more the axes are, the greater the engine power is, so that energy waste is caused.
Disclosure of Invention
The invention aims to overcome the defects of high engine power and energy waste in the prior art, and provides a hydraulic suspension system, a lifting control method and a multi-axis flat car which not only can realize speed control in the whole lifting process of the flat car, but also have a flow regeneration function, effectively reduce throttling loss and realize energy saving of the system.
The technical scheme adopted for solving the technical problems is as follows:
The invention discloses a hydraulic suspension system, which is characterized in that: the device comprises an oil tank, a load sensitive variable pump, at least one suspension hydraulic cylinder, a load port independent control valve group, a first two-position three-way electromagnetic directional valve, a second two-position three-way electromagnetic directional valve and a constant delivery pump, wherein the number of the load port independent control valve group corresponds to that of the suspension hydraulic cylinder; the load port independent control valve group comprises a control valve block, a first two-position two-normally-open electro-hydraulic proportional valve, a second two-position two-normally-open electro-hydraulic proportional valve, a three-position four-way electro-hydraulic reversing valve, a shuttle valve and a two-position two-normally-closed electro-hydraulic proportional valve; the control valve block is respectively provided with a first oil inlet P 1, a second oil inlet P 2, a first oil return port T 1, a second oil return port T 2, a first load sensitive port LS 1, a second load sensitive port LS 2, a first working oil port A 11 and a second working oil port B 4; an oil outlet A 3 of the load-sensitive variable pump is connected with an oil inlet P 3 hydraulic pipeline of the first two-position three-way electromagnetic directional valve, a second working oil port B 1 of the first two-position three-way electromagnetic directional valve is connected with an oil outlet A 4 hydraulic pipeline of the constant delivery pump, and a first working oil port A 6 of the first two-position three-way electromagnetic directional valve is connected with the first oil inlet P 1 and the second oil inlet P 2 hydraulic pipeline; the first oil inlet P 1 and the second oil inlet P 2 are communicated with an oil inlet P 5 of the three-position four-way electro-hydraulic reversing valve through an internal flow passage of the control valve block; the first working oil port A 7 of the three-position four-way electro-hydraulic reversing valve is communicated with the oil inlet P 6 of the first two-position two-way normally-open electro-hydraulic proportional valve through an internal flow passage of a control valve block; an oil outlet A 8 of the first two-position two-way normally-open electro-hydraulic proportional valve, a first comparison oil port A 15 of the shuttle valve and an oil inlet P 8 of the two-position two-way normally-closed electro-hydraulic proportional valve are communicated to the first working oil port A 11 through an internal flow passage of the control valve block; the first working oil port A 11 is communicated with the rodless cavity of the suspension hydraulic cylinder through a hydraulic pipeline, and the rod cavity of the suspension hydraulic cylinder is communicated with the second working oil port B 4 through a hydraulic pipeline; an oil outlet A 10 of the two-position normally-closed electro-hydraulic proportional valve and an oil outlet A 9 of the second two-position normally-open electro-hydraulic proportional valve are communicated to the second working oil port B 4 through an internal channel of the control valve block, and an oil inlet P 7 of the second two-position normally-open electro-hydraulic proportional valve is communicated with the second working oil port B3 of the three-position four-way electro-hydraulic reversing valve through an internal channel; the load sensitive port X of the load sensitive variable pump is connected with a first working oil port A 5 of the second two-position three-way electromagnetic directional valve through a hydraulic pipeline, and an oil return port T 3 of the three-position four-way electro-hydraulic directional valve is communicated with the first oil return port T 1 and the second oil return port T 2 through an internal flow passage; the load sensing port X of the load sensing variable pump is communicated to the first load sensing port LS 1 through a hydraulic pipeline; the first load sensing port LS 1 is communicated to the output port C 1 of the shuttle valve through an internal flow passage; a second comparison oil port B 6 of the shuttle valve is communicated to the second load sensitive port LS 2 through an internal flow passage; an oil suction port S 2 of the constant delivery pump is connected to an oil tank through a hydraulic pipeline.
Further, the second two-position three-way electromagnetic directional valve is connected to a hydraulic pipeline between the load sensitive port X and the second two-position three-way electromagnetic directional valve, and the load sensitive port X is communicated with a first working oil port A 5 of the second two-position three-way electromagnetic directional valve through the hydraulic pipeline; an oil inlet P 4 of the second two-position three-way electromagnetic directional valve is communicated with the first load sensitive port LS 1 through a hydraulic pipeline; and an oil outlet B 2 of the second two-position three-way electromagnetic directional valve is connected to the oil tank through a hydraulic pipeline.
Further, the load-sensitive variable pump includes: the system comprises a sensitive variable valve block, a first two-position three-way hydraulic reversing valve, a second two-position three-way hydraulic reversing valve, a power valve, a variable pump, a plunger cylinder, a first damping hole, a second damping hole and a third damping hole; an oil suction port S 1, an oil outlet A 3, an oil discharge port L 1 and a load sensitive port X are arranged on the sensitive variable valve block, the variable pump is fixedly arranged on the sensitive variable valve block, and an oil inlet P 11 of the variable pump is communicated with the oil suction port S 1 through an internal flow channel; an oil outlet A 16 of the variable pump, an oil outlet A 3 on the sensitive variable valve block, a first working oil port A 18 of the first two-position three-way hydraulic reversing valve, a first pilot oil port C 2, and a first working oil port A 19 and a first pilot oil port C 24 of the second two-position three-way hydraulic reversing valve are communicated through an internal flow channel on the sensitive variable valve block; an oil inlet P 12 of the power valve, an oil outlet A 23 of the third damping hole and a second pilot oil port C 5 of the second two-position three-way hydraulic reversing valve are communicated to the load sensitive port X through an internal flow passage of the sensitive variable valve block; the oil discharge port L 2 of the variable pump, the oil outlet A 17 of the power valve, the second working oil port B 8 of the second two-position three-way hydraulic reversing valve and the second pilot oil port C3 of the first two-position three-way hydraulic reversing valve are communicated to the oil discharge port L 1 through an internal flow passage of the sensitive variable block; an oil inlet P 15 of the first damping hole, an oil inlet P 14 of the second two-position three-way hydraulic electromagnetic valve, a second working oil port B 7 of the first two-position three-way hydraulic reversing valve and an oil outlet A 20 of the second damping hole are communicated through an internal flow passage of the sensitive variable valve block; an oil inlet P 16 of the second damping hole, an oil inlet P 13 of the first two-position three-way hydraulic reversing valve and an oil inlet A 21 of the plunger cylinder are communicated through an internal flow passage of the sensitive variable valve block; the piston rod of the plunger cylinder, the variable mechanism pushing rod of the variable pump and the spring regulator of the power valve are connected through a mechanical structure, so that the displacement of the piston rod is changed in proportional relation with the displacement of the variable pump and the spring force of the power valve.
Further, the engine is further provided with an output shaft connected with the input shaft of the load-sensitive variable pump through a coupler; the input shaft of the constant displacement pump is connected with the tail end shaft hole of the load sensitive variable displacement pump.
Further, an oil outlet A 3 of the load-sensitive variable pump and an oil inlet P 3 of the first two-position three-way electromagnetic directional valve are both connected with an oil inlet P 9 of a first overflow valve through hydraulic pipelines, and an oil outlet A 13 of the first overflow valve is connected to an oil tank through a hydraulic pipeline.
Further, the second working oil port B 1 of the first two-position three-way electromagnetic directional valve and the oil outlet A 4 of the constant delivery pump are both connected to the oil inlet P 10 of the second overflow valve through a hydraulic pipeline, and the oil outlet A 14 of the second overflow valve is connected to the oil tank through a hydraulic pipeline.
Further, the number of the suspension hydraulic cylinders is four.
Further, two hydraulic suspension systems are arranged on each axis of the arranged flat car.
The invention also discloses a lifting control method of the hydraulic suspension system, which is characterized in that:
The ascending control method comprises the following steps: the electromagnets of the first two-position three-way electromagnetic reversing valve and the second two-position three-way electromagnetic reversing valve are powered off simultaneously, oil is supplied to a suspension system by a load-sensitive variable pump, the left electromagnet of the three-position four-way electro-hydraulic reversing valve is powered on simultaneously, the electromagnets of the two-position two-way normally-closed electro-hydraulic proportional valve are powered off simultaneously, a current signal is input to the first two-position two-way normally-open electro-hydraulic proportional valve to throttle and regulate the speed of an inlet, and meanwhile, the input current signal of the second two-position two-way normally-open electro-hydraulic proportional valve is set to be the maximum value, so that the full opening of a valve port of the second two-position two-way normally-open electro-hydraulic proportional valve is ensured; hydraulic oil enters from an oil inlet P 1 or P 2, enters a rodless cavity of a suspension hydraulic cylinder after being throttled and regulated by a first two-position two-way normal-open electro-hydraulic reversing valve, pushes a piston rod of the suspension hydraulic cylinder to extend so as to push a flat car body to lift upwards, and meanwhile, flows out from rod cavities of four suspension hydraulic cylinders and flows back to an oil tank through a fully-opened second two-position two-way normal-open electro-hydraulic reversing valve, the left position of the three-position four-way electro-hydraulic reversing valve, a first oil return port T 1 or a second oil return port T 2; the pressure between the rod cavity and the rodless cavity of the suspension hydraulic cylinder is fed back to the load sensitive variable pump through the second two-position three-way electromagnetic reversing valve, so that the load sensitive variable pump adjusts the oil supply speed and the oil supply quantity according to the load change condition;
The descent control method comprises the following steps: the electromagnets of the first two-position three-way electromagnetic directional valve and the second two-position three-way electromagnetic directional valve are simultaneously electrified, a constant displacement pump supplies oil to a suspension system, a load sensitive port X of a load sensitive variable pump is communicated with an oil tank through the second two-position three-way electromagnetic directional valve, the load sensitive variable pump works at minimum pressure, the load sensitive variable pump is in an energy-saving mode, under the gravity action of a flat car body, a rodless cavity of a suspension hydraulic cylinder generates high pressure, the right electromagnet of the three-position four-way electro-hydraulic directional valve is simultaneously electrified, the first two-position two-way normally-open electro-hydraulic proportional valve regulates speed according to an input current signal, so that the effect of outlet throttling speed regulation is achieved, meanwhile, the input current signal of the second two-position two-way normally-open electro-hydraulic proportional valve is set to be maximum, the electromagnets of the two-position two-normally-closed electro-hydraulic proportional valve are simultaneously input with maximum current value, and a flow regeneration mode is started; the hydraulic oil is subjected to right position of a three-position four-way electro-hydraulic reversing valve, oil is replenished to a rod cavity of a suspension hydraulic cylinder after passing through a second two-position two-way normally-open electro-hydraulic proportional valve, meanwhile, after an electromagnet of a first two-position two-way normally-open electro-hydraulic proportional valve receives a proportional current signal, the hydraulic oil flows out of a rodless cavity of the suspension hydraulic cylinder, and then flows back to an oil tank after being subjected to throttling and speed regulation of the first two-position two-way normally-open electro-hydraulic reversing valve, and then flows back to the oil tank through the right position of the three-position four-way electro-hydraulic reversing valve and a first oil return port T 1 or a second oil return port T 2; and one part of high-pressure oil generated by the rodless cavity flows back to the oil tank through the throttling speed regulation effect of the first two-position two-way normally-open electro-hydraulic proportional valve, and the other part flows into the rod cavity of the suspension hydraulic cylinder through the two-position two-way normally-closed electro-hydraulic proportional valve, and when the flow of the rod cavity of the suspension hydraulic cylinder is insufficient, the constant delivery pump supplements the oil to the rod cavity of the suspension hydraulic cylinder, so that the outlet throttling speed regulation and the inlet flow regeneration are realized.
The invention also discloses a multi-axis flat car, which is characterized in that: comprises a plurality of axes, wherein each axis is provided with two suspension hydraulic cylinders; each suspension hydraulic cylinder is independently controlled through a load port independent control valve group connected with a load sensitive variable pump.
The hydraulic suspension system, the lifting control method and the multi-axis flat car have the beneficial effects that:
1. The invention adopts the load sensitive variable pump, the quantitative pump and the two-position three-way electromagnetic reversing valve to construct a double-pump switching oil supply system, which can switch in real time according to the integral lifting action of the flat car, adopts the load sensitive variable pump to supply oil in the integral lifting process, and adopts the quantitative pump to supply oil in the integral falling process, thereby reducing the use frequency of the load sensitive variable pump, prolonging the service life of the load sensitive variable pump, and having lower output power of the quantitative pump in the integral falling process, so that the system has certain energy-saving characteristic.
2. According to the invention, a two-position two-normally-open electro-hydraulic proportional valve, a two-position two-normally-closed electro-hydraulic proportional valve, a three-position four-way electro-hydraulic reversing valve and a shuttle valve are adopted to form an independent control valve group of a load port, in the whole lifting process of the flat car, the throttle and speed regulation control of an inlet in the whole lifting process and the full-open control of an outlet can be realized by changing the control logic and input current of the control valve, so that the throttle loss is effectively reduced, the output power of a load sensitive variable pump is reduced, and the output power of an engine in the whole lifting process of the flat car is reduced; meanwhile, the functions of controlling the speed regulation of the outlet throttle and regenerating the inlet flow in the process of 'integral landing' can be realized, so that the gravitational potential energy of the flat car is effectively utilized, the work made by the gravitational potential energy is converted into the kinetic energy of 'integral landing' of the flat car, the oil supply of a load-sensitive variable pump is not needed, and only the oil supplementing is needed by a quantitative pump, thereby effectively reducing the output power of an engine in the process of 'integral landing' of the flat car and realizing the energy saving of a system.
3. According to the invention, a combined form of the load sensitive variable pump, the quantitative pump and the independent control valve group of the load port is adopted, when the axis is increased and the number of the suspension systems is increased, the displacement of the load sensitive variable pump is not required to be increased, and only the number of the independent control valve group of the load port is required to be correspondingly increased according to the number of the suspension hydraulic cylinders, so that the power of the engine is only required to be correspondingly increased according to the requirements of other systems, the influence of the suspension systems is avoided, and the system has higher universality and higher energy-saving characteristic compared with the traditional hydraulic systems.
Drawings
The invention will be described in further detail with reference to the drawings and the detailed description.
FIG. 1 is a schematic illustration of an eight-axis flatbed in accordance with an embodiment of the present invention;
FIG. 2 is a schematic view of a suspension of a flatbed in accordance with an embodiment of the present invention;
FIG. 3 is a diagram of a hydraulic suspension system with only one suspension according to an embodiment of the invention
FIG. 4 is a hydraulic schematic of a suspension system for a two-axis flatbed;
FIG. 5 is a hydraulic schematic diagram of a load port independent control valve block;
FIG. 6 is a hydraulic schematic of a load-sensitive variable pump;
fig. 7 is a control flow chart of a suspension system of a two-axis flatbed.
In the figure: the hydraulic control system comprises a hydraulic tank, 2, a suspension hydraulic cylinder, 3, a load port independent control valve bank, 30, a control valve block, 31, a first two-position normally-open electro-hydraulic proportional valve, 32, a second two-position two-normally-open electro-hydraulic proportional valve, 33, a three-position four-way electro-hydraulic reversing valve, 34, a shuttle valve, 35, a two-position two-normally-closed electro-hydraulic proportional valve, 4, a load sensitive variable pump, 40, a sensitive variable valve block, 41, a first two-position three-way hydraulic reversing valve, 42, a second two-position three-way hydraulic reversing valve, 43, a power valve, 44, a variable pump, 45, a plunger cylinder, 46, a first damping hole, 47, a second damping hole, 48, a third damping hole, 5, a first two-position three-way electromagnetic reversing valve, 6, a second two-position three-way electromagnetic reversing valve, 7, a constant delivery pump, 8, an engine, 9, a coupling, 10, a first overflow valve, 11, a second overflow valve, 12, a gooseneck, 13, a flat car body, 14, a suspension, 15, a slewing support, 16, a suspension large arm, 17, a suspension arm support, a small wheel support, and a small wheel support.
Detailed Description
The invention will now be described in further detail with reference to the accompanying drawings. The drawings are simplified schematic representations which merely illustrate the basic structure of the invention and therefore show only the structures which are relevant to the invention.
In the embodiment of the hydraulic suspension system of the present invention shown in fig. 1-6, fig. 1 is an eight-axis flat car, which comprises a gooseneck 12, a flat car body 13 and suspensions 14, wherein the gooseneck 12 is positioned at the front section of the flat car body 13 and is used for being connected with a tractor, the suspensions 14 are fixed on auxiliary beams of the flat car body 13 by bolts and play the roles of supporting and connecting shafts, the whole lifting of the flat car can be realized, the number of the suspensions 14 is 2 times that of the axis of the flat car, for example, the eight-axis flat car is provided with 16 suspensions 14, and the two-axis flat car is provided with 4 suspensions 14.
The suspension 14 of the flat car is shown in fig. 2, and comprises a rotary support 15, a suspension big arm 16, a suspension hydraulic cylinder 2, an axle bracket 17, a suspension small arm 18 and wheels 19, wherein the rotary support 15 is positioned at the upper end of the suspension 14, and is connected with one end of the suspension big arm 16 through bolts, so that the whole suspension 14 rotates relative to the flat car body 13, the other end of the suspension big arm 16 is connected with the suspension small arm 18 through a suspension 14 arm shaft, the inner hinging point of the suspension big arm 16 is connected with the piston rod ear end of the suspension hydraulic cylinder 2 through a pin shaft, the cylinder body ear end of the suspension hydraulic cylinder 2 is connected with the hinging point of the suspension small arm 18 through a pin shaft, the suspension hydraulic cylinders 2 of all the suspensions 14 simultaneously extend and retract, the whole lifting function of the flat car body can be realized, the suspension small arm 18 is connected with the axle bracket 17 through bolts, two wheels 19 are respectively arranged at two ends of the axle bracket 17, and the wheels 19 play a role in supporting the car body and walking.
The invention is applicable to suspension 14 systems of various axis flat cars, and a two-axis flat car is taken as an example for explanation, and is combined with fig. 3 and 4, wherein the two-axis flat car is provided with four suspension hydraulic cylinders 2, and four load ports are needed to be controlled by independent control valve groups 3 respectively. The hydraulic suspension system of the two-axis flat shoe box comprises: the hydraulic system comprises an oil tank 1, a load sensitive variable pump 4, four suspension hydraulic cylinders 2, four load port independent control valve groups 3 connected with the suspension hydraulic cylinders 2, a first two-position three-way electromagnetic directional valve 5, a second two-position three-way electromagnetic directional valve 6 and a constant delivery pump 7.
Referring to fig. 3-5, the load port independent control valve group 3 includes a control valve block 30, a first two-position two-way normally open electro-hydraulic proportional valve 31, a second two-position two-way normally open electro-hydraulic proportional valve 32, a three-position four-way electro-hydraulic reversing valve 33, a shuttle valve 34, and a two-position two-way normally closed electro-hydraulic proportional valve 35; the control valve block 30 is provided with a first oil inlet P 1, a second oil inlet P 2, a first oil return port T 1, a second oil return port T 2, a first load sensing port LS 1, a second load sensing port LS 2, a first working oil port A 11 and a second working oil port B 4 respectively; an oil outlet A 3 of the load-sensitive variable pump 4 is connected with an oil inlet P 3 hydraulic pipeline of the first two-position three-way electromagnetic directional valve 5, a second working oil port B 1 of the first two-position three-way electromagnetic directional valve 5 is connected with an oil outlet A 4 hydraulic pipeline of the constant delivery pump 7, and a first working oil port A 6 of the first two-position three-way electromagnetic directional valve 5 is connected with a first oil inlet P 1 and a second oil inlet P 2 hydraulic pipeline; the first oil inlet P 1 and the second oil inlet P 2 are communicated with an oil inlet P 5 of the three-position four-way electro-hydraulic reversing valve 33 through an internal flow passage of the control valve block 30; the first working oil port A 7 of the three-position four-way electro-hydraulic reversing valve 33 is communicated with the oil inlet P 6 of the first two-position two-way normally-open electro-hydraulic proportional valve 31 through an internal flow passage of the control valve block 30; the oil outlet A 8 of the first two-position two-way normally-open electro-hydraulic proportional valve 31, the first comparison oil port A 15 of the shuttle valve 34 and the oil inlet P 8 of the two-position two-way normally-closed electro-hydraulic proportional valve 35 are communicated to the first working oil port A 11 through an internal flow passage of the control valve block 30; the first working oil port A 11 is communicated with the rodless cavity of the suspension hydraulic cylinder 2 through a hydraulic pipeline, and the rod cavity of the suspension hydraulic cylinder 2 is communicated with the second working oil port B 4 through a hydraulic pipeline; the oil outlet A 10 of the two-position normally-closed electro-hydraulic proportional valve 35 and the oil outlet A 9 of the second two-position normally-open electro-hydraulic proportional valve 32 are communicated to the second working oil port B 4 through an internal channel of the control valve block 30, and the oil inlet P 7 of the second two-position normally-open electro-hydraulic proportional valve 32 is communicated with the second working oil port B 3 of the three-position four-way electro-hydraulic reversing valve 33 through an internal channel; the load sensitive port X of the load sensitive variable pump 4 is connected with a first working oil port A 5 hydraulic pipeline of a second two-position three-way electromagnetic directional valve 6, and an oil return port T 3 of the three-position four-way electro-hydraulic directional valve 33 is communicated to a first oil return port T 1 and a second oil return port T 2 through internal flow channels; the load sensing port X of the load sensing variable pump 4 is communicated to the first load sensing port LS 1 through a hydraulic pipeline; the first load sensing port LS 1 is connected to the output port C 1 of the shuttle valve 34 through an internal flow passage; the second comparison oil port B 6 of the shuttle valve 34 is communicated to the second load sensing port LS 2 through an internal flow passage; the oil suction port S 2 of the metering pump 7 is connected to the oil tank 1 through a hydraulic pipe.
Referring to fig. 5, the second two-position three-way electromagnetic directional valve 6 is connected to a hydraulic pipeline between the load sensing port X and the second two-position three-way electromagnetic directional valve 6, and the load sensing port X is communicated with the first working oil port a 5 of the second two-position three-way electromagnetic directional valve 6 through the hydraulic pipeline; an oil inlet P 4 of the second two-position three-way electromagnetic directional valve 6 is communicated with the first load sensitive port LS 1 through a hydraulic pipeline; the oil outlet B 2 of the second two-position three-way electromagnetic directional valve 6 is connected to the oil tank 1 through a hydraulic pipeline.
Referring to fig. 3,4 and 6, the load-sensitive variable pump 4 includes: the sensitive variable valve block 40, the first two-position three-way hydraulic reversing valve 41, the second two-position three-way hydraulic reversing valve 42, the power valve 43, the variable pump 44, the plunger cylinder 45, the first damping hole 46, the second damping hole 47 and the third damping hole 48; an oil suction port S 1, an oil outlet A 3, an oil discharge port L 1 and a load sensitive port X are arranged on the sensitive variable valve block 40, the variable pump 44 is fixedly arranged on the sensitive variable valve block 40, and an oil inlet P 11 of the variable pump 44 is communicated with the oil suction port S 1 through an internal flow channel; the oil outlet A 16 of the variable pump 44, the oil outlet A 3 on the sensitive variable valve block 40, the first working oil port A 18 of the first two-position three-way hydraulic reversing valve 41, the first pilot oil port C 2, and the first working oil port A 19 and the first pilot oil port C 24 of the second two-position three-way hydraulic reversing valve 42 are communicated through an internal flow channel on the sensitive variable valve block 40; the oil inlet P 12 of the power valve 43, the oil outlet A 23 of the third damping hole 48 and the second pilot oil port C 5 of the second two-position three-way hydraulic reversing valve 42 are communicated to the load sensitive port X through an internal flow passage of the sensitive variable valve block 40; the oil discharge port L 2 of the variable pump 44, the oil outlet A 17 of the power valve 43, the second working port B 8 of the second two-position three-way hydraulic reversing valve 42 and the second pilot port C3 of the first two-position three-way hydraulic reversing valve 41 are communicated to the oil discharge port L 1 through an internal flow passage of the sensitive variable block; the oil inlet P 15 of the first damping hole 46, the oil inlet P 14 of the second two-position three-way hydraulic electromagnetic valve, the second working oil port B 7 of the first two-position three-way hydraulic reversing valve 41 and the oil outlet A 20 of the second damping hole 47 are communicated through an internal flow passage of the sensitive variable valve block 40; the oil inlet P 16 of the second damping hole 47, the oil inlet P 13 of the first two-position three-way hydraulic reversing valve 41 and the oil inlet A 21 of the plunger cylinder 45 are communicated through an internal flow passage of the sensitive variable valve block 40; the piston rod of the plunger cylinder 45, the variable mechanism push rod of the variable displacement pump 44, and the spring adjuster of the power valve 43 are connected by a mechanical structure such that the displacement amount of the piston rod varies in proportion to the displacement of the variable displacement pump 44, the spring force of the power valve 43.
Referring to fig. 4, the hydraulic suspension system further comprises an engine 8, and an output shaft of the engine 8 is connected with an input shaft of the load-sensitive variable pump 4 through a coupling 9; the input shaft of the constant displacement pump 7 is connected with the tail shaft hole of the load sensitive variable displacement pump 4.
Referring to fig. 3 and 4, an oil outlet a 3 of the load-sensitive variable pump 4 and an oil inlet P 3 of the first two-position three-way electromagnetic directional valve 5 are both hydraulically connected with an oil inlet P 9 of the first relief valve 10, and an oil outlet a 13 of the first relief valve 10 is connected to the oil tank 1 through a hydraulic pipe. The second working oil port B 1 of the first two-position three-way electromagnetic directional valve 5 and the oil outlet A 4 of the constant delivery pump 7 are both connected to the oil inlet P 10 of the second overflow valve 11 through hydraulic pipelines, and the oil outlet A 14 of the second overflow valve 11 is connected to the oil tank 1 through hydraulic pipelines.
Referring to fig. 4, a second oil inlet P 2, a first oil return port T 2, a second load sensing port LS 2 of the first load port independent control valve group 3 are connected with a first oil inlet P 1, a first oil return port T 1, and a first load sensing port LS 1 of the second load port independent control valve group 3 through hydraulic pipelines respectively, and so on, wherein a second oil inlet P2, a second load sensing port LS2, and a second oil return port T2 of the fourth load port independent control valve group 3 are plugged through bolts.
If the axis is increased, only the load port independent control valve groups 3 are required to be increased according to the number of the suspension hydraulic cylinders 2, for example, a load port independent hydraulic system of eight-axis sixteen suspension 14 is required to be increased, 16 suspension hydraulic cylinders 2 are required to be oiled, only 16 load port independent control valve groups 3 are required to be increased correspondingly, and not only can the lifting of each suspension 14 be controlled independently.
Referring to fig. 7, the lifting control method of the hydraulic suspension system according to the embodiment of the invention is as follows:
Step 1: initializing a control system, checking whether input and output parameters of a controller, an operation handle, a sensor, a displacement sensor, a load port independent control valve group 3 and the like are normal or not, if not, not executing downwards, and alarming; if normal, execution continues downward.
Step 2: parameter setting: the springs of the first overflow valve 10 and the second overflow valve 11 are regulated, the overflow pressure of the first overflow valve 10 and the second overflow valve 11 is set, and the overflow pressure of the first overflow valve 10 is the highest pressure of the suspension 14 system operation and is set to be a high value, for example, set to be 28MPa; the relief pressure of the second relief valve 11 is the oil make-up pressure of the suspension 14 system, should be low, for example set to 2MPa; other relevant parameters are set.
Step 3: and (5) data acquisition, namely acquiring an input signal of an operation handle.
Step 4: judging the whole lifting mode, namely judging whether the lifting mode is in the lifting mode or not through a lifting start button of the operating handle, if a lifting start signal is not read from the operating handle, stopping the lifting; if a "lift start" signal is read in.
Step 5: overall raising/lowering mode judgment: judging that the operation handle is in an integral lifting/falling mode through an integral lifting button and an integral falling button of the operation handle, if an integral lifting signal is read from the operation handle, entering a step 6.1; if a "drop-in" signal is read from the operating handle, step 6.2 is entered.
Step 6.1: in the integral lifting mode, after the input analog signals of the ' integral lifting ' of the operating handle are obtained, the electromagnets of the first two-position three-way electromagnetic directional valve 5 and the second two-position three-way electromagnetic directional valve 6 are simultaneously powered off, the load sensitive variable pump 4 supplies oil to the suspension 14 system, meanwhile, the left electromagnets of the three-position four-way electro-hydraulic directional valves 33 of the four-load port independent control valve group 3 are simultaneously powered on, as the three-position four-way electro-hydraulic directional valves 33 are large-flow control valves and only play a role in reversing, the throttle speed regulation function is not realized, the electromagnets of the two-position two-way normally-closed electro-hydraulic proportional valve 35 of the four-load port independent control valve group 3 are simultaneously powered off, the equal proportion of the electromagnets are converted into the input current signals of the first two-position two-normally-open electro-hydraulic proportional valve 31 according to the input analog signal value of the operating handle, so that the throttle speed regulation function is realized, and simultaneously, the input current signals of the second two-position two-normally-open electro-hydraulic proportional valve group 32 are set to be maximum, so that the full-port opening of the second two-position two-normally-open electro-hydraulic proportional valve group 32 is guaranteed, and the energy-saving control mode of ' throttle speed regulation of the throttle speed regulation valve is realized, the four-position two-normally-open electro-hydraulic proportional valve group 3 is provided with the throttle speed control valve 2 is driven by the four-position plate valve 2, the four-position load control valve 2 is driven by the four-position control valve 2, and the throttle speed control valve 2 is driven by the throttle valve 2, and the throttle valve 2. Meanwhile, hydraulic oil flows out from rod cavities of the four suspension hydraulic cylinders 2, flows back to the oil tank 1 through a fully-opened second two-position two-normally-open electric liquid proportional valve 32, a left position of a three-position four-way electric liquid reversing valve 33 and a first oil return port T 1 or a second oil return port T 2 of the four-load-port independent control valve group 3; in the process of 'integrally lifting', the rodless cavities of the four suspension hydraulic cylinders 2 are high pressure, the highest pressure of the rodless cavities of the four suspension hydraulic cylinders 2 is fed back to the load sensitive port X of the load sensitive variable pump 4 through the second two-position three-way electromagnetic reversing valve 6 by the comparison function of the four shuttle valves 34 of the load port independent control valve group 3, so that the load sensitive variable pump 4 can realize the functions of load sensitivity, constant power and pressure cutoff, and the load sensitive variable pump 4 adjusts the oil supply speed and the oil supply quantity by the load change condition.
Step 6.2: integral landing mode: after the input analog signals of 'integral drop' of the operating handle are obtained, the electromagnets of the first two-position three-way electromagnetic directional valve 5 and the second two-position three-way electromagnetic directional valve 6 are simultaneously electrified, oil is supplied to the suspension 14 system by the constant displacement pump 7, the load sensitive port X of the load sensitive variable pump 4 is communicated with the oil tank 1, the load sensitive variable pump 4 works at minimum pressure and is in an energy-saving mode, and in the process of 'integral drop', the flat car body moves under the action of gravity, high pressure is generated by all rodless cavities of the suspension hydraulic cylinder 2, the right electromagnets of the four three-position four-way electro-hydraulic directional valves 33 of the load port independent control valve group 3 are simultaneously electrified, and the equal proportion is converted into the input current signals of the first two-position two-way normal open-electric liquid proportional valve 31 according to the input analog signal value of the operating handle, so that the outlet throttle speed regulation function is achieved. Meanwhile, the input current signal of the second two-position two-normally-open electro-hydraulic proportional valve 32 is set to be the maximum value, the electromagnets of the four two-position two-normally-closed electro-hydraulic proportional valves 35 of the load port independent control valve group 3 are simultaneously input with the maximum current value, and the flow regeneration mode is started, so that hydraulic oil flows out of the constant delivery pump 7, enters from the first oil inlet P 1 or the second oil inlet P 2 of the four-load port independent control valve group 3, passes through the right position of the three-position four-way electro-hydraulic reversing valve 33, and supplements oil to the rod cavities of the four suspension hydraulic cylinders 2 after passing through the second two-position two-normally-open electro-hydraulic proportional valve 32. Meanwhile, after the electromagnet of the first two-position two-way normally-open electric liquid proportional valve 31 receives a proportional current signal, hydraulic oil flowing out of rodless cavities of the four suspension hydraulic cylinders 2 flows back to the oil tank 1 through the first oil return port T 1 or the second oil return port T 2 of the three-position four-way electric liquid reversing valve 33 and the four load port independent control valve group 3 after the hydraulic oil is throttled and regulated by the first two-position two-way normally-open electric liquid proportional valve 31; in the process of 'integral drop', because under the action of gravity, the rodless cavities of the four suspension hydraulic cylinders 2 generate high-pressure oil, one part of the high-pressure oil flows back to the oil tank 1 through the throttling speed regulation function of the first two-position two-normally-open electro-hydraulic proportional valve 31, the other part of the high-pressure oil flows into the rod cavities of the four suspension hydraulic cylinders 2 through the two-position two-normally-closed electro-hydraulic proportional valve 35, and when the rod cavities of the four suspension hydraulic cylinders 2 are insufficient in flow, the constant delivery pump 7 only needs to supplement oil, so that the 'outlet throttling speed regulation and inlet flow regeneration' are realized, and the energy saving of the system can be realized.
Each suspension hydraulic cylinder is individually controlled by a load port independent control valve group 3 connected with a load sensitive variable pump 4.
It should be understood that the above-described specific embodiments are only for explaining the present invention and are not intended to limit the present invention. Obvious variations or modifications which extend from the spirit of the present invention are within the scope of the present invention.
Claims (9)
1. A hydraulic suspension system characterized by: the hydraulic control system comprises an oil tank (1), a load sensitive variable pump (4), at least one suspension hydraulic cylinder (2), load port independent control valve groups (3) corresponding to the suspension hydraulic cylinders (2), a first two-position three-way electromagnetic directional valve (5), a second two-position three-way electromagnetic directional valve (6) and a dosing pump (7); the load port independent control valve group (3) comprises a control valve block (30), a first two-position normally-open electro-hydraulic proportional valve (31), a second two-position two-normally-open electro-hydraulic proportional valve (32), a three-position four-way electro-hydraulic reversing valve (33), a shuttle valve (34) and a two-position two-normally-closed electro-hydraulic proportional valve (35); a first oil inlet P 1, a second oil inlet P 2, a first oil return port T 1, a second oil return port T 2, a first load sensitive port LS 1, a second load sensitive port LS 2, a first working oil port A 11 and a second working oil port B 4 are drilled on the control valve block (30) respectively; an oil outlet A 3 of the load-sensitive variable pump (4) is connected with an oil inlet P 3 hydraulic pipeline of the first two-position three-way electromagnetic directional valve (5), a second working oil port B 1 of the first two-position three-way electromagnetic directional valve (5) is connected with an oil outlet A 4 hydraulic pipeline of the constant delivery pump (7), and a first working oil port A 6 of the first two-position three-way electromagnetic directional valve (5) is connected with the first oil inlet P 1 and the second oil inlet P 2 hydraulic pipeline; the first oil inlet P 1 and the second oil inlet P 2 are communicated with an oil inlet P 5 of the three-position four-way electro-hydraulic reversing valve (33) through an internal flow passage of the control valve block (30); the first working oil port A 7 of the three-position four-way electro-hydraulic reversing valve (33) is communicated with the oil inlet P 6 of the first two-position two-way normally-open electro-hydraulic proportional valve (31) through an internal flow passage of the control valve block (30); the oil outlet A 8 of the first two-position two-way normally-open electro-hydraulic proportional valve (31), the first comparison oil port A 15 of the shuttle valve (34) and the oil inlet P 8 of the two-position two-way normally-closed electro-hydraulic proportional valve (35) are communicated to the first working oil port A 11 through an internal flow passage of the control valve block (30); the first working oil port A 11 is communicated with the rodless cavity of the suspension hydraulic cylinder (2) through a hydraulic pipeline, and the rod cavity of the suspension hydraulic cylinder (2) is communicated with the second working oil port B 4 through a hydraulic pipeline; an oil outlet A 10 of the two-position normally-closed electro-hydraulic proportional valve (35) and an oil outlet A 9 of the second two-position normally-open electro-hydraulic proportional valve (32) are communicated to the second working oil port B 4 through an internal channel of the control valve block (30), and an oil inlet P 7 of the second two-position normally-open electro-hydraulic proportional valve (32) is communicated with the second working oil port B3 of the three-position four-way electro-hydraulic reversing valve (33) through an internal channel; the load sensitive port X of the load sensitive variable pump (4) is connected with a hydraulic pipeline of a first working oil port A 5 of the second two-position three-way electromagnetic directional valve (6), and an oil return port T 3 of the three-position four-way electro-hydraulic directional valve (33) is communicated to the first oil return port T 1 and the second oil return port T 2 through internal flow channels; the load sensing port X of the load sensing variable pump (4) is communicated to the first load sensing port LS 1 through a hydraulic pipeline; the first load sensing port LS 1 is communicated to an output port C 1 of the shuttle valve (34) through an internal flow passage; a second comparison oil port B 6 of the shuttle valve (34) is communicated to the second load sensitive port LS 2 through an internal flow passage; an oil suction port S 2 of the constant delivery pump (7) is connected to the oil tank (1) through a hydraulic pipeline.
2. A hydraulic suspension system according to claim 1, wherein: the second two-position three-way electromagnetic directional valve (6) is connected to a hydraulic pipeline between the load sensitive port X and the second two-position three-way electromagnetic directional valve (6), and the load sensitive port X is communicated with a first working oil port A 5 of the second two-position three-way electromagnetic directional valve (6) through the hydraulic pipeline; an oil inlet P 4 of the second two-position three-way electromagnetic directional valve (6) is communicated with the first load sensitive port LS 1 through a hydraulic pipeline; an oil outlet B 2 of the second two-position three-way electromagnetic directional valve (6) is connected to the oil tank (1) through a hydraulic pipeline.
3. A hydraulic suspension system according to claim 1, wherein: the load-sensitive variable pump (4) comprises: the system comprises a sensitive variable valve block (40), a first two-position three-way hydraulic reversing valve (41), a second two-position three-way hydraulic reversing valve (42), a power valve (43), a variable pump (44), a plunger cylinder (45), a first damping hole (46), a second damping hole (47) and a third damping hole (48); an oil suction port S 1, an oil outlet A 3, an oil discharge port L 1 and a load sensitive port X are arranged on the sensitive variable valve block (40), the variable pump (44) is fixedly arranged on the sensitive variable valve block (40), and an oil inlet P 11 of the variable pump (44) is communicated with the oil suction port S 1 through an internal flow channel; an oil outlet A 16 of the variable pump (44), an oil outlet A 3 on the sensitive variable valve block (40), a first working oil port A 18 and a first pilot oil port C 2 of the first two-position three-way hydraulic reversing valve (41) and a first working oil port A 19 and a first pilot oil port C 24 of the second two-position three-way hydraulic reversing valve (42) are communicated through an internal flow channel on the sensitive variable valve block (40); an oil inlet P 12 of the power valve (43), an oil outlet A 23 of the third damping hole (48) and a second pilot oil port C 5 of the second two-position three-way hydraulic reversing valve (42) are communicated to the load sensitive port X through an internal flow passage of the sensitive variable valve block (40); an oil discharge port L 2 of the variable pump (44), an oil outlet A 17 of the power valve (43), a second working port B 8 of the second two-position three-way hydraulic reversing valve (42) and a second pilot port C3 of the first two-position three-way hydraulic reversing valve (41) are communicated to the oil discharge port L 1 through an internal flow passage of the sensitive variable valve block; an oil inlet P 15 of the first damping hole (46), an oil inlet P 14 of the second two-position three-way hydraulic electromagnetic valve, a second working oil port B 7 of the first two-position three-way hydraulic reversing valve (41) and an oil outlet A 20 of the second damping hole (47) are communicated through an internal flow passage of the sensitive variable valve block (40); an oil inlet P 16 of the second damping hole (47), an oil inlet P 13 of the first two-position three-way hydraulic reversing valve (41) and an oil inlet A 21 of the plunger cylinder (45) are communicated through an internal flow passage of the sensitive variable valve block (40); the piston rod of the plunger cylinder (45), the variable mechanism pushing rod of the variable pump (44) and the spring regulator of the power valve (43) are connected through a mechanical structure, so that the displacement of the piston rod is changed in proportion to the displacement of the variable pump (44) and the spring force of the power valve (43).
4. A hydraulic suspension system according to claim 3, wherein: the device also comprises an engine (8), wherein an output shaft of the engine (8) is connected with an input shaft of the load-sensitive variable pump (4) through a coupler (9); the input shaft of the quantitative pump (7) is connected with the tail shaft hole of the load sensitive variable pump (4).
5. A hydraulic suspension system according to claim 3, wherein: an oil outlet A 3 of the load-sensitive variable pump (4) and an oil inlet P 3 of the first two-position three-way electromagnetic directional valve (5) are connected with an oil inlet P 9 of the first overflow valve (10) through hydraulic pipelines, and an oil outlet A 13 of the first overflow valve (10) is connected to an oil tank (1) through a hydraulic pipeline.
6. The hydraulic suspension system of any one of claims 3-5 wherein: the second working oil port B 1 of the first two-position three-way electromagnetic directional valve (5) and the oil outlet A 4 of the constant delivery pump (7) are both connected to the oil inlet P 10 of the second overflow valve (11) through a hydraulic pipeline, and the oil outlet A 14 of the second overflow valve (11) is connected to the oil tank (1) through a hydraulic pipeline.
7. A hydraulic suspension system according to claim 1, wherein: the number of the suspension hydraulic cylinders (2) is four.
8. A hydraulic suspension system according to claim 1, wherein: on the axis of the flatbed that sets up, set up two hydraulic suspension on every axis.
9. A lifting control method of a hydraulic suspension system is characterized in that:
the ascending control method comprises the following steps: the electromagnets of the first two-position three-way electromagnetic directional valve (5) and the second two-position three-way electromagnetic directional valve (6) are powered off simultaneously, oil is supplied to a suspension (14) system by a load sensitive variable pump (4), the left electromagnet of the three-position four-way electro-hydraulic directional valve (33) is powered on simultaneously, the electromagnets of the two-position two-way normally-closed electro-hydraulic proportional valve (35) are powered off simultaneously, a current signal is input to the first two-position two-way normally-open electro-hydraulic proportional valve (31) to throttle and regulate the inlet, and meanwhile, the input current signal of the second two-position two-way normally-open electro-hydraulic proportional valve (32) is set to be the maximum value, so that the full opening of the valve port of the second two-position two-way normally-open electro-hydraulic proportional valve (32) is ensured; hydraulic oil enters from an oil inlet P 1 or P 2, enters a rodless cavity of a suspension hydraulic cylinder (2) after passing through the left position of a three-position four-way electro-hydraulic reversing valve (33) and through the throttling speed regulation of a first two-position two-way normally-open electro-hydraulic reversing valve (31), pushes a piston rod of the suspension hydraulic cylinder (2) to extend, further pushes a flat car body to lift upwards, simultaneously, flows out from rod cavities of the four suspension hydraulic cylinders (2), and flows back to an oil tank (1) through the left position of a fully-opened second two-position two-way normally-open electro-hydraulic reversing valve (32), a first oil return port T 1 or a second oil return port T 2 of the three-position four-way electro-hydraulic reversing valve (33); the pressure between the rod cavity and the rodless cavity of the suspension hydraulic cylinder (2) is fed back to the load sensitive variable pump (4) through the second two-position three-way electromagnetic reversing valve (6), so that the load sensitive variable pump (4) adjusts the oil supply speed and the oil supply quantity according to the load change condition;
The descent control method comprises the following steps: the electromagnets of the first two-position three-way electromagnetic directional valve (5) and the second two-position three-way electromagnetic directional valve (6) are simultaneously powered, oil is supplied to a suspension (14) system by a constant displacement pump (7), a load sensitive port X of a load sensitive variable pump (4) is communicated with an oil tank (1) through the second two-position three-way electromagnetic directional valve (6), the load sensitive variable pump (4) works at minimum pressure, the electromagnet is in an energy-saving mode, under the action of gravity of a flat car body, a rodless cavity of a suspension hydraulic cylinder (2) generates high pressure, the right electromagnet of a three-position four-way electro-hydraulic directional valve (33) is simultaneously powered on, a first two-position two-way normally-open electro-hydraulic proportional valve (31) regulates speed according to an input current signal, so that an outlet throttling speed regulating function is achieved, meanwhile, the input current signal of the second two-position two-way normally-open electro-hydraulic proportional valve (32) is set as a maximum value, the electromagnets of the two-position two-way normally-closed electro-hydraulic proportional valve (35) are simultaneously input with a maximum current value, and a flow regeneration mode is started; the hydraulic oil is subjected to right position of a three-position four-way electro-hydraulic reversing valve (33), oil is replenished to a rod cavity of a suspension hydraulic cylinder (2) after passing through a second two-position two-way normally-open electro-hydraulic proportional valve (32), meanwhile, after the electromagnet of a first two-position two-way normally-open electro-hydraulic reversing valve (31) receives a proportional current signal, the hydraulic oil flows out of a rodless cavity of the suspension hydraulic cylinder (2), and then flows back to an oil tank (1) after passing through the right position of the three-position four-way electro-hydraulic reversing valve (33) and a first oil return port T 1 or a second oil return port T 2 after being subjected to throttling and speed regulation of the first two-position two-way normally-open electro-hydraulic reversing valve (31); and one part of high-pressure oil generated by the rodless cavity flows back to the oil tank (1) through the throttling speed regulation function of the first two-position two-way normally-open electro-hydraulic proportional valve (31), the other part flows into the rod cavity of the suspension hydraulic cylinder (2) through the two-position two-way normally-closed electro-hydraulic proportional valve (35), and when the flow of the rod cavity of the suspension hydraulic cylinder (2) is insufficient, the oil is supplemented to the rod cavity by the constant delivery pump (7), so that the outlet throttling speed regulation and the inlet flow regeneration are realized.
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| CN111927836B (en) * | 2020-09-09 | 2021-01-08 | 湖南三一中型起重机械有限公司 | Hydraulic cylinder control device, variable amplitude hydraulic system and crane |
| CN115107892A (en) * | 2022-07-22 | 2022-09-27 | 安徽开乐专用车辆股份有限公司 | Vehicle-mounted platform applied to nuclear power treasure transportation system |
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