CN111483284A - 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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- CN111483284A CN111483284A CN202010484725.8A CN202010484725A CN111483284A CN 111483284 A CN111483284 A CN 111483284A CN 202010484725 A CN202010484725 A CN 202010484725A CN 111483284 A CN111483284 A CN 111483284A
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- 239000000725 suspension Substances 0.000 title claims abstract description 137
- 238000000034 method Methods 0.000 title claims abstract description 30
- 239000003921 oil Substances 0.000 claims description 296
- 238000006073 displacement reaction Methods 0.000 claims description 29
- 238000013016 damping Methods 0.000 claims description 24
- 239000010720 hydraulic oil Substances 0.000 claims description 12
- 230000008929 regeneration Effects 0.000 claims description 9
- 238000011069 regeneration method Methods 0.000 claims description 9
- 230000009471 action Effects 0.000 claims description 7
- 230000005484 gravity Effects 0.000 claims description 5
- 230000008859 change Effects 0.000 claims description 3
- 230000008878 coupling Effects 0.000 claims description 3
- 238000010168 coupling process Methods 0.000 claims description 3
- 238000005859 coupling reaction Methods 0.000 claims description 3
- 230000007246 mechanism Effects 0.000 claims description 3
- 230000001174 ascending effect Effects 0.000 claims description 2
- 230000000694 effects Effects 0.000 claims description 2
- 230000008569 process Effects 0.000 abstract description 17
- 230000005540 biological transmission Effects 0.000 abstract description 2
- 230000001105 regulatory effect Effects 0.000 description 7
- 238000010586 diagram Methods 0.000 description 5
- 238000004134 energy conservation Methods 0.000 description 3
- 244000261422 Lysimachia clethroides Species 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
- 230000006978 adaptation Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012530 fluid Substances 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
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
- 230000001502 supplementing effect Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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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
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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
- 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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2500/00—Indexing codes relating to the regulated action or device
- B60G2500/30—Height or ground clearance
-
- 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, load port independent control valve groups, 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 load port independent control valve groups are in the number corresponding to that of the suspension hydraulic cylinders; the load port independent control valve group comprises a control valve block, a first two-position two-way normally-opened electro-hydraulic proportional valve, a second two-position two-way normally-opened electro-hydraulic proportional valve, a three-position four-way electro-hydraulic reversing valve, a shuttle valve and a two-position two-way normally-closed electro-hydraulic proportional valve. In the integral lifting process, the load sensitive variable pump is adopted to supply oil, and in the integral falling process, the constant delivery pump is adopted to supply oil, so that the use frequency of the load sensitive variable pump can be reduced, and in the integral falling process, the output power of the constant delivery pump is lower, 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 the transportation of heavy, large, high and special-shaped structures, has the advantages of flexible use, convenient loading and unloading, and the load capacity of more than 50000 tons under the condition of multi-car mechanical assembly or free combination, and is widely applied in the engineering fields of equipment manufacturing industry, petroleum, chemical industry, marine petroleum, bridge construction and the like. The multi-axis flat car mainly comprises a frame wheel shaft, a suspension system, a steering system, a hydraulic system, a braking system, a power system, a control system and the like. The frame adopts a welding structure with a high-strength alloy steel box-shaped section and comprises a main beam, an auxiliary beam, a cross beam, an inclined support and an end beam. The wheel shafts are arranged at the bottom of the frame, the wheel shafts capable of steering independently are longitudinally arranged along the two sides of the frame, and each wheel shaft is provided with 2 tires. A typical flatbed has 2-10 axes per column, 2 suspension systems per axis, 2 axles, 4 tires per axis.
The suspension system of the multi-axis flat car is supported on the auxiliary beam and plays a role in supporting and connecting the wheel shaft, the suspension system comprises a rotary support, a suspension pivot, a large suspension arm, a small suspension arm, a swing shaft, a suspension hydraulic cylinder, wheels and the like, and the suspension hydraulic cylinder of the multi-axis flat car extends out and retracts simultaneously, so that the integral lifting function of the body of the flat car can be realized. The driving suspension hydraulic cylinder generally adopts a combination form of a load-sensitive variable pump and a load-sensitive multi-way valve, 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 excessive, the power of an engine needs 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 path and an outlet oil path of a hydraulic actuator, and corresponding control logics can be designed according to the number and the functions of the control valves, so that the functions of flow regeneration, inlet and outlet independent control, 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 multi-axis flat car is subjected to the action of gravity, so that the oil supply requirement is low, the traditional load sensitive system still needs to supply oil to a suspension system in order to control the landing speed, and the more the axes are, the larger the engine power is, so that the 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 can realize speed control in the integral lifting process of the flat car, have a flow regeneration function, effectively reduce throttling loss and realize system energy conservation.
The technical scheme adopted by the invention for solving the technical problems is as follows:
the invention discloses a hydraulic suspension system, which is characterized in that: the system comprises an oil tank, a load sensitive variable pump, at least one suspension hydraulic cylinder, load port independent control valve groups, 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 groups corresponds to that of the suspension hydraulic cylinders; the load port independent control valve group comprises a control valve block, a first two-position two-way normally-opened electro-hydraulic proportional valve, a second two-position two-way normally-opened electro-hydraulic proportional valve, a three-position four-way electro-hydraulic reversing valve, a shuttle valve and a two-position two-way normally-closed electro-hydraulic proportional valve; a first oil inlet P is drilled on the control valve block respectively1A second oil inlet P2The first oil return port T1A second oil return port T2A first load sensing port L S1A second load sensing port L S2The first working oil port A11And a second working oil port B4(ii) a Of said load-sensitive variable displacement pumpsOil outlet A3And an oil inlet P of the first two-position three-way electromagnetic directional valve3A hydraulic pipeline is connected, and a second working oil port B of the first two-position three-way electromagnetic directional valve1With the oil outlet A of the fixed displacement pump4A hydraulic pipeline is connected, and a first working oil port A of the first two-position three-way electromagnetic directional valve6With said first oil inlet P1And the second oil inlet P2Hydraulic pipeline connection; the first oil inlet P1And the second oil inlet P2Through the internal flow passage of the control valve block and the oil inlet P of the three-position four-way electro-hydraulic reversing valve5Communicating; the first working oil port A of the three-position four-way electro-hydraulic reversing valve7And an oil inlet P of the first two-position two-normally-opened electro-hydraulic proportional valve6Communicated through an internal flow passage of the control valve block; oil outlet A of first two-position two-normally-opened electro-hydraulic proportional valve8First comparing oil port A of shuttle valve15Oil inlet P of two-position two-way normally-closed electro-hydraulic proportional valve8Are communicated to the first working oil port A through an inner flow passage of the control valve block11(ii) a The first working oil port A11The rodless cavity of the suspension hydraulic cylinder 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 through a hydraulic pipeline4Communicating; oil outlet A of the two-position two-way normally-closed electro-hydraulic proportional valve10Oil outlet A of second two-position two-way normally-opened electro-hydraulic proportional valve9Is communicated to the second working oil port B through an internal channel of the control valve block4The oil inlet P of the second two-position two-way normally-opened electro-hydraulic proportional valve7The three-position four-way electro-hydraulic reversing valve is communicated with a second working oil port B3 of the three-position four-way electro-hydraulic reversing valve through an internal flow passage; the load sensitive port X of the load sensitive variable displacement pump and the first working oil port A of the second two-position three-way electromagnetic directional valve5Hydraulic pipeline connection, oil return port T of three-position four-way electro-hydraulic reversing valve3Is communicated to the first oil return port T through an internal flow passage1And said second oil return port T2The load sensing port X of the load sensing variable pump is communicated to the first load sensing port L S through a hydraulic pipeline1(ii) a The first negativeCarrier sensing port L S1An oil outlet C communicated to the shuttle valve through an internal flow passage1(ii) a A second comparing oil port B of the shuttle valve6Is communicated to the second load sensing port L S through an internal flow passage2(ii) a The oil suction port S of the fixed displacement pump2Is connected to the oil tank through a hydraulic pipeline.
Further, the second two-position three-way electromagnetic directional valve is connected to the hydraulic pipeline between the load sensing port X and the second two-position three-way electromagnetic directional valve, and the load sensing port X and the first working oil port A of the second two-position three-way electromagnetic directional valve5Are communicated through a hydraulic pipeline; oil inlet P of second two-position three-way electromagnetic directional valve4Through hydraulic pipeline and the first load sensing port L S1Communicating; oil outlet B of second two-position three-way electromagnetic directional valve2Is connected to the oil tank through a hydraulic pipeline.
Further, the load sensitive variable displacement pump includes: the variable valve 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 is arranged on the sensitive variable valve block1Oil outlet A3And an oil discharge port L1The variable pump is fixedly arranged on the sensitive variable valve block, and an oil inlet P of the variable pump11And the oil suction opening S1Are communicated through an internal flow passage; the oil outlet A of the variable pump16Oil outlet A on sensitive variable valve block3A first working oil port A of a first two-position three-way hydraulic reversing valve18And a first pilot oil port C2And a first working oil port A of a second two-position three-way hydraulic reversing valve19And a first pilot oil port C24Communicating through an internal flow passage on the sensitive variable valve block; an oil inlet P of the power valve12Oil outlet A of the third damping hole23And a second pilot oil port C of a second two-position three-way hydraulic reversing valve5Communicated to the load sensitive port X through an internal flow passage of the sensitive variable valve block and an oil discharge port L of the variable pump2Power valveOil outlet A of17A second working oil port B of a second two-position three-way hydraulic reversing valve8The second pilot oil port C3 of the first two-position three-way hydraulic reversing valve is communicated to the oil discharge port L through the internal flow passage of the sensitive variable block1(ii) a An oil inlet P of the first damping hole15And an oil inlet P of a second two-position three-way hydraulic electromagnetic valve14A second working oil port B of the first two-position three-way hydraulic reversing valve7Oil outlet A of second damping hole20The internal flow channels are communicated through the sensitive variable valve block; an oil inlet P of the second damping hole16An oil inlet P of a first two-position three-way hydraulic reversing valve13Oil inlet A of plunger cylinder21The internal flow channels are communicated through the sensitive variable valve block; the piston rod of the plunger cylinder, the variable mechanism push rod of the variable pump and the spring regulator of the power valve are connected through mechanical structures, so that the displacement of the piston rod changes in proportion to the displacement of the variable pump and the spring force of the power valve.
The output shaft of the engine is connected with the input shaft of the load-sensitive variable pump through a coupling; the input shaft of the constant delivery pump is connected with the tail end shaft hole of the load-sensitive variable delivery pump.
Further, an oil outlet A of the load-sensitive variable pump3And the oil inlet P of the first two-position three-way electromagnetic directional valve3Oil inlet P of first overflow valve connected with equal hydraulic pipeline9An oil outlet A of the first overflow valve13Is connected to the oil tank through a hydraulic pipeline.
Further, a second working oil port B of the first two-position three-way electromagnetic directional valve1And an oil outlet A of the fixed displacement pump4Are connected to an oil inlet P of a second overflow valve through hydraulic pipelines10An oil outlet A of the second overflow valve14Is connected to the oil tank through a hydraulic pipeline.
Further, the number of the suspension hydraulic cylinders is four.
Furthermore, the flat car is arranged on the axes, and two hydraulic suspension systems are arranged on each axis.
The invention also discloses a lifting control method of the hydraulic suspension system, which is characterized by comprising the following steps:
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 simultaneously de-energized, the load sensitive variable displacement pump supplies oil to the suspension system, the left electromagnet of the three-position four-way electromagnetic reversing valve is simultaneously energized, the electromagnet of the two-position two-way normally closed electro-hydraulic proportional valve is simultaneously de-energized, a current signal is input to the first two-position two-way normally open electro-hydraulic proportional valve to throttle and regulate the inlet, 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, and the full opening of the valve port of the second two-position two-way normally open; hydraulic oil inlet P1Or P2The hydraulic oil enters a rodless cavity of the suspension hydraulic cylinder after passing through the left position of the three-position four-way electro-hydraulic reversing valve and throttling and speed regulating of the first two-position two-way normally-opened electro-hydraulic proportional valve, a piston rod of the suspension hydraulic cylinder is pushed to extend, the body of the flat car is further pushed to upwards rise, meanwhile, the hydraulic oil flows out of rod cavities of the four suspension hydraulic cylinders and passes through a fully-opened second two-position two-way normally-opened electro-hydraulic proportional valve, the left position of the three-position four-way electro-hydraulic reversing valve and a first oil return port T1Or a second oil return port T2Flows back to the oil tank; 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 directional valve, so that the load sensitive variable pump adjusts the oil supply speed and the oil supply amount according to the load change condition;
the descending control method comprises the following steps: electromagnets of a first two-position three-way electromagnetic reversing valve and a second two-position three-way electromagnetic reversing valve are simultaneously electrified, oil is supplied to a suspension system by a constant delivery pump, 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 reversing valve, the load sensitive variable pump works at the minimum pressure and is in an energy-saving mode, a rodless cavity of a suspension hydraulic cylinder generates high pressure under the action of gravity of a body of a flat car, a right electromagnet of the three-position four-way electro-hydraulic reversing valve is simultaneously electrified, a first two-position two-normally-opened electro-hydraulic proportional valve regulates speed according to an input current signal, so that the effect of throttling and regulating speed of an outlet is achieved, and meanwhile, the second two-position twoThe input current signal of the normally open electro-hydraulic proportional valve is set to be the maximum value, the maximum current value is simultaneously input into the electromagnet of the two-position two-way normally closed electro-hydraulic proportional valve, and the flow regeneration mode is started; the hydraulic oil passes through the right position of the three-position four-way electro-hydraulic reversing valve and then passes through the second two-position two-way normally-opened electro-hydraulic proportional valve, oil is supplemented to the rod cavity of the suspension hydraulic cylinder, meanwhile, the electromagnet of the first two-position two-way normally-opened electro-hydraulic proportional valve receives a proportional current signal and then flows out of the rodless cavity of the suspension hydraulic cylinder, and then the hydraulic oil passes through the throttle speed regulation of the first two-position two-way normally-opened electro-hydraulic proportional valve and then passes through the right position of the three-position four-way electro-hydraulic reversing valve and the first1Or a second oil return port T2Flows back to the oil tank; one part of high-pressure oil generated by the rodless cavity flows back to the oil tank through the throttling and speed-regulating function of the first two-position two-way normally-opened electro-hydraulic proportional valve, 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 metering pump supplies oil to the rod cavity, so that the purposes of 'outlet throttling and speed regulation and inlet flow regeneration' are realized.
The invention also discloses a multi-axis flat car, which is characterized in that: the hydraulic suspension system 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 the 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 double-pump switching oil supply system is constructed by adopting the load sensitive variable pump, the constant delivery pump and the two-position three-way electromagnetic directional valve, can be switched 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 constant delivery pump to supply oil in the integral falling process, so that the use frequency of the load sensitive variable pump can be reduced, the service life of the load sensitive variable pump is prolonged, and the output power of the constant delivery pump is lower in the integral falling process, so that the system has certain energy-saving characteristic.
2. The two-position two-way normally open electro-hydraulic proportional valve, the two-position two-way normally closed electro-hydraulic proportional valve, the three-position four-way electro-hydraulic reversing valve and the shuttle valve are adopted to form the load port independent control valve group, and in the integral lifting process of the flat car, the inlet throttling speed regulation control and the outlet full-open control can be realized in the integral lifting process by changing the control logic and the input current of the control valve, so that the throttling loss is effectively reduced, the output power of the load sensitive variable pump is reduced, and the output power of an engine in the integral lifting process of the flat car is reduced; meanwhile, the functions of outlet throttling and speed regulating and inlet flow regeneration can be realized in the integral landing process, so that the gravitational potential energy of the flat car is effectively utilized, the work done by the gravitational potential energy is converted into the kinetic energy of the integral landing of the flat car, a sensitive variable pump is not required to be carried for supplying oil, and only a fixed pump is required for supplying oil, so that the output power of the engine in the integral landing process of the flat car is effectively reduced, and the energy conservation of the system is realized.
3. The invention adopts the combination form of the load sensitive variable pump, the fixed displacement pump and the load port independent control valve group, when the number of the suspension systems is increased due to the increase of the axes, the discharge capacity of the load sensitive variable pump does not need to be increased, and the number of the load port independent control valve groups is correspondingly increased according to the number of the suspension hydraulic cylinders, so that the power of the engine only needs to be correspondingly increased according to the requirements of other systems, and the engine is not influenced by the suspension systems, has greater universality, and has greater energy-saving property compared with the traditional hydraulic system.
Drawings
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
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 suspension diagram of a flat car according to 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 present invention
FIG. 4 is a hydraulic schematic diagram of a suspension system for a two-axis flatbed;
FIG. 5 is a hydraulic schematic diagram of a load port independent control valve bank;
FIG. 6 is a hydraulic schematic of a load sensitive variable displacement pump;
fig. 7 is a control flow diagram of a suspension system of a two-axis flatbed.
In the figure, 1, an oil tank, 2, a suspension hydraulic cylinder, 3, a load port independent control valve group, 30, a control valve block, 31, a first two-position two-way normally-open electro-hydraulic proportional valve, 32, a second two-position two-way 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-way 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 coupler, 10, a first overflow valve, 11, a second overflow valve, 12, 14. suspension 15, rotary support 16, suspension big arm 17, wheel axle support 18, suspension small arm 19 and wheel.
Detailed Description
The present invention will now be described in further detail with reference to the accompanying drawings. These drawings are simplified schematic views illustrating only the basic structure of the present invention in a schematic manner, and thus show only the constitution related to the present invention.
Fig. 1-6 show an embodiment of a hydraulic suspension system according to the present invention, in which fig. 1 shows an eight-axis flatbed, which includes a gooseneck 12, a flatbed body 13, and suspensions 14, the gooseneck 12 is located at the front section of the flatbed body 13 for connecting with a tractor, the suspensions 14 are bolted to the secondary beams of the flatbed body 13 and function as a support and connection shaft, and the suspensions 14 can be integrally lifted and lowered, and the number of suspensions 14 is 2 times the number of axes of the flatbed, for example, the eight-axis flatbed has 16 suspensions 14, and the two-axis flatbed has 4 suspensions 14.
As shown in fig. 2, the suspension 14 of the flatbed comprises a rotary support 15, a large suspension arm 16, a hydraulic suspension cylinder 2, a wheel axle bracket 17, a small suspension 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 large suspension arm 16 by a bolt, so that the whole suspension 14 can rotate relative to the flatbed 13, the other end of the large suspension arm 16 is connected with the small suspension arm 18 by an arm shaft of the suspension 14, a hinged point inside the large suspension arm 16 is connected with an ear end of a piston rod of the hydraulic suspension cylinder 2 by a pin shaft, an ear end of a cylinder body of the hydraulic suspension cylinder 2 is connected with a hinged point inside the small suspension arm 18 by a pin shaft, the whole lifting function of the flatbed can be realized by the simultaneous extending and retracting movement of the hydraulic suspension cylinders 2 of all the suspensions 14 of the flatbed, the small suspension arm 18 is connected with the wheel axle bracket 17, the wheels 19 play a role in supporting the vehicle body and walking.
The invention is suitable for suspension 14 systems of various axis flat cars, which are exemplified by a two-axis flat car, and the two-axis flat car is provided with four suspension hydraulic cylinders 2 and needs four independent control valve banks 3 for load ports to control respectively by combining the figures 3 and 4. The hydraulic suspension system for a two-axis plate shoe box comprises: the hydraulic control 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.
With reference 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 directional valve 33, a shuttle valve 34, and a two-position two-way normally closed electro-hydraulic proportional valve 35; a first oil inlet P is drilled on the control valve block 301A second oil inlet P2The first oil return port T1A second oil return port T2A first load sensing port L S1A second load sensing port L S2The first working oil port A11And a second working oil port B4(ii) a Oil outlet A of load-sensitive variable pump 43And an oil inlet P of a first two-position three-way electromagnetic directional valve 53A second working oil port B of the first two-position three-way electromagnetic directional valve 5 connected by a hydraulic pipeline1And an oil outlet A of the fixed displacement pump 74Hydraulic pipe connection, the first twoFirst working oil port A of position three-way electromagnetic directional valve 56With the first oil inlet P1And a second oil inlet P2Hydraulic pipeline connection; first oil inlet P1And a second oil inlet P2Through the internal flow passage of the control valve block 30 and the oil inlet P of the three-position four-way electro-hydraulic reversing valve 335Communicating; first working oil port A of three-position four-way electro-hydraulic reversing valve 337And an oil inlet P of the first two-position two-way normally-opened electro-hydraulic proportional valve 316Through the internal flow passages of the control valve block 30; oil outlet A of first two-position two-way normally-open electro-hydraulic proportional valve 318A first comparing port A of the shuttle valve 3415Oil inlet P of two-position two-way normally closed electro-hydraulic proportional valve 358Are communicated to the first working oil port A through the internal flow passage of the control valve block 3011(ii) a First working oil port A11Is communicated with a rodless cavity of the suspension hydraulic cylinder 2 through a hydraulic pipeline, and a rod cavity of the suspension hydraulic cylinder 2 is communicated with a second working oil port B through a hydraulic pipeline4Communicating; oil outlet A of two-position two-way normally-closed electro-hydraulic proportional valve 3510Oil outlet A of second two-position two-way normally-opened electro-hydraulic proportional valve 329Is communicated to the second working oil port B through an internal passage of the control valve block 304And an oil inlet P of a second two-position two-way normally-opened electro-hydraulic proportional valve 327A second working oil port B passing through the internal flow passage and the three-position four-way electro-hydraulic directional valve 333Communicating; a load sensitive port X of the load sensitive variable pump 4 and a first working oil port A of a second two-position three-way electromagnetic directional valve 65Oil return port T of hydraulic pipeline connection three-position four-way electro-hydraulic reversing valve 333Is communicated to the first oil return port T through the internal flow passage1And a second oil return port T2The load sensitive port X of the load sensitive variable pump 4 is communicated to the first load sensitive port L S through a hydraulic pipeline1First load sensing port L S1An outlet port C communicating with the shuttle valve 34 through an internal flow passage1(ii) a Second comparison port B of the shuttle valve 346Is communicated to the second load sensing port L S through an internal flow passage2(ii) a Oil suction port S of constant delivery pump 72Is connected to the oil tank 1 by hydraulic pipes.
Referring to fig. 5, a second two-position three-way electromagnetic directional valve 6 is connected to the load sensing portA load sensitive port X and a first working oil port A of the second two-position three-way electromagnetic directional valve 6 are arranged on a hydraulic pipeline between the X and the second two-position three-way electromagnetic directional valve 65Are communicated through a hydraulic pipeline; oil inlet P of second two-position three-way electromagnetic directional valve 64Through the hydraulic pipeline and the first load sensitive port L S1Communicating; oil outlet B of second two-position three-way electromagnetic directional valve 62Is connected to the oil tank 1 by hydraulic pipes.
Referring to fig. 3, 4 and 6, the load sensitive variable displacement pump 4 includes: the variable valve 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 is arranged on the sensitive variable valve block 401Oil outlet A3And an oil discharge port L1And a load sensitive port X, the variable pump 44 is fixedly arranged on the sensitive variable valve block 40, and an oil inlet P of the variable pump 4411And the oil suction opening S1Are communicated through an internal flow passage; oil outlet A of variable pump 4416Oil outlet A on the sensitive variable valve block 403A first working oil port A of a first two-position three-way hydraulic reversing valve 4118And a first pilot oil port C2A first working oil port A of a second two-position three-way hydraulic reversing valve 4219And a first pilot oil port C24Through an internal flow passage in the sensitive variable valve block 40; oil inlet P of power valve 4312Oil outlet A of third damping hole 4823And a second pilot oil port C of a second two-position three-way hydraulic reversing valve 425Is communicated to the load sensitive port X through an internal flow passage of the sensitive variable valve block 40 and an oil discharge port L of the variable pump 442Oil outlet A of power valve 4317A second working oil port B of a second two-position three-way hydraulic reversing valve 428The second pilot port C3 of the first two-position three-way hydraulic directional valve 41 is communicated to the oil discharge port L through the internal flow passage of the sensitive variable block1(ii) a Oil inlet P of first damping hole 4615And an oil inlet P of a second two-position three-way hydraulic electromagnetic valve14A second working oil port B of the first two-position three-way hydraulic reversing valve 417Oil outlet A of second damping hole 4720By passingThe internal flow passages of the sensitive variable valve block 40 are communicated; oil inlet P of second damping hole 4716An oil inlet P of a first two-position three-way hydraulic reversing valve 4113Oil inlet A of plunger cylinder 4521Internal flow passage communication through 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 regulator of the power valve 43 are mechanically connected such that the displacement amount of the piston rod changes in proportion to the displacement amount of the variable displacement pump 44 and the spring force of the power valve 43.
Referring to fig. 4, the hydraulic suspension system further 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 coupling 9; the input shaft of the fixed displacement pump 7 is connected with the tail end shaft hole of the load-sensitive variable displacement pump 4.
Referring to fig. 3 and 4, the oil outlet a of the load-sensitive variable displacement pump 43And an oil inlet P of a first two-position three-way electromagnetic directional valve 53The hydraulic pipeline is connected with an oil inlet P of a first overflow valve 109The oil outlet A of the first overflow valve 1013Is connected to the oil tank 1 by hydraulic pipes. A second working oil port B of the first two-position three-way electromagnetic directional valve 51And an oil outlet A of the constant delivery pump 74Are connected to an oil inlet P of a second overflow valve 11 through hydraulic pipelines10An oil outlet A of the second overflow valve 1114Is connected to the oil tank 1 by hydraulic pipes.
Referring to fig. 4, the second oil inlet P of the first load port independent control valve group 32The first oil return port T2A second load sensing port L S2A first oil inlet P of the valve group 3 is independently controlled with a second load port1The first oil return port T1A first load sensing port L S1The hydraulic oil inlet P2, the second load sensitive oil port L S2 and the second oil return port T2 of the fourth load port independent control valve group 3 are plugged by screws.
If increase the axis, only need according to hanging 2 numbers of pneumatic cylinder, the adaptation increase load mouth independent control valves 3 can, for example eight axis sixteen hang 14 load mouth independent hydraulic system, then hang 2 oil 16 of pneumatic cylinder, only need corresponding increase 16 load mouth independent control valves 3, both can realize the lift of each suspension 14 of independent control.
Referring to fig. 7, the lift control method of the hydraulic suspension system according to the embodiment of the present invention includes:
step 1: initializing, namely initializing a control system, checking whether input and output parameters of a controller, an operating handle, a sensor, a displacement sensor, a load port independent control valve group 3 and the like are normal, if not, executing downwards, and alarming; if normal, execution continues down.
Step 2: setting parameters: adjusting springs of the first overflow valve 10 and the second overflow valve 11, and setting overflow pressures of the first overflow valve 10 and the second overflow valve 11, wherein the overflow pressure of the first overflow valve 10 is the highest pressure of the system working of the suspension 14, and should be a high value, for example, set to be 28 MPa; the relief pressure of the second relief valve 11 is the oil supplementing pressure of the suspension 14 system, and should be a low value, for example, set to 2 MPa; other relevant parameters are set.
And step 3: and data acquisition, namely acquiring input signals of the operating handle.
And 4, 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 an operating handle, and if a lifting start signal is not read from the operating handle, stopping and not lifting; if a "lift start" signal is read in.
And 5: integral lift/fall mode determination: judging that the operation mode is in an integral lifting/falling mode through an integral lifting button and an integral falling button of the operation handle, and if an integral lifting signal is read from the operation handle, entering step 6.1; if the "global fall" signal is read from the operating handle, the process proceeds to step 6.2.
Step 6.1: in the integral lifting mode, after an input analog signal of integral lifting of the operating handle is 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 de-energized, the load sensitive variable displacement pump 4 supplies oil to the suspension 14 system, and the left electromagnets of the three-position four-way electro-hydraulic directional valves 33 of the four load port independent control valve groups 3 are simultaneously energized because of the three-position three-wayThe four-way electro-hydraulic directional control valve 33 is a large-flow control valve, only plays a role of reversing, but does not play a role of throttling and speed regulating, 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 de-energized, the electromagnets are converted into input current signals of the first two-position two-way normally-opened electro-hydraulic proportional valve 31 in an equal proportion according to an input analog signal value of 'integral rising' of the operating handle, so that an inlet throttling and speed regulating effect is achieved, meanwhile, the input current signal of the second two-position two-way normally-opened electro-hydraulic proportional valve 32 is set to be the maximum value, so that the valve port full opening of the second two-position two-way normally-opened electro-hydraulic proportional valve 32 is ensured, and an energy-saving control mode of 'inlet throttling and speed regulating and outlet full opening' is achieved1Or a second oil inlet P2And after entering through the left position of the three-position four-way electro-hydraulic reversing valve 33 and the throttling and speed regulation of the first two-position two-way normally-opened electro-hydraulic proportional valve 31, the hydraulic fluid enters into the rodless cavities of the four suspension hydraulic cylinders 2 simultaneously, so that piston rods of the four suspension hydraulic cylinders 2 are pushed to move in an extending mode, and the body of the flat car is pushed to move upwards. Meanwhile, the hydraulic oil flows out from the rod cavities of the four suspension hydraulic cylinders 2 and passes through the second fully-opened two-position two-way normally-opened electro-hydraulic proportional valve 32, the left position of the three-position four-way electro-hydraulic reversing valve 33 and the first oil return ports T of the four load port independent control valve groups 31Or a second oil return port T2Flows back to the oil tank 1; in the process of 'integral lifting', the rodless cavities of the four suspension hydraulic cylinders 2 are high-pressure, and the highest pressure of the rodless cavities of the four suspension hydraulic cylinders 2 is fed back to a load sensitive port X of the load sensitive variable pump 4 through a second two-position three-way electromagnetic directional 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, constant-power and pressure cut-off functions of the load sensitive variable pump 4 can be realized, and the load sensitive variable pump 4 adjusts the oil supply speed and the oil supply quantity according to the load change condition.
Step 6.2: integral landing mode: after obtaining the input analog signal of 'integral landing' of the operating handle, 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, and the constant delivery pump is used for supplying powerThe load port independent control valve group 3 is characterized in that oil is supplied to a suspension 14 system, a load sensitive port X of a load sensitive variable pump 4 is communicated with an oil tank 1, the load sensitive variable pump 4 works at the minimum pressure and is in an energy-saving mode, because a flat car body moves under the action of gravity in the integral landing process, rodless cavities of all suspension hydraulic cylinders 2 generate high pressure, right electromagnets of four three-position four-way electro-hydraulic reversing valves 33 of the load port independent control valve group 3 are simultaneously electrified, and the right electromagnets are converted into input current signals of a first two-position two-way normally-open electro-hydraulic proportional valve 31 in an equal proportion mode according to an input analog signal value of the integral landing of an operation handle, so that the outlet throttling and speed regulation functions are achieved. Meanwhile, the input current signal of the second two-position two-way normally-opened electro-hydraulic proportional valve 32 is set to be the maximum value, the electromagnets of the four two-position two-way normally-opened 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 the hydraulic oil flows out of the constant delivery pump 7 and flows out of the first oil inlets P of the four load port independent control valve groups 31Or a second oil inlet P2And after the oil enters the right position of the three-position four-way electro-hydraulic reversing valve 33 and passes through the second two-position two-way normally-opened electro-hydraulic proportional valve 32, oil is supplemented to the rod cavities of the four suspension hydraulic cylinders 2. Meanwhile, after the electromagnet of the first two-position two-way normally open electro-hydraulic proportional valve 31 receives a proportional current signal, hydraulic oil flowing out of the rodless cavities of the four suspension hydraulic cylinders 2 passes through the throttling and speed regulation of the first two-position two-way normally open electro-hydraulic proportional valve 31 and then passes through the right position of the three-position four-way electro-hydraulic reversing valve 33 and the first oil return ports T of the four load port independent control valve sets 31Or a second oil return port T2Flows back to the oil tank 1; in the process of 'integral landing', because under the action of gravity, 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 and speed-regulating function of the first two-position two-way normally-opened electro-hydraulic proportional valve 31, the other part of the high-pressure oil flows into rod cavities of the four suspension hydraulic cylinders 2 through the two-position two-way normally-closed electro-hydraulic proportional valve 35, and when the flow of the rod cavities of the four suspension hydraulic cylinders 2 is insufficient, the metering pump 7 only needs to supplement the oil to the rod cavities, so that 'outlet throttling and speed regulating and inlet flow regeneration' are realized, and the energy conservation.
Each suspension hydraulic cylinder is independently 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 merely illustrative of the present invention and are not intended to limit the present invention. Obvious variations or modifications which are within the spirit of the invention are possible within the scope of the invention.
Claims (10)
1. A hydraulic suspension system characterized by: the device 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) with the number corresponding to that of the suspension hydraulic cylinder (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); the load port independent control valve group (3) comprises a control valve block (30), a first two-position two-way normally-opened electro-hydraulic proportional valve (31), a second two-position two-way normally-opened 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); a first oil inlet P is drilled on the control valve block (30) respectively1A second oil inlet P2The first oil return port T1A second oil return port T2A first load sensing port L S1A second load sensing port L S2The first working oil port A11And a second working oil port B4(ii) a An oil outlet A of the load-sensitive variable pump (4)3And the oil inlet P of the first two-position three-way electromagnetic directional valve (5)3A hydraulic pipeline is connected, and a second working oil port B of the first two-position three-way electromagnetic directional valve (5)1And an oil outlet A of the fixed displacement pump (7)4A hydraulic pipeline is connected, and a first working oil port A of the first two-position three-way electromagnetic directional valve (5)6With said first oil inlet P1And the second oil inlet P2Hydraulic pipeline connection; the first oil inlet P1And the second oil inlet P2An oil inlet P of the three-position four-way electro-hydraulic reversing valve (33) is communicated with an internal flow passage of the control valve block (30)5Communicating; a first working oil port A of the three-position four-way electro-hydraulic reversing valve (33)7And the first two-position two-way normally open electric liquidAn oil inlet P of the proportional valve (31)6Communicating through an internal flow passage of the control valve block (30); an oil outlet A of a first two-position two-way normally-opened electro-hydraulic proportional valve (31)8A first comparing oil port A of the shuttle valve (34)15An oil inlet P of a two-position two-way normally closed electro-hydraulic proportional valve (35)8Are communicated to the first working oil port A through an internal flow passage of the control valve block (30)11(ii) a The first working oil port A11The rodless cavity of the suspension hydraulic cylinder (2) is communicated with the rodless cavity of the suspension hydraulic cylinder through a hydraulic pipeline, and the rod cavity of the suspension hydraulic cylinder (2) is communicated with the second working oil port B through a hydraulic pipeline4Communicating; an oil outlet A of the two-position two-way normally-closed electro-hydraulic proportional valve (35)10And an oil outlet A of a second two-position two-way normally-opened electro-hydraulic proportional valve (32)9Is communicated to the second working oil port B through an internal passage of the control valve block (30)4An oil inlet P of the second two-position two-way normally-opened electro-hydraulic proportional valve (32)7The three-position four-way electro-hydraulic reversing valve is communicated with a second working oil port B3 of the three-position four-way electro-hydraulic reversing valve (33) through an internal flow passage; the load sensitive port X of the load sensitive variable pump (4) and the first working oil port A of the second two-position three-way electromagnetic directional valve (6)5Hydraulic pipeline connection, oil return port T of the three-position four-way electro-hydraulic reversing valve (33)3Is communicated to the first oil return port T through an internal flow passage1And said second oil return port T2The load sensitive port X of the load sensitive variable pump (4) is communicated to the first load sensitive port L S through a hydraulic pipeline1The first load sensing port L S1An oil outlet C communicated to the shuttle valve (34) through an internal flow passage1(ii) a A second comparison oil port B of the shuttle valve (34)6Is communicated to the second load sensing port L S through an internal flow passage2(ii) a An oil suction port S of the fixed displacement pump (7)2Is connected to the oil tank (1) through a hydraulic pipeline.
2. A hydraulic suspension system as defined in 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 XA first working oil port A of the second two-position three-way electromagnetic directional valve (6)5Are communicated through a hydraulic pipeline; an oil inlet P of the second two-position three-way electromagnetic directional valve (6)4Through hydraulic pipeline and the first load sensing port L S1Communicating; an oil outlet B of the second two-position three-way electromagnetic directional valve (6)2Is connected to the oil tank (1) by a hydraulic pipeline.
3. A hydraulic suspension system as defined in claim 1 wherein: the load-sensitive variable displacement pump (4) comprises: the variable valve 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 is arranged on the sensitive variable valve block (40)1Oil outlet A3And an oil discharge port L1And a load sensitive port X, the variable pump (44) is fixedly arranged on the sensitive variable valve block (40), and an oil inlet P of the variable pump (44)11And the oil suction opening S1Are communicated through an internal flow passage; an oil outlet A of the variable pump (44)16An oil outlet A on the sensitive variable valve block (40)3A first working oil port A of a first two-position three-way hydraulic reversing valve (41)18And a first pilot oil port C2A first working oil port A of a second two-position three-way hydraulic reversing valve (42)19And a first pilot oil port C24Communicating through an internal flow passage on the sensitive variable valve block (40); an oil inlet P of the power valve (43)12An oil outlet A of the third damping hole (48)23A second pilot oil port C of a second two-position three-way hydraulic reversing valve (42)5Is communicated to the load sensitive port X through an internal flow passage of the sensitive variable valve block (40) and an oil discharge port L of the variable pump (44)2Oil outlet A of power valve (43)17A second working oil port B of a second two-position three-way hydraulic reversing valve (42)8A second pilot oil port C3 of the first two-position three-way hydraulic reversing valve (41) is communicated to the oil discharge port L through an internal flow passage of the sensitive variable block1(ii) a An oil inlet of the first damping hole (46)P15And an oil inlet P of a second two-position three-way hydraulic electromagnetic valve14A second working oil port B of the first two-position three-way hydraulic reversing valve (41)7And an oil outlet A of the second damping hole (47)20Communicating through an internal flow passage of a sensitive variable valve block (40); an oil inlet P of the second damping hole (47)16An oil inlet P of a first two-position three-way hydraulic reversing valve (41)13Oil inlet A of plunger cylinder (45)21Communicating through an internal flow passage of a sensitive variable valve block (40); and a piston rod of the plunger cylinder (45), a variable mechanism pushing rod of the variable pump (44) and a spring regulator of the power valve (43) are connected through a mechanical structure, so that the displacement of the piston rod is changed in a proportional relation with the displacement of the variable pump (44) and the spring force of the power valve (43).
4. A hydraulic suspension system as claimed in claim 3, wherein: the output shaft of the engine (8) is connected with the input shaft of the load-sensitive variable pump (4) through a coupling (9); the input shaft of the constant delivery pump (7) is connected with the tail end shaft hole of the load sensitive variable pump (4).
5. A hydraulic suspension system as claimed in claim 3, wherein: an oil outlet A of the load-sensitive variable pump (4)3And an oil inlet P of the first two-position three-way electromagnetic directional valve (5)3An oil inlet P of a first overflow valve (10) is connected with the hydraulic pipeline9An oil outlet A of the first overflow valve (10)13Is connected to the oil tank (1) through a hydraulic pipeline.
6. The hydraulic suspension system according to any one of claims 3 to 5, wherein: a second working oil port B of the first two-position three-way electromagnetic directional valve (5)1And an oil outlet A of the constant delivery pump (7)4Are connected to an oil inlet P of a second overflow valve (11) through hydraulic pipelines10An oil outlet A of the second overflow valve (11)14Is connected to the oil tank (1) by a hydraulic pipeline.
7. A hydraulic suspension system as defined in claim 1 wherein: the number of the suspension hydraulic cylinders (2) is four.
8. A hydraulic suspension system as defined in claim 1 wherein: and two hydraulic suspension systems are arranged on each axis of the arranged flat car.
9. A lifting control method of a hydraulic suspension system is characterized by comprising the following steps:
the ascending control method comprises the following steps: electromagnets of a first two-position three-way electromagnetic reversing valve (5) and a second two-position three-way electromagnetic reversing valve (6) are simultaneously de-energized, a load sensitive variable displacement pump (4) supplies oil to a suspension (14) system, a left electromagnet of a three-position four-way electro-hydraulic reversing valve (33) is simultaneously energized, an electromagnet of a two-position two-way normally closed electro-hydraulic proportional valve (35) is simultaneously de-energized, a current signal is input to a first two-position two-way normally open electro-hydraulic proportional valve (31) to throttle and regulate the speed of an inlet, meanwhile, an input current signal of a second two-position two-way normally open electro-hydraulic proportional valve (32) is set to be the maximum value, and the full port of a valve port of the second two-position two-way normally; hydraulic oil inlet P1Or P2Entering, through the left position of three-position four-way electro-hydraulic directional valve (33), after the throttle speed regulation through first two-position two-way normally-opened electro-hydraulic proportional valve (31), entering the rodless cavity of suspension hydraulic cylinder (2), pushing the piston rod of suspension hydraulic cylinder (2) to make stretching motion, and then pushing the flat car body to move upwards, and simultaneously, hydraulic oil flows out from the rod cavity of four suspension hydraulic cylinders (2), through second two-position two-way normally-opened electro-hydraulic proportional valve (32) which is fully opened, the left position of three-position four-way electro-hydraulic directional valve (33), first oil return port T1Or a second oil return port T2Flows back to the oil tank (1); the pressure between a rod cavity and a 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 directional valve (6), so that the load sensitive variable pump (4) adjusts the oil supply speed and the oil supply amount according to the load change condition;
the descending control method comprises the following steps: 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 obtainedThe constant delivery pump (7) supplies oil to the suspension system (14), a load sensitive port X of the load sensitive variable pump (4) is communicated with the oil tank (1) through a second two-position three-way electromagnetic directional valve (6), the load sensitive variable pump (4) works at the minimum pressure and is in an energy-saving mode, under the action of gravity of a body of the flat car, a rodless cavity of a suspension hydraulic cylinder (2) generates high pressure, a right electromagnet of a three-position four-way electro-hydraulic reversing valve (33) is electrified simultaneously, a first two-position two-normally-opened electro-hydraulic proportional valve (31) regulates speed according to an input current signal, therefore, the effect of outlet throttling and speed regulation is achieved, meanwhile, the input current signal of the second two-position two-way normally-opened electro-hydraulic proportional valve (32) is set to be the maximum value, the maximum current value is simultaneously input into the electromagnet of the two-position two-way normally-closed electro-hydraulic proportional valve (35), and the flow regeneration mode is started; the hydraulic oil passes through the right position of the three-position four-way electro-hydraulic directional valve (33), is supplemented to a rod cavity of the suspension hydraulic cylinder (2) after passing through the second two-position two-way normally-open electro-hydraulic proportional valve (32), and simultaneously flows out of a rodless cavity of the suspension hydraulic cylinder (2) after an electromagnet of the first two-position two-way normally-open electro-hydraulic proportional valve (31) receives a proportional current signal, and then passes through the right position of the three-position four-way electro-hydraulic directional valve (33) and a first oil return port T after the throttling and the speed regulation of the first two-position two-way normally-open electro-hydraulic proportional valve (31), and then passes through the right1Or a second oil return port T2Flows back to the oil tank (1); one part of high-pressure oil generated by the rodless cavity flows back to the oil tank (1) under the throttling and speed-regulating action of the first two-position two-way normally-opened electro-hydraulic proportional valve (31), the other part of high-pressure oil 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 constant delivery pump (7) supplies oil to the rod cavity, so that the outlet throttling and speed-regulating function and the inlet flow regeneration function are realized.
10. The utility model provides a multiaxis flatbed which characterized in that: the hydraulic suspension system 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 (3) connected with a load sensitive variable pump (4).
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111927836A (en) * | 2020-09-09 | 2020-11-13 | 湖南三一中型起重机械有限公司 | Hydraulic cylinder control device, variable amplitude hydraulic system and crane |
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| CN111483284B (en) | 2024-05-03 |
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