CN201792744U - Single-pump dual-motor driving engineering vehicle and hydraulic system and control device thereof - Google Patents
Single-pump dual-motor driving engineering vehicle and hydraulic system and control device thereof Download PDFInfo
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- CN201792744U CN201792744U CN2010205109968U CN201020510996U CN201792744U CN 201792744 U CN201792744 U CN 201792744U CN 2010205109968 U CN2010205109968 U CN 2010205109968U CN 201020510996 U CN201020510996 U CN 201020510996U CN 201792744 U CN201792744 U CN 201792744U
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Abstract
The utility model provides a control device of a hydraulic system of a single-pump dual-motor driving engineering vehicle, which comprises two solenoid valves, a flow distributing and collecting valve, a corner sensor, an electric proportional throttle valve and a controller, wherein the two solenoid valves are respectively arranged in a first oil inlet oil line and a second oil inlet oil line; the inlet of the flow distributing and collecting valve is connected with the outlet of a hydraulic pump, the first outlet of the flow distributing and collecting valve is connected into the first oil inlet oil line, and the second outlet is connected into the second oil inlet oil line; the corner sensor is arranged on the engineering vehicle to detect the corner of the engineering vehicle and output corresponding electrical corner signals; the first end of the electric proportional throttle valve is connected into the first oil inlet oil line, and the second end of the electric proportional throttle valve is connected into the second oil inlet oil line; and the controller is connected with the electric proportional throttle valve, receives the electrical corner signals output by the corner sensor, and outputs electric proportional throttle valve control signals which control the size of a conduction opening of the electric proportional throttle valve according to the electrical corner signals. The control device can prevent the vehicle from slipping unilaterally, and simultaneously prevents the phenomena of hydraulic system overflow and ultraslow running of the vehicle.
Description
Technical field
The utility model relates to the hydrostatic drive field, more specifically, relates to the control setup that a kind of single pump double motor drives engineering truck and hydraulic efficiency pressure system and hydraulic efficiency pressure system.
Background technology
Hydrostatic drive is to carry out the type of drive of transfer of energy with liquid as working medium, has the good characteristic of controlling, and has inborn preceence at aspects such as low speed high torque transmission, frequent start-stop commutation, dead slow speed action and crawl operations.At present, along with the development of domestic and international hydraulic technique, the performance of Hydraulic Elements improves constantly, and price constantly reduces, and hydrostatic drive and control technology have obtained to use widely in construction machinery and equipment.
The power transmission route of full hydraulic drive engineering truck is: driving engine-coupler-Hydraulic Pump-HM Hydraulic Motor-deceleration tandem-driving bogie-wheel.Under PLC or nonshared control unit control, engine operation speed and output torque can be according to the variation automatic compensations of external load, its parameter of rational Match, pursue dynamic property during promptly big the load, economic pursuit when gently (sky) loads, thereby make full use of the power of driving engine, the maximal efficiency of performance machine.
At present, realize that as two HM Hydraulic Motor in parallel that drive power source is arranged in the fuselage both sides type of drive of walking has application widely with single pump on construction machinery and equipment.The fluid of Hydraulic Pump output freely is assigned to two HM Hydraulic Motor place oil circuits, the size of distribution oil mass depends on the load size of motor, be subjected to unbalance loading or road adherence hour at equipment, as not taking non-skid feature, be prone to monolateral skidding, the oil circuit oil pressure reduction of motor one side that load just is less causes delivery quality to infeed to this side oil circuit in a large number, and then cause this side motor rotary speed to improve, and the opposite side motor can't normal operation because delivery quality is not enough, produces the phenomenon of whole engineering truck stagnation.This not only influences the service life of Hydraulic Elements, and the tractive force of complete machine is descended, and power-handling capability reduces.
Both at home and abroad at this problem, common have a following way:
1, at the two HM Hydraulic Motor oil circuits big flow inserted valve of respectively connecting, when a certain drive wheel trackslips, control system is closed the wheel working connection inserted valve that trackslips, fluid can only enter the motor that trackslips by the throttling damping oil circuit of parallel connection, force the power fluid major part to be assigned to the motor that do not trackslip like this, system works pressure rebulids, the motor torque of not trackslipping strengthens, overcoming resistance rotates, but the also hour alternately skidding of appearance easily of dypass face adhesive ability of ought not trackslipping, and the power-handling capability of the motor that trackslips can not get bringing into play fully.
2, adopt automatically controlled mode, when a certain drive wheel trackslipped, control system made the motor output torque reduce with certain algorithm reduce to trackslip discharge capacity of motor, descends until the side rotating speed that skids, and system pressure rebulids.There are the problems referred to above equally in this method, and the motor that trackslips can cause the rotating speed of motor to increase when the capacity reduction process, thereby the phenomenon of motor hypervelocity may occur, i.e. alleged hypervelocity " driving " phenomenon usually.
3, on hydraulic circuit, set up branch/combiner valve, judge whether monolateral skidding by detecting two motor rotary speed signals and equipment turn sign, if then two motor oil circuits are switched to the flow distributing and collecting state, make oil circuit through flow divider-combiner, this valve forces single-candidate to be distributed to two CD-ROM drive motor flows; Detect two motor place oil circuit pressure signals afterwards, if pressure reduction then switches back oil circuit free distribution state less than setting value.Consider the factor of aspects such as cost; the switching of oil circuit state also can not adopted automatic control mode; such as chaufeur can be the flow distributing and collecting state according to road surface situation manual switchover; but no matter which kind of mode of employing; when under the flow distributing and collecting state, turning to; the both sides motor can't form speed difference and then can not normal direction of rotation; and along with inboard motor pressure sharply raises; the defective of flow divider-combiner itself causes its automatic pressure compensation; turn down the valve port of outside motor oil circuit; further will make system's overflow (being the phenomenon that hydraulic oil returns fuel tank), it is slow unusually that the equipment moving velocity of making becomes.
The utility model content
Technical problem to be solved in the utility model provides the control setup that a kind of single pump double motor drives engineering truck and hydraulic efficiency pressure system and hydraulic efficiency pressure system; can prevent that single pump double motor from driving that engineering truck is monolateral to skid, and can prevent simultaneously vehicle can not normal direction of rotation for avoiding monolateral skidding or when turning single pump double motor of hydraulic efficiency pressure system overflow, the unusual slow phenomenon of vehicle ' drive the control setup of hydraulic system of engineering vehicle.
According to an aspect of the present utility model, provide a kind of single pump double motor to drive the control setup of hydraulic system of engineering vehicle, comprise: first electromagnetic valve and second electromagnetic valve are arranged in the first oil-feed oil circuit between the Hydraulic Pump and first HM Hydraulic Motor and in the second oil-feed oil circuit between the Hydraulic Pump and second HM Hydraulic Motor; Flow divider-combiner, its import connects hydraulic pressure delivery side of pump, and its first outlet is connected in the first oil-feed oil circuit between first electromagnetic valve and first HM Hydraulic Motor, and second outlet is connected in the second oil-feed oil circuit between second electromagnetic valve and second HM Hydraulic Motor; Rotary angle transmitter is installed on the engineering truck, detects the corner and the output corner electric signal correspondingly of engineering truck; Electricity proportional throttle valve, its first end are connected in the first oil-feed oil circuit between first electromagnetic valve and first HM Hydraulic Motor, and second end is connected in the second oil-feed oil circuit between second electromagnetic valve and second HM Hydraulic Motor; Controller connects electric proportional throttle valve, and receives the corner electric signal of rotary angle transmitter output, and the electric proportional throttle valve control signal of the lead-through opening size of electric proportional throttle valve is controlled in output according to the corner electric signal.
Further, also comprise: first tachogen and second tachogen, be installed in respectively on first HM Hydraulic Motor and second HM Hydraulic Motor, detect the rotating speed of first HM Hydraulic Motor and second HM Hydraulic Motor and to the controller output first rotating speed electric signal and the second rotating speed electric signal correspondingly; First pressure sensor and second pressure sensor, be installed in respectively on the first oil-feed oil circuit and the second oil-feed oil circuit, detect on the first oil-feed oil circuit and the second oil-feed oil circuit pressure and to the controller output first oil pressure electric signal and the second oil pressure electric signal correspondingly, wherein, controller is controlled the opening and closing of first electromagnetic valve and second electromagnetic valve according to rotating speed electric signal and oil pressure electric signal, and opens the control to electric proportional throttle valve when closing electromagnetic valve.
Further, also comprise: manual triggers portion, be connected to controller, provide the manual triggers signal to controller; Wherein, controller is according to the opening and closing of manual triggers signal control first electromagnetic valve and second electromagnetic valve, and opens the control to electric proportional throttle valve when closing electromagnetic valve.
Further, electric proportional throttle valve is arranged in the downstream of Hydraulic Pump to the oil feeding line flow divider-combiner of HM Hydraulic Motor.
Further, rotary angle transmitter is for turning to potentiometer.
Further, first electromagnetic valve and second electromagnetic valve are Solenoid ball valve or electromagnetic switch valve.
Further, flow divider-combiner is synchronous branch combiner valve.
According to another aspect of the present utility model, provide a kind of single pump double motor to drive the hydraulic efficiency pressure system of engineering truck, comprise above-mentioned any control setup.
According to another aspect of the present utility model, the engineering truck that provides a kind of single pump double motor to drive comprises above-mentioned hydraulic efficiency pressure system.
The utlity model has following beneficial effect:
1. because the existence of first electromagnetic valve and second electromagnetic valve and flow divider-combiner, make when the conducting of controller control electromagnetic valve, hydraulic efficiency pressure system is in nature branch stream mode, and in that vehicle is monolateral when skidding, the may command closed electromagnetic valve, this moment, hydraulic efficiency pressure system entered pressure flow distributing and collecting state by the effect of flow divider-combiner, thereby regulated the fuel feeding oil mass of first HM Hydraulic Motor and second HM Hydraulic Motor, the rotating speed of both sides motor is reached unanimity, thereby can solve the monolateral problem of slip of vehicle; Forcing the flow distributing and collecting state, when monolateral skidding disappeared, the may command electromagnetic valve reopened, and this moment, hydraulic efficiency pressure system was got back to nature branch stream mode again.As mentioned above, this control setup can be eliminated the monolateral skidding of vehicle.In addition; when hydraulic efficiency pressure system is in pressure flow distributing and collecting state; because the existence of electric proportional throttle valve; make at Ackermann steer angle; can control the lead-through opening size of electric proportional throttle valve by controller in real time according to the detected steering angle signal of rotary angle transmitter; and that the motor that makes both sides reaches best speed is poor; and avoided inboard motor pressure sharply to raise simultaneously; thereby avoided the hydraulic efficiency pressure system overflow; the moving velocity phenomenon unusually slowly that becomes; alleviated the correction intensity of chaufeur, realized that vehicle can turn to High Performance under the pressure flow distributing and collecting state.
Since this control setup can also comprise first tachogen and second tachogen that is installed in respectively on first HM Hydraulic Motor and second HM Hydraulic Motor and be installed in the first oil-feed oil circuit respectively and the second oil-feed oil circuit in first pressure sensor and second pressure sensor, make difference that two tachogens in the system detect speed greater than in the controller during preset value, can make hydraulic efficiency pressure system enter the flow distributing and collecting state of forcing by controller automatic guidance closed electromagnetic valve by the effect of flow divider-combiner.And force in the flow distributing and collecting state, when the difference of the pressure of two the detected both sides of pressure sensor oil circuits less than controller in during preset value, reopen by controller automatic guidance electromagnetic valve, this moment, hydraulic efficiency pressure system was got back to nature branch stream mode again.Like this, just make hydraulic efficiency pressure system has been realized automatic guidance, alleviated work load for drivers, increased control accuracy.
Description of drawings
Accompanying drawing is used to provide further understanding of the present utility model, constitutes the application's a part, and illustrative examples of the present utility model and explanation thereof are used to explain the utility model, do not constitute improper qualification of the present utility model.In the accompanying drawings:
Fig. 1 shows the schematic block diagram that drives hydraulic system of engineering vehicle according to single pump double motor of the present utility model.
The specific embodiment
Below with reference to the accompanying drawings and in conjunction with the embodiments, describe the utility model in detail.
As shown in Figure 1, the hydraulic efficiency pressure system that drives engineering truck according to single pump double motor of the present utility model comprise first HM Hydraulic Motor 21 that is positioned at the vehicle both sides and second HM Hydraulic Motor 22, to the Hydraulic Pump 1 of these two motor fuel feeding and the control setup 3 that the fuel feeding process is controlled.Wherein, Hydraulic Pump 1 by the first oil-feed oil circuit and the second oil-feed oil circuit to first HM Hydraulic Motor 21 and second HM Hydraulic Motor, 22 fuel feeding, that is to say, the first oil-feed oil circuit is connected between the Hydraulic Pump 1 and first HM Hydraulic Motor 21, and the second oil-feed oil circuit is connected between the Hydraulic Pump 1 and second HM Hydraulic Motor 22.
As can be seen from Figure 1, control setup 3 comprises and is arranged in first electromagnetic valve 33 in the first oil-feed oil circuit and is arranged in second electromagnetic valve 34 in the second oil-feed oil circuit, is arranged in flow divider-combiner 35 and electric proportional throttle valve 36 in the oil circuit.In addition, control setup 3 also comprises rotary angle transmitter 31 and the controller 32 that is installed on the engineering truck, its middle controller 32 connects rotary angle transmitters 31 receiving the electric signal that it sends, and connects first electromagnetic valve 33 and second electromagnetic valve 34 and electric proportional throttle valve 36 to send control signal to these valves.
Particularly, the import of flow divider-combiner 35 connects the outlet of Hydraulic Pump 1, first outlet of flow divider-combiner 35 is connected in the first oil-feed oil circuit between first electromagnetic valve 33 and first HM Hydraulic Motor 21, second outlet is connected in the second oil-feed oil circuit between second electromagnetic valve 34 and second HM Hydraulic Motor 22, and it can play the effect of forcing single-candidate to be distributed to the delivery quality that is supplied to two CD-ROM drive motor.First end of electricity proportional throttle valve 36 is connected in the first oil-feed oil circuit between first electromagnetic valve 33 and first HM Hydraulic Motor 21, second end is connected in the second oil-feed oil circuit between second electromagnetic valve 34 and second HM Hydraulic Motor 22, its lead-through opening can be realized the mutual output of fuel feeding between two HM Hydraulic Motor, and this lead-through opening size can be controlled and change.Rotary angle transmitter 31 is used to detect the angle of turn and the output corner electric signal correspondingly of engineering truck, and to controller 32, preferably, rotary angle transmitter 31 is simple and easy to realize for turning to potentiometer as voltage signal.Controller 32 receives the corner electric signal of rotary angle transmitter 31 outputs, as voltage signal, electric proportional throttle valve control signal according to the electric proportional throttle valve 36 lead-through opening sizes of corner electric signal output control, make the lead-through opening size of electric proportional throttle valve 36 along with the increase of corner electric signal/reduce and increase/reduce, thereby can control the defeated oil-out flow size of the HM Hydraulic Motor of a side to the HM Hydraulic Motor of opposite side.
When engineering truck is worked, when vehicle is normally advanced, first electromagnetic valve 33 controlled by controller and second electromagnetic valve 34 is opened (conducting), this moment, hydraulic efficiency pressure system was in nature branch stream mode, at this moment, Hydraulic Pump 1 depends on pressure in the first oil-feed oil circuit and the pressure in the second oil-feed oil circuit to the delivery quality of first HM Hydraulic Motor 21 and second HM Hydraulic Motor 22, and pressure hour delivery quality increases.When since traction less, vehicle unbalance-loading causes the oil circuit pressure of a side to diminish, Hydraulic Pump 1 increases to one-sided delivery quality, the rotating speed that causes one-sided HM Hydraulic Motor becomes big and opposite side when diminishing, two closed electromagnetic valves of controller 32 controls, at this moment, from Fig. 1, be appreciated that, hydraulic efficiency pressure system enters the pressure flow distributing and collecting state that single-candidate is distributed by the effect of flow divider-combiner 35, thereby the fuel feeding oil mass to first HM Hydraulic Motor 21 and second HM Hydraulic Motor 22 reaches unanimity, the rotating speed of the motor of both sides reaches unanimity, and has avoided that the rotating speed of one-sided motor is excessive to cause monolateral phenomenon of skidding.Be appreciated that, forcing the flow distributing and collecting state, when monolateral skidding disappears, just the first oil-feed oil circuit neutralizes oil pressure pressure reduction in the second oil-feed oil circuit when returning to less than preset value, controller 32 control first electromagnetic valves 33 and second electromagnetic valve 34 reopen, and this moment, hydraulic efficiency pressure system was got back to nature branch stream mode again.
Wherein, when hydraulic efficiency pressure system is in pressure flow distributing and collecting state, controller 32 is according to the corner electric signal of rotary angle transmitter 31 outputs, regulate the lead-through opening size of electric proportional throttle valve 36 in the present embodiment for the size of voltage signal, and then the flow size of control vehicle inboard HM Hydraulic Motor HM Hydraulic Motor output laterally when turning, thereby it is poor to make the both sides motor form best speed, the corresponding oil circuit pressure of inboard HM Hydraulic Motor sharply raises when simultaneously also having avoided turning to, thereby hydraulic efficiency pressure system overflow, the slack-off phenomenon of car speed can not occur turning to the time.When vehicle no longer turned to, the lead-through opening of the electric proportional throttle valve 36 of controller 32 controls was closed, and made hydraulic efficiency pressure system recover the oil mass single-candidate of the first oil-feed oil circuit and the second oil-feed oil circuit is distributed, and like this, vehicle promptly keeps straight-line travelling.
Preferably, in the present embodiment, as can be seen from Figure 1 electric proportional throttle valve 36 is arranged in the downstream of Hydraulic Pump 1 to the oil feeding line flow divider-combiner 35 of HM Hydraulic Motor, can regulate between the oil circuit of motor of both sides the oil mass of output mutually so better.
Preferably, control setup 3 can also comprise first tachogen and second tachogen and first pressure sensor and the second pressure sensor (not shown).Wherein, first tachogen and second tachogen are installed in respectively on first HM Hydraulic Motor 21 and second HM Hydraulic Motor 22, detect the rotating speed of first HM Hydraulic Motor 21 and second HM Hydraulic Motor 22 and to controller 32 output and the corresponding first rotating speed electric signal of rotating speed and the second rotating speed electric signal; First pressure sensor and second pressure sensor are installed in respectively on the first oil-feed oil circuit and the second oil-feed oil circuit, detect on the first oil-feed oil circuit and the second oil-feed oil circuit pressure and to controller 32 output and the corresponding first oil pressure electric signal of pressure and the second oil pressure electric signal.
Like this, be appreciated that, when hydraulic efficiency pressure system is in nature branch stream mode, controller 32 obtains the first rotating speed electric signal and the second rotating speed electric signal in real time, that is obtain the rotating speed of first HM Hydraulic Motor 21 and second HM Hydraulic Motor 22, when the difference of the rotating speed of first HM Hydraulic Motor 21 and second HM Hydraulic Motor 22 during greater than the preset value in the controller 32, two closed electromagnetic valves of controller 32 automatic guidances and make the effect of hydraulic efficiency pressure system by flow divider-combiner 35 enter the flow distributing and collecting state of forcing, and open the control to electric proportional throttle valve 36 as indicated above.When hydraulic efficiency pressure system was in pressure flow distributing and collecting state, controller 32 obtained the first oil pressure electric signal and the second oil pressure electric signal in real time, that is obtains the pressure in the first oil-feed oil circuit and the second oil-feed oil circuit.When the difference of pressure in the two-way oil circuit during less than the preset value in the controller 32, two electromagnetic valves of controller 32 automatic guidances reopen and make hydraulic efficiency pressure system get back to nature branch stream mode, and close electric proportional throttle valve 36 simultaneously.Like this, just make hydraulic efficiency pressure system has been realized automatic guidance, alleviated work load for drivers, increased control accuracy.
Certainly, preferably, the conversion of branch stream mode and pressure flow distributing and collecting state also can be undertaken by M/C naturally.Particularly, a manual triggers portion (not shown) is set in control setup 3, as button etc., this manual triggers portion is connected to controller 32, and being used for provides the manual triggers signal to controller 32.
Particularly, when the hydraulic efficiency pressure system of engineering truck is in nature branch stream mode, chaufeur is according to the rotating speed of road surface situation, observation both sides motor, when judgement will or monolateral skidding occur, by pressing manual triggers portion to controller 32 output manual triggers signals, controller 32 makes hydraulic efficiency pressure system enter pressure flow distributing and collecting state by the effect of flow divider-combiner 35 according to two closed electromagnetic valves of this manual triggers signal control, and opens the control to electric proportional throttle valve 36 as indicated above.When hydraulic efficiency pressure system is in pressure flow distributing and collecting state, the driver's observation judgement can be switched back when dividing stream mode naturally, portion exports the manual triggers signals to controller 32 by the operation manual triggers, controller 32 reopens according to two electromagnetic valves of this manual triggers signal control and makes hydraulic efficiency pressure system get back to nature branch stream mode, and closes electric proportional throttle valve 36 simultaneously.This kind structure of the control setup 3 of hydraulic efficiency pressure system is switched nature branch stream mode and is forced the flow distributing and collecting state by manual control, has saved tachogen and pressure sensor, has simplified the control program of controller 32, simple economy.
Preferably, above-mentioned first electromagnetic valve 33 and second electromagnetic valve 34 are Solenoid ball valve, and the speed of response of its valve body is very fast, or electromagnetic switch valve, and it is stronger that the oil rub resistance of its valve body dyes ability.
Preferably, this flow divider-combiner 35 is synchronous branch combiner valve, realizes that the oil circuit single-candidate of both sides is distributed.
In addition; the utility model also provides a kind of single pump double motor to drive the hydraulic efficiency pressure system of engineering truck; it comprises above-described any control setup 3; thereby can prevent that single pump double motor from driving that engineering truck is monolateral to skid, and can prevent simultaneously that vehicle is for avoiding monolateral the skidding can not normal direction of rotation or hydraulic efficiency pressure system overflow, the unusual slow phenomenon of vehicle ' when turning.
In addition; the engineering truck that the utility model also provides a kind of single pump double motor to drive; it comprises hydraulic efficiency pressure system mentioned above; thereby can prevent monolateral skidding; and can prevent from simultaneously to alleviate the correction working strength of chaufeur for avoiding monolateral the skidding can not normal direction of rotation or hydraulic efficiency pressure system overflow, the unusual slow phenomenon of vehicle ' when turning.
The above is a preferred embodiment of the present utility model only, is not limited to the utility model, and for a person skilled in the art, the utility model can have various changes and variation.All within spirit of the present utility model and principle, any modification of being done, be equal to replacement, improvement etc., all should be included within the protection domain of the present utility model.
Claims (10)
1. a single pump double motor drives the control setup (3) of hydraulic system of engineering vehicle, comprising:
First electromagnetic valve (33) and second electromagnetic valve (34) are arranged in the first oil-feed oil circuit between Hydraulic Pump (1) and first HM Hydraulic Motor (21) and in the second oil-feed oil circuit between Hydraulic Pump (1) and second HM Hydraulic Motor (22);
Flow divider-combiner (35), its import connects the outlet of described Hydraulic Pump (1), its first outlet is connected between first electromagnetic valve (33) described in the described first oil-feed oil circuit and first HM Hydraulic Motor (21), and second exports and to be connected in the described second oil-feed oil circuit between second electromagnetic valve (34) and second HM Hydraulic Motor (22);
It is characterized in that described control setup (3) also comprises:
Rotary angle transmitter (31) is installed on the described engineering truck, detects the corner and the output corner electric signal correspondingly of described engineering truck;
Electricity proportional throttle valve (36), its first end is connected between first electromagnetic valve (33) described in the described first oil-feed oil circuit and first HM Hydraulic Motor (21), and second end is connected between second electromagnetic valve (34) described in the described second oil-feed oil circuit and second HM Hydraulic Motor (22);
Controller (32), connect described electric proportional throttle valve (36), and receive the corner electric signal that described rotary angle transmitter (31) is exported, control the electric proportional throttle valve control signal of the lead-through opening size of described electric proportional throttle valve (36) according to described corner electric signal output.
2. control setup according to claim 1 (3) is characterized in that, also comprises:
First tachogen and second tachogen, be installed in respectively on first HM Hydraulic Motor (21) and second HM Hydraulic Motor (22), detect the rotating speed of described first HM Hydraulic Motor (21) and second HM Hydraulic Motor (22) and to described controller (32) the output first rotating speed electric signal and the second rotating speed electric signal correspondingly;
First pressure sensor and second pressure sensor, be installed in respectively on the described first oil-feed oil circuit and the second oil-feed oil circuit, detect on the described first oil-feed oil circuit and the second oil-feed oil circuit pressure and to described controller (32) the output first oil pressure electric signal and the second oil pressure electric signal correspondingly
Wherein, described controller (32) is controlled the opening and closing of described first electromagnetic valve (33) and second electromagnetic valve (34) according to described rotating speed electric signal and described oil pressure electric signal, and opens the control to described electric proportional throttle valve (36) when closing described first electromagnetic valve (33) and second electromagnetic valve (34).
3. control setup according to claim 1 (3) is characterized in that, also comprises:
Manual triggers portion is connected to described controller (32), provides the manual triggers signal to described controller (32);
Wherein, described controller (32) is according to the opening and closing of described first electromagnetic valve of described manual triggers signal control (33) and second electromagnetic valve (34), and opens the control to described electric proportional throttle valve (36) when closing described first electromagnetic valve (33) and second electromagnetic valve (34).
4. control setup according to claim 1 (3) is characterized in that, described electric proportional throttle valve (36) is positioned at the downstream of described Hydraulic Pump (1) to flow divider-combiner (35) described in the oil feeding line of described HM Hydraulic Motor.
5. according to claim 1,2,3 or 4 described control setups (3), it is characterized in that described rotary angle transmitter (31) is for turning to potentiometer.
6. according to claim 1,2 or 3 described control setups (3), it is characterized in that described first electromagnetic valve (33) and second electromagnetic valve (34) are Solenoid ball valve or electromagnetic switch valve.
7. control setup according to claim 4 (3) is characterized in that, described first electromagnetic valve (33) and second electromagnetic valve (34) are Solenoid ball valve or electromagnetic switch valve.
8. control setup according to claim 1 (3) is characterized in that, described flow divider-combiner (35) is synchronous branch combiner valve.
9. the hydraulic efficiency pressure system of a single pump double motor driving engineering truck is characterized in that, comprises each described control setup (3) in the claim 1 to 8.
10. the engineering truck that single pump double motor drives is characterized in that, comprises the described hydraulic efficiency pressure system of claim 9.
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2010
- 2010-08-31 CN CN2010205109968U patent/CN201792744U/en not_active Expired - Lifetime
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