CN205064447U - Many function test system of full hydraulic steering - Google Patents
Many function test system of full hydraulic steering Download PDFInfo
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- CN205064447U CN205064447U CN201520764181.5U CN201520764181U CN205064447U CN 205064447 U CN205064447 U CN 205064447U CN 201520764181 U CN201520764181 U CN 201520764181U CN 205064447 U CN205064447 U CN 205064447U
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Abstract
The utility model discloses a many function test system of full hydraulic steering, including taking temperature control system's oil tank module ( I ), the motor pump package module ( II ) of taking the flow control system, system's oil circuit to switch module ( III ), long -range pressure load module ( IV ), overload valve capability test module ( V ), operation control mechanism ( VI ), bridge circuit analog loading module ( VII ), sensor data collection module, electrical system and computer data flow control 0. This test system passes through system's oil circuit and switches the module, can realize the switching to steering gear (including opening the reactionless type of core, opening the core type of responding and close the reactionless type of core etc. ) the test system of the steering gear of load sensing type and other functional type formulas. Carry out data acquisition and processing to the pressure among the test performance, flow, moment of torsion, rotational speed parameter through all kinds of sensors, PLC etc. Properties of product are differentiated to the accuracy.
Description
Technical field
The utility model relates to hydraulic system field, particularly, relates to a kind of multifunctional test system of all-hydraulic steering gear.
Background technique
All-hydraulic steering gear due to its reliable performance, handle the advantages such as comfortable, compact structure, on the hydraulic steering system being widely used in the low-speed heave-load vehicles such as engineering machinery, farm machinery, fork truck and Hydraulic Drive in Vessel rudder.But due to the diversity (as load sensing type turns, opens core absorbing wave maker, opens core reactive pattern and close core absorbing wave maker etc.) of all-hydraulic steering gear function pattern, cause test event mainly with and the difference of performance requirement, make existing test system cannot meet the delivery test of all-hydraulic steering gear and the test request of type approval test.Existing test system adopts series flow control valve regulating system flow, cause that system pressure loss is high, pipeline is complicated, there is the shortcomings such as system heating is serious, energy consumption is large, and test system oil circuit switches employing manual ball valve and switches, complex operation, pipeline structure is complicated, simultaneously for the delivery test of all-hydraulic steering gear (load sensing type, open core absorbing wave maker, open core reactive pattern and close core absorbing wave maker) and the poor universality of type approval test of difference in functionality pattern, the test request of all Test items cannot be met simultaneously.
Model utility content
The purpose of this utility model is to provide a kind of all-hydraulic steering gear multifunctional test system, this all-hydraulic steering gear multifunctional test system simple structure, mode of operation is quick, stable performance, general interchangeability is good, operating process is simple and easy, and can meet delivery test and the type approval test project of the all-hydraulic steering gear of difference in functionality pattern.
To achieve these goals, the utility model provides a kind of all-hydraulic steering gear multifunctional test system, comprises the fuel tank module of band temperature control system, the electric-motor pump group module being with flow control system, system oil-way handover module, remote pressure load-on module, overload valve performance test module, operation control mechanism, bridge type return simulation loading module, sensor data acquisition module, automatical control system and computer digital animation center; Wherein, fuel tank module is connected with system oil-way handover module by electric-motor pump group module; Fuel tank module is connected with the T mouth of all-hydraulic steering gear to be measured by remote pressure load-on module; System oil-way handover module is connected with the P mouth of all-hydraulic steering gear to be measured by solenoid valve; System oil-way handover module is connected with R mouth with the L mouth of all-hydraulic steering gear to be measured respectively by overload valve performance test module; The two ends of bridge type return simulation loading module are connected with R mouth with the L mouth of all-hydraulic steering gear to be measured respectively by solenoid valve; Operation control mechanism is connected to the steering power input end of all-hydraulic steering gear to be measured.
Preferably, fuel tank module comprises the fuel tank, temperature control heating device, the first temperature transducer and the circulating cooler that are connected successively by high-pressure oil pipe, wherein, is also provided with the 3rd filter between temperature transducer and circulating cooler.
Preferably, electric-motor pump group module comprises the first stop valve, the second stop valve, variable-frequency electric pump group, common electric machine pump group, the first one-way valve and the second one-way valve; Wherein, the first stop valve, variable-frequency electric pump group and the first one-way valve are in turn connected to form the first oil duct, and the second stop valve, common electric machine pump group and the second one-way valve are in turn connected to form the second oil duct; First oil duct and the second oil duct are connected in parallel rear one end and are connected with fuel tank module by high-pressure oil pipe, and the other end is connected with system oil-way handover module by the first filter.
Preferably, system oil-way handover module comprises 3-position 4-way electro-hydraulic directional valve, priority flow control valves, shuttle valve, the 3rd one-way valve and two-way stop formula Solenoid ball valve; Wherein, 3-position 4-way electro-hydraulic directional valve is connected with priority flow control valves respectively by high-pressure oil pipe, shuttle valve, the 3rd one-way valve, and system oil-way handover module is connected with the P mouth of all-hydraulic steering gear to be measured by two-way stop formula Solenoid ball valve;
Preferably, remote pressure load-on module comprises the first pilot operated electromagnetic relief valve, the second pilot operated electromagnetic relief valve and the 3rd pilot operated electromagnetic relief valve; Second direct-acting overflow valve, the 3rd direct-acting overflow valve; Wherein,
First pilot operated electromagnetic relief valve two ends are connected with 3-position 4-way electro-hydraulic directional valve, circulating cooler respectively by high-pressure oil pipe, and the first pilot operated electromagnetic relief valve is also connected with the first direct-acting overflow valve;
Second pilot operated electromagnetic relief valve one end is connected with the 3rd one-way valve by high-pressure oil pipe, the other end is connected with circulating cooler by the second two-bit triplet solenoid directional control valve, second gauge and the 4th one-way valve successively, and the second pilot operated electromagnetic relief valve is also connected with the second direct-acting overflow valve;
3rd pilot operated electromagnetic relief valve one end is connected with the T mouth of all-hydraulic steering gear to be measured by high-pressure oil pipe, the other end is connected with circulating cooler by the first two-bit triplet solenoid directional control valve, second gauge and the 4th one-way valve successively, and the 3rd pilot operated electromagnetic relief valve is also connected with the 3rd direct-acting overflow valve.
Preferably, overload valve performance test module comprises the first two-way stop formula Solenoid ball valve, the second two-way stop formula Solenoid ball valve, the 3rd two-way stop formula Solenoid ball valve, the 4th two-way stop formula Solenoid ball valve, the 5th two-way stop formula Solenoid ball valve and the Characteristic of Priority Valve that are connected by high-pressure oil pipe.
Preferably, operate control mechanism mainly to comprise: torque rotary speed sensing instrument, speed-change gear box, actuating motor and steering wheel; Wherein, actuating motor and steering wheel to be connected on speed-change gear box and speed-change gear box is connected with the steering power input end of all-hydraulic steering gear to be measured by torque rotary speed sensing instrument.
Preferably, bridge type return simulation loading module comprises the first plate-type non-return valve, the second plate-type non-return valve, three-plate type one-way valve, the 4th plate-type non-return valve, the 4th pilot operated electromagnetic relief valve and the 4th direct-acting overflow valve; Wherein, the first plate-type non-return valve and the second plate-type non-return valve are connected to form the first branch road, and the two ends of the first branch road are connected with the L mouth of all-hydraulic steering gear to be measured, R mouth respectively; Three-plate type one-way valve and the 4th plate-type non-return valve are connected to form the second branch road, and the two ends of the second branch road are connected with the L mouth of all-hydraulic steering gear to be measured, R mouth respectively; First branch road and the second branch road are also connected with the second filter, first-class gauge and the 4th pilot operated electromagnetic relief valve in turn; 4th pilot operated electromagnetic relief valve is also connected with the 4th direct-acting overflow valve.
Preferably, sensor data acquisition module comprises the first pressure transducer, the second pressure transducer, the 3rd pressure transducer, the 4th pressure transducer, the 5th pressure transducer, the 6th pressure transducer, the 7th pressure transducer and the second temperature transducer; Wherein,
First pressure transducer is arranged on the P mouth of all-hydraulic steering gear to be measured; Second pressure transducer and the second temperature transducer are connected to the L mouth of all-hydraulic steering gear to be measured in turn; 3rd pressure transducer is arranged on the R mouth of all-hydraulic steering gear to be measured; 4th pressure transducer is arranged on the T mouth of all-hydraulic steering gear to be measured; 5th pressure transducer is arranged on all-hydraulic steering gear to be measured; 6th pressure transducer is arranged on the first pilot operated electromagnetic relief valve; 7th pressure transducer is arranged on the second pilot operated electromagnetic relief valve.
According to technique scheme, the utility model uses variable-frequency electric pump group, common electric machine pump group makes flow system flow scope in 0 ~ 160L/min, can meet the traffic demand of testing property under all kinds all-hydraulic steering gear different displacements, different rotating speeds.There is system pressure loss little, the features such as the impact that pressure versus flow amount changes is little.This system also adopts system oil-way handover module to design, combined by the function of 3-position 4-way electro-hydraulic reversing valve and shuttle valve, the long-range switching of the commutator test system to load sensing type commutator and other function patterns can be realized, there is system architecture simple and easy, mode of operation is quick, steady performance.Carry out accurate acquisition and processing by various kinds of sensors and PLC etc. to supplemental characteristics such as the pressure in test performance, flow, moment of torsion, rotating speeds, test process realizes automation to a certain degree and informationization, makes test result more accurate and directly perceived.Like this, this system can meet delivery test and the type approval test project of the all-hydraulic steering gear (load sensing type, open core absorbing wave maker, open core reactive pattern and close core absorbing wave maker) of difference in functionality pattern, there is general interchangeability good, the easy feature of operating process.
Other feature and advantage of the present utility model are described in detail in embodiment part subsequently.
Accompanying drawing explanation
Accompanying drawing is used to provide further understanding of the present utility model, and forms a part for specification, is used from explanation the utility model, but does not form restriction of the present utility model with embodiment one below.In the accompanying drawings:
Fig. 1 is the module map of the multifunctional test system of all-hydraulic steering gear in a kind of mode of execution provided according to the utility model;
Fig. 2 is the schematic diagram of the multifunctional test system of all-hydraulic steering gear in a kind of mode of execution provided according to the utility model;
Fig. 3 is the functional symbol figure opening core absorbing wave maker all-hydraulic steering gear in a kind of mode of execution provided according to the utility model;
Fig. 4 is the functional symbol figure opening core reactive pattern all-hydraulic steering gear in a kind of mode of execution provided according to the utility model;
Fig. 5 is the functional symbol figure closing core absorbing wave maker all-hydraulic steering gear in a kind of mode of execution provided according to the utility model; And
Fig. 6 is the functional symbol figure of the load sensing type all-hydraulic steering gear in a kind of mode of execution provided according to the utility model.
Description of reference numerals
I-fuel tank module, II-electric-motor pump group module
III-system oil-way handover module, IV-remote pressure load-on module
V-overload valve performance test module, VI-operation control mechanism
VII-bridge type return simulation loading module 11-first filter
12-second filter 13-the 3rd filter
21-first stop valve 22-second stop valve
31-variable-frequency electric pump group 32-common electric machine pump group
41-first one-way valve 42-second one-way valve
43-the 3rd one-way valve 44-the 4th one-way valve
51-3-position 4-way electro-hydraulic directional valve 61-priority flow control valves
71-shuttle valve 81-first two-bit triplet solenoid directional control valve
82-second two-bit triplet solenoid directional control valve 91-first pilot operated electromagnetic relief valve
92-second pilot operated electromagnetic relief valve 93-the 3rd pilot operated electromagnetic relief valve
94-the 4th pilot operated electromagnetic relief valve 101-first direct-acting overflow valve
102-second direct-acting overflow valve 103-the 3rd direct-acting overflow valve
104-the 4th direct-acting overflow valve 111-Characteristic of Priority Valve
121-first plate-type non-return valve 122-second plate-type non-return valve
123-three-plate type one-way valve 124-the 4th plate-type non-return valve
131-first two-way stop formula Solenoid ball valve 132-second two-way stop formula Solenoid ball valve
133-the 3rd two-way stop formula Solenoid ball valve 134-the 4th two-way stop formula Solenoid ball valve
The first-class gauge of 135-the 5th two-way stop formula Solenoid ball valve 141-
142-second gauge 151-first pressure transducer
152-second pressure transducer 153-the 3rd pressure transducer
154-the 4th pressure transducer 155-the 5th pressure transducer
156-the 6th pressure transducer 157-the 7th pressure transducer
161-torque rotary speed sensing instrument 171-speed-change gear box
181-actuating motor 191-steering wheel
201-temperature control heating device 211-first temperature transducer
212-second temperature transducer 221-circulating cooler
231-fuel tank 241-all-hydraulic steering gear to be measured
Embodiment
Below in conjunction with accompanying drawing, embodiment of the present utility model is described in detail.Should be understood that, embodiment described herein, only for instruction and explanation of the utility model, is not limited to the utility model.
A, steering wheel rotational speed regulation: start actuating motor 181, regulable control knob left (or to the right) can obtain required steering wheel rotating speed.
B, system pressure regulate: electromagnet 6DT is energized, start variable-frequency electric pump group 31 and common electric machine pump group 32 (not starting variable-frequency electric pump group 31 when commutator 241 test traffic is less than 80L/min), regulate the adjusting knob of variable-frequency electric pump group 31 variable-frequency motor to set tested commutator 241 test traffic; Make 3-position 4-way electro-hydraulic directional valve 51 be in meta, regulate the first direct-acting overflow valve 101, can initialization system pressure.
The T mouth backpressure regulation of C, commutator 241: electromagnet 6DT, 13DT are energized, starts variable-frequency electric pump group 31 and common electric machine pump group 32 (not starting variable-frequency electric pump group 31 when commutator 241 test traffic is less than 80L/min) regulates the adjusting knob of variable-frequency electric pump group 31 variable-frequency motor to set tested commutator 241 test traffic; Electromagnet 3DT obtains electric, regulates the 3rd direct-acting overflow valve 103, can set the T mouth back pressure of commutator 241.
The P of D, commutator 241, A, B mouth pressure regulates: electromagnet 6DT is energized, start variable-frequency electric pump group 31 and common electric machine pump group 32 (not starting variable-frequency electric pump group 31 when commutator 241 test traffic is less than 80L/min), regulate the adjusting knob of variable-frequency electric pump group 31 variable-frequency motor to set tested commutator 241 test traffic; Electromagnet 3DT, 10DT, 11DT, 13DT obtain electric, start actuating motor 181, and regulable control knob left (or to the right), regulates the 4th direct-acting overflow valve 104, can set the P of commutator 241, A, B mouth pressure.
The unloaded pressure of E, commutator 241 regulates: electromagnet 6DT is energized, start variable-frequency electric pump group 31 and common electric machine pump group 32 (not starting variable-frequency electric pump group 31 when commutator 241 test traffic is less than 80L/min), regulate the adjusting knob of variable-frequency electric pump group 31 variable-frequency motor to set nominal flow rate (test traffic) needed for tested commutator 241; Electromagnet 3DT, 10DT, 11DT, 13DT obtain electric, start actuating motor 181, and regulable control knob, can make commutator 241 be in unloaded state left (or to the right).
The test of F, load sensing type commutator: associated adjustment roughly the same with above-mentioned A, B, C, D, E project, difference is, to be energized switched system oil circuit by electromagnet 2DT; 2 times that test traffic (inlet flow rate of priority flow control valves 61) is tested commutator 241 nominal flow rate are regulated by electromagnet 2DT, 5DT energising.
1, safety valve pressure is set up and pressure stability experiment
By step B, make system pressure be not less than tested commutator 241 safety valve setting pressure 6MPa, tested commutator 241 is adjusted with nominal flow rate, and electromagnet 3DT, 13DT obtain electric, to the left or to the right steering wheel rotation, under the operating mode of endpoint detection moment of torsion, carry out following test:
A. regulate the safety valve pressure regulating screw of tested commutator 241, whether steadily observe its pressure change procedure from pressure gauge, until be adjusted to required force value and record;
B. regulate the safety valve of tested commutator 241 to set pressure, observe pressure oscillation value from pressure gauge, test gets its mean value and record 3 times repeatedly.
2, overload valve valve pressure setting and pressure stability experiment
Commutator 241 is in meta, by step B, makes test traffic be about 4L/min; Regulation relief valve 101, makes system pressure be not less than the safety valve setting pressure 2MPa of tested commutator 241; Magnet 3DT, 8DT (or 9DT), electric, steering wheel rotation to the left or to the right, carry out following test:
A. regulate the left and right overload valve pressure regulating screw of tested commutator 241, whether steadily observe its pressure change procedure from corresponding pressure table respectively, until be adjusted to required force value and record;
B. regulate the left and right overload valve of tested commutator 241 to set pressure, observe pressure oscillation value from corresponding pressure table respectively, repeatedly get its mean value and record 3 times.
3, mechanical resistance square
The each hydraulic fluid port of tested commutator 241 does not take over road, by steps A, regulates steering wheel rotating speed, the torque of direction of measurement dish under (30 ± 5) r/min.
4, steering wheel maximum speed test (being only applicable to load sensing type commutator)
Electromagnet 2DT obtains electric, regulates the adjusting knob of variable-frequency electric pump group 31 variable-frequency motor, makes test traffic (inlet flow rate of priority flow control valves 61) for 2 times of tested commutator 241 nominal flow rate; Electromagnet 4DT, 10DT, 11DT, 12DT, 13DT obtain electric, by steps A, steering wheel rotating speed are increased gradually from zero; Regulate the 3rd direct-acting overflow valve 103, the T mouth of tested commutator 241 is made to be pressed as 0.63MPa, record the pressure difference value of steering wheel rotating speed, input torque and P mouth and LS mouth simultaneously, till input torque is obvious ascendant trend (occurring manual steering), there is not maximum speed value during manual steering phenomenon in record.
5, servosteering performance
By step B, make system pressure be 1.25 times of maximum inlet pressure, tested commutator 241 is adjusted with nominal flow rate, carries out following test:
A. by step D, the P mouth pressure of commutator 241 is made to be maximum inlet pressure; By step C, the T mouth back pressure making commutator 241 is 0.63Mpa, with about hand steering wheel rotation each more than 5 times, checks servosteering performance.
B. by steps A, steering wheel rotating speed is made to be 60r/min; By step D, the P mouth pressure of commutator 241 is made to be maximum inlet pressure; By step C, the T mouth back pressure making commutator 241 is 0.63Mpa, measures the power torque of now commutator 241 and the A of commutator 241, the pressure oscillation value of B mouth.By step C, the T mouth back pressure making commutator 241 is 6.3Mpa, measures the power torque of now commutator 241.
C. by step D, the P mouth pressure of commutator 241 is made to be maximum inlet pressure, electromagnet 10DT and electromagnet 11DT power-off; By steps A, make steering wheel rotating speed be 0r/min, check terminal sensation, survey its terminal torque and record.
6, sealability
By step B, system pressure is made to be 1.25 times of maximum inlet pressure; By step D, the P mouth pressure of commutator 241 is made to be maximum inlet pressure; By step C, the T mouth back pressure making commutator 241 is 6.3Mpa; By steps A, regulate actuating motor 181 control handle (or to the right) left, make steering wheel rotating speed be 60r/min, by about 30 seconds, interval alternately, checked whether outer Seepage.
7, the pressure loss
By step e, tested commutator 241 is adjusted with nominal flow rate, makes commutator 241 be in unloaded state, carries out following test:
A. by steps A, steering wheel rotating speed is made to be 60r/min; Measure the pressure reduction of PA (or B) mouth of commutator 241.
B. stop actuating motor 181, measure the pressure reduction (note: the no this item of load sensing type all-hydraulic steering gear is tested) of the PT mouth of commutator 241.
8, internal leakage
Open core absorbing wave maker (as shown in Figure 3) and open core reactive pattern (as shown in Figure 4) all-hydraulic steering gear:
By step C, tested commutator 241 is adjusted with nominal flow rate, and regulate the 4th direct-acting overflow valve 104, the T mouth back pressure making commutator 241 is 6.3Mpa.After tested commutator 241 starts 30 seconds, start timing, measure the A of commutator 241, the leakage rate of B hydraulic fluid port 1min.
Load sensing type all-hydraulic steering gear:
Regulate the adjusting knob of pump 32 variable-frequency motor, electromagnet 2DT obtains electric, makes test traffic (inlet flow rate of pressure-gradient control valve 61) for 2 times of tested commutator 241 nominal flow rate; Commutator 241 is in meta, and right A (or B) mouth is to commutator 241 fuel feeding respectively, is under the condition of 12.5MPa at pilot system pressure, measures the leakage total amount of P, T, B (or A) mouth 1min.
9, flow change rate (note: the no this item of load sensing type all-hydraulic steering gear is tested)
By step e and D, tested commutator 241 is adjusted with nominal flow rate, makes the P mouth pressure of commutator 241 be unloaded pressure and maximum inlet pressure; By steps A, make steering wheel rotating speed be 60r/min, electromagnet 6DT is energized, and measures the flow under two states, calculated flow rate variance ratio.
Below preferred implementation of the present utility model is described by reference to the accompanying drawings in detail; but; the utility model is not limited to the detail in above-mentioned mode of execution; within the scope of technical conceive of the present utility model; can carry out multiple simple variant to the technical solution of the utility model, these simple variant all belong to protection domain of the present utility model.
It should be noted that in addition, each concrete technical characteristics described in above-mentioned embodiment, in reconcilable situation, can be combined by any suitable mode, in order to avoid unnecessary repetition, the utility model illustrates no longer separately to various possible compound mode.
In addition, also can carry out combination in any between various different mode of execution of the present utility model, as long as it is without prejudice to thought of the present utility model, it should be considered as content disclosed in the utility model equally.
Claims (9)
1. the multifunctional test system of an all-hydraulic steering gear, it is characterized in that, comprise the fuel tank module (I) of band temperature control system, the electric-motor pump group module (II) being with flow control system, system oil-way handover module (III), remote pressure load-on module (IV), overload valve performance test module (V), operation control mechanism (VI), bridge type return simulation loading module (VII), sensor data acquisition module, automatical control system and computer digital animation center; Wherein,
Described fuel tank module (I) is connected with described system oil-way handover module (III) by described electric-motor pump group module (II);
Described fuel tank module (I) is connected with the T mouth of all-hydraulic steering gear to be measured (241) by described remote pressure load-on module (IV);
Described system oil-way handover module (III) is connected by the P mouth of solenoid valve with described all-hydraulic steering gear to be measured (241);
Described system oil-way handover module (III) is connected with R mouth with the L mouth of described all-hydraulic steering gear to be measured (241) respectively by described overload valve performance test module (V);
The two ends of described bridge type return simulation loading module (VII) are connected with R mouth respectively by the L mouth of solenoid valve with described all-hydraulic steering gear to be measured (241);
Described operation control mechanism (VI) is connected to the steering power input end of described all-hydraulic steering gear to be measured (241).
2. according to the multifunctional test system of the all-hydraulic steering gear described in claim 1, it is characterized in that, described fuel tank module (I) comprises the fuel tank (231), temperature control heating device (201), the first temperature transducer (211) and the circulating cooler (221) that are connected successively by high-pressure oil pipe, wherein, the 3rd filter (13) is also provided with between described first temperature transducer (211) and circulating cooler (221).
3. according to the multifunctional test system of the all-hydraulic steering gear described in claim 2, it is characterized in that, described electric-motor pump group module (II) comprises the first stop valve (21), the second stop valve (22), variable-frequency electric pump group (31), common electric machine pump group (32), the first one-way valve (41) and the second one-way valve (42); Wherein, described first stop valve (21), variable-frequency electric pump group (31) and the first one-way valve (41) are in turn connected to form the first oil duct, and described second stop valve (22), common electric machine pump group (32) and the second one-way valve (42) are in turn connected to form the second oil duct; Described first oil duct and described second oil duct are connected in parallel rear one end and are connected with described fuel tank module (I) by high-pressure oil pipe, and the other end is connected with described system oil-way handover module (III) by the first filter (11).
4. according to the multifunctional test system of the all-hydraulic steering gear described in claim 3, it is characterized in that, described system oil-way handover module (III) comprises 3-position 4-way electro-hydraulic directional valve (51), priority flow control valves (61), shuttle valve (71), the 3rd one-way valve (43) and the 5th two-way stop formula Solenoid ball valve (135); Wherein, described 3-position 4-way electro-hydraulic directional valve (51) is connected with described priority flow control valves (61) respectively by high-pressure oil pipe, described shuttle valve (71), described 3rd one-way valve (43), and described system oil-way handover module (III) is connected with the P mouth of described all-hydraulic steering gear to be measured (241) by described 5th two-way stop formula Solenoid ball valve (135).
5. according to the multifunctional test system of the all-hydraulic steering gear described in claim 4, it is characterized in that, described remote pressure load-on module (IV) comprises the first pilot operated electromagnetic relief valve (91), the second pilot operated electromagnetic relief valve (92), the 3rd pilot operated electromagnetic relief valve (93), the second direct-acting overflow valve (102), the 3rd direct-acting overflow valve (103); Wherein,
Described first pilot operated electromagnetic relief valve (91) two ends are connected with described 3-position 4-way electro-hydraulic directional valve (51), described circulating cooler (221) respectively by high-pressure oil pipe, and described first pilot operated electromagnetic relief valve (91) is also connected with the first direct-acting overflow valve (101);
Described second pilot operated electromagnetic relief valve (92) one end is connected with described 3rd one-way valve (43) by high-pressure oil pipe, the other end is connected with described circulating cooler (221) by the second two-bit triplet solenoid directional control valve (82), second gauge (142) and the 4th one-way valve (44) successively, and described second pilot operated electromagnetic relief valve (92) is also connected with the second direct-acting overflow valve (102);
Described 3rd pilot operated electromagnetic relief valve (93) one end is connected by the T mouth of high-pressure oil pipe with described all-hydraulic steering gear to be measured (241), the other end is connected with described circulating cooler (221) by the first two-bit triplet solenoid directional control valve (81), second gauge (142) and the 4th one-way valve (44) successively, and described 3rd pilot operated electromagnetic relief valve (93) is also connected with the 3rd direct-acting overflow valve (103).
6. according to the multifunctional test system of the all-hydraulic steering gear described in claim 1, it is characterized in that, described overload valve performance test module (V) comprises the first two-way stop formula Solenoid ball valve (131), the second two-way stop formula Solenoid ball valve (132), the 3rd two-way stop formula Solenoid ball valve (133), the 4th two-way stop formula Solenoid ball valve (134), the 5th two-way stop formula Solenoid ball valve (135) and the Characteristic of Priority Valve (111) that are connected by high-pressure oil pipe.
7. according to the multifunctional test system of the all-hydraulic steering gear described in claim 1, it is characterized in that, described operation control mechanism (VI) mainly comprises: torque rotary speed sensing instrument (161), speed-change gear box (171), actuating motor (181) and steering wheel (191); Wherein, described actuating motor (181) and steering wheel (191) are connected to the upper and described speed-change gear box (171) of described speed-change gear box (171) and are connected by the steering power input end of described torque rotary speed sensing instrument (161) with described all-hydraulic steering gear to be measured (241).
8. according to the multifunctional test system of the all-hydraulic steering gear described in claim 1, it is characterized in that, described bridge type return simulation loading module (VII) comprises the first plate-type non-return valve (121), the second plate-type non-return valve (122), three-plate type one-way valve (123), the 4th plate-type non-return valve (124), the 4th pilot operated electromagnetic relief valve (94) and the 4th direct-acting overflow valve (104); Wherein,
Described first plate-type non-return valve (121) and the second plate-type non-return valve (122) are connected to form the first branch road, and the two ends of described first branch road are connected with the L mouth of described all-hydraulic steering gear to be measured (241), R mouth respectively; Described three-plate type one-way valve (123) and the 4th plate-type non-return valve (124) are connected to form the second branch road, and the two ends of described second branch road are connected with the L mouth of described all-hydraulic steering gear to be measured (241), R mouth respectively; Described first branch road and the second branch road are also connected with the second filter (12), first-class gauge (141) and the 4th pilot operated electromagnetic relief valve (94) in turn; Described 4th pilot operated electromagnetic relief valve (94) is also connected with described 4th direct-acting overflow valve (104).
9. according to the multifunctional test system of the all-hydraulic steering gear described in claim 5, it is characterized in that, described sensor data acquisition module comprises the first pressure transducer (151), the second pressure transducer (152), the 3rd pressure transducer (153), the 4th pressure transducer (154), the 5th pressure transducer (155), the 6th pressure transducer (156), the 7th pressure transducer (157) and the second temperature transducer (212); Wherein,
Described first pressure transducer (151) is arranged on the P mouth of described all-hydraulic steering gear to be measured (241); Described second pressure transducer (152) and the second temperature transducer (212) are connected to the L mouth of described all-hydraulic steering gear to be measured (241) in turn; Described 3rd pressure transducer (153) is arranged on the R mouth of described all-hydraulic steering gear to be measured (241); Described 4th pressure transducer (154) is arranged on the T mouth of described all-hydraulic steering gear to be measured (241); Described 5th pressure transducer (155) is arranged on described all-hydraulic steering gear to be measured (241); Described 6th pressure transducer (156) is arranged on described first pilot operated electromagnetic relief valve (91); Described 7th pressure transducer (157) is arranged on described second pilot operated electromagnetic relief valve (92).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520764181.5U CN205064447U (en) | 2015-09-29 | 2015-09-29 | Many function test system of full hydraulic steering |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520764181.5U CN205064447U (en) | 2015-09-29 | 2015-09-29 | Many function test system of full hydraulic steering |
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| CN205064447U true CN205064447U (en) | 2016-03-02 |
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| CN201520764181.5U Withdrawn - After Issue CN205064447U (en) | 2015-09-29 | 2015-09-29 | Many function test system of full hydraulic steering |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105134692A (en) * | 2015-09-29 | 2015-12-09 | 芜湖中意液压科技股份有限责任公司 | Multifunctional testing system of full hydraulic steering gear |
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2015
- 2015-09-29 CN CN201520764181.5U patent/CN205064447U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105134692A (en) * | 2015-09-29 | 2015-12-09 | 芜湖中意液压科技股份有限责任公司 | Multifunctional testing system of full hydraulic steering gear |
| CN105134692B (en) * | 2015-09-29 | 2017-07-04 | 芜湖中意液压科技股份有限责任公司 | The multifunctional test system of all-hydraulic steering gear |
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Legal Events
| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20160302 Effective date of abandoning: 20170704 |