CN210949326U - Hydraulic system for tipping moment test of excavator - Google Patents
Hydraulic system for tipping moment test of excavator Download PDFInfo
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- CN210949326U CN210949326U CN201922082882.1U CN201922082882U CN210949326U CN 210949326 U CN210949326 U CN 210949326U CN 201922082882 U CN201922082882 U CN 201922082882U CN 210949326 U CN210949326 U CN 210949326U
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Abstract
A hydraulic system for a tipping moment test of an excavator comprises a hydraulic pump and a hydraulic oil tank; the hydraulic system also comprises a hydraulic oil cylinder I, a hydraulic oil cylinder II, a hydraulic oil cylinder III and a hydraulic oil cylinder IV; the hydraulic oil cylinder I, the hydraulic oil cylinder II, the hydraulic oil cylinder III and the hydraulic oil cylinder IV are connected with a manual reversing valve II, and the four oil cylinders are controlled by the manual reversing valve II to lift the excavator during testing; the hydraulic oil cylinder I is connected with the manual reversing valve V, the hydraulic oil cylinder II is connected with the manual reversing valve III, the hydraulic oil cylinder III is connected with the manual reversing valve IV, and the hydraulic oil cylinder IV is connected with the manual reversing valve I; pressure sensors are arranged at the large cavity oil inlet of the hydraulic oil cylinder I, the hydraulic oil cylinder II, the hydraulic oil cylinder III and the hydraulic oil cylinder IV, and pressure sensors are arranged at the small cavity oil inlet of the hydraulic oil cylinder I, the hydraulic oil cylinder II, the hydraulic oil cylinder III and the hydraulic oil cylinder IV. The utility model has the characteristics of control simply, require low, the hydro-cylinder can independently finely tune, the cost of manufacture is low to hydraulic system cleanliness.
Description
Technical Field
The utility model relates to a hydraulic system for excavator moment of tumbling is experimental belongs to the experimental technical field of excavator.
Background
The excavator is a main tool for earth and rockwork, and the stability of the excavator affects the exertion of the operation capability of the excavator and the comfort of a driver during operation. The tipping moment is taken as an important stability parameter, and in the design process, a basis is provided for the calculation of the balance weight of the whole excavator, the design of the bucket capacity, the preparation of a working tool and the like.
The existing hydraulic system for jacking the multiple hydraulic cylinders adopts four hydraulic cylinders to be separately controlled, so that manual operation is required to be accurate, and the control difficulty is high; a single flow dividing and collecting valve system is adopted, and the final posture cannot be finely adjusted; the electro-hydraulic proportional system is adopted for adjustment, although the excavator can be accurately jacked to a preset position, the electro-hydraulic proportional valve and the synchronous control system are adopted, the price is high, and the requirement on the cleanliness of the hydraulic system is high.
Disclosure of Invention
The utility model aims at overcoming above-mentioned defect, the purpose provides an excavator torque test hydraulic system that tumbles that experimental place required lowly, easy operation, intensity of labour are low.
In order to realize the purpose, the utility model discloses a technical scheme is:
a hydraulic system for a tipping moment test of an excavator comprises a hydraulic pump and a hydraulic oil tank; the hydraulic system also comprises a hydraulic oil cylinder I, a hydraulic oil cylinder II, a hydraulic oil cylinder III and a hydraulic oil cylinder IV; the hydraulic oil cylinders I, II, III and IV are connected with a manual reversing valve II, and four oil cylinders are controlled by the manual reversing valve II to lift the excavator during testing; the hydraulic oil cylinder I is connected with the manual reversing valve V, the hydraulic oil cylinder II is connected with the manual reversing valve III, the hydraulic oil cylinder III is connected with the manual reversing valve IV, and the hydraulic oil cylinder IV is connected with the manual reversing valve I; pressure sensors are arranged at the large cavity oil inlet of the hydraulic oil cylinder I, the hydraulic oil cylinder II, the hydraulic oil cylinder III and the hydraulic oil cylinder IV, and pressure sensors are arranged at the small cavity oil inlet of the hydraulic oil cylinder I, the hydraulic oil cylinder II, the hydraulic oil cylinder III and the hydraulic oil cylinder IV; the position of a hydraulic cylinder is finely adjusted by adjusting a manual reversing valve I, a manual reversing valve III, a manual reversing valve IV and a manual reversing valve V, so that the posture of the excavator is adjusted to a tipping moment testing posture, pressure data of each pressure sensor is recorded, the distance from the hydraulic cylinder I, the hydraulic cylinder II, the hydraulic cylinder III and the hydraulic cylinder IV to a tipping line is measured, the force borne by each hydraulic cylinder is calculated according to the pressure data and parameters of the hydraulic cylinders, and the tipping moment of the excavator under the posture is calculated according to the distance of each hydraulic cylinder relative to the tipping line.
Furthermore, a T port of the manual reversing valve I is connected with a hydraulic oil tank, an A port of the manual reversing valve I is connected with an inlet of a ninth hydraulic control one-way valve and a control port of a tenth hydraulic control one-way valve, and a B port of the manual reversing valve I is connected with an inlet of the tenth hydraulic control one-way valve and a control port of the ninth hydraulic control one-way valve; an outlet of the ninth hydraulic control one-way valve is connected with a small cavity oil inlet of a hydraulic oil cylinder IV; and an outlet of the tenth hydraulic control one-way valve is connected with an oil inlet of a large cavity of the hydraulic oil cylinder IV.
Furthermore, a port T of the manual reversing valve III is connected with a hydraulic oil tank, a port A of the manual reversing valve III is connected with an inlet of a twelfth hydraulic control one-way valve and a control port of the eleventh hydraulic control one-way valve, and a port B of the manual reversing valve III is connected with an inlet of the eleventh hydraulic control one-way valve and a control port of the twelfth hydraulic control one-way valve; an outlet of the eleventh hydraulic control one-way valve is connected with a large cavity oil inlet of the hydraulic oil cylinder II; and an outlet of the twelfth hydraulic control one-way valve is connected with a small cavity oil inlet of the hydraulic oil cylinder II.
Furthermore, a T port of the manual reversing valve IV is connected with a hydraulic oil tank, a A port of the manual reversing valve IV is connected with an inlet of a thirteenth hydraulic control one-way valve and a control port of a fourteenth hydraulic control one-way valve, and a B port of the manual reversing valve IV is connected with an inlet of the fourteenth hydraulic control one-way valve and a control port of the thirteenth hydraulic control one-way valve; an outlet of the thirteenth hydraulic control one-way valve is connected with a small cavity oil inlet of the hydraulic oil cylinder III; and an outlet of the fourteenth hydraulic control one-way valve is connected with an oil inlet of a large cavity of the hydraulic oil cylinder III.
Furthermore, a port T of the manual reversing valve V is connected with a hydraulic oil tank, a port A of the manual reversing valve V is connected with an inlet of a fifteenth hydraulic control one-way valve and a control port of a sixteenth hydraulic control one-way valve, and a port B of the manual reversing valve V is connected with an inlet of the fifteenth hydraulic control one-way valve and a control port of the sixteenth hydraulic control one-way valve.
Furthermore, a T port of the manual reversing valve II is connected with a hydraulic oil tank, a A port of the manual reversing valve II is connected with a P port of the flow dividing and collecting valve II, and a B port of the manual reversing valve II is connected with an inlet of the second hydraulic control one-way valve, an inlet of the fourth hydraulic control one-way valve, an inlet of the fifth hydraulic control one-way valve, an inlet of the seventh hydraulic control one-way valve, a control port of the first hydraulic control one-way valve, a control port of the third hydraulic control one-way valve, a control port of the sixth hydraulic control one-way valve and a control port of the eighth hydraulic control.
Furthermore, an A port of the flow distributing and collecting valve II is connected with a P port of a flow distributing and collecting valve III, and a B port of the flow distributing and collecting valve II is connected with the P port of the flow distributing and collecting valve I; the port A of the flow collecting valve I is connected with an inlet of a sixth hydraulic control one-way valve and a control port of a fifth hydraulic control one-way valve, and the port B of the flow collecting valve I is connected with an inlet of an eighth hydraulic control one-way valve and a control port of a seventh hydraulic control one-way valve; an outlet of the sixth hydraulic control one-way valve is connected with a large cavity oil inlet of the hydraulic oil cylinder II, an outlet of the eighth hydraulic control one-way valve is connected with a large cavity oil inlet of the hydraulic oil cylinder IV, an outlet of the fifth hydraulic control one-way valve is connected with a small cavity oil inlet of the hydraulic oil cylinder II, and an outlet of the seventh hydraulic control one-way valve is connected with a small cavity oil inlet of the hydraulic oil cylinder IV; and the port A of the flow distributing and collecting valve III is connected with the inlet of the first hydraulic control one-way valve and the control port of the second hydraulic control one-way valve, and the port B of the flow distributing and collecting valve III is connected with the inlet of the third hydraulic control one-way valve and the control port of the fourth hydraulic control one-way valve.
Further, a pressure sensor I is installed at a large cavity oil inlet of the hydraulic oil cylinder I, and a pressure sensor II is installed at a small cavity oil inlet of the hydraulic oil cylinder I; a pressure sensor III is arranged at an oil inlet of a large cavity of the hydraulic oil cylinder III, and a pressure sensor IV is arranged at an oil inlet of a small cavity of the hydraulic oil cylinder III; a pressure sensor VI is arranged at an oil inlet of a large cavity of the hydraulic oil cylinder II, and a pressure sensor V is arranged at an oil inlet of a small cavity of the hydraulic oil cylinder II; and an oil inlet of a large cavity of the hydraulic oil cylinder IV is provided with a pressure sensor VIII, and an oil inlet of a small cavity of the hydraulic oil cylinder IV is provided with a pressure sensor VII.
Further, the inlet of the hydraulic pump is connected with a hydraulic oil tank, and the outlet of the hydraulic pump is respectively connected with the inlet of an overflow valve and the inlet of a one-way valve; the outlet of the overflow valve is connected with an oil tank; the outlet of the one-way valve is connected with the inlet of the reversing valve, the left control oil port of the reversing valve and the P port of the electromagnetic reversing valve; the outlet of the reversing valve and the T port of the electromagnetic reversing valve are connected with a hydraulic oil tank, and the A port of the electromagnetic reversing valve and the right control oil port of the reversing valve are connected with the P ports of a manual reversing valve I, a manual reversing valve II, a manual reversing valve III, a manual reversing valve IV and a manual reversing valve V.
Furthermore, the manual reversing valve I, the manual reversing valve II, the manual reversing valve III, the manual reversing valve IV and the manual reversing valve V are Y-shaped three-position four-way reversing valves, a left-position port P is communicated with a port B, and a port A is communicated with a port T; the right port P is communicated with the port A, and the port B is communicated with the port T.
The utility model discloses beneficial effect:
by adopting the scheme, on the basis of meeting the application requirements, the hydraulic system adopts the common reversing valve and the flow distributing and collecting valve, so that the requirement on the cleanliness of the hydraulic system is low, and the manufacturing cost is low. In the operation process, the four hydraulic cylinders can stably and synchronously ascend by controlling one reversing valve; the system is provided with an independent reversing valve for each hydraulic cylinder, and the oil cylinders can be independently controlled to move up and down for fine adjustment. Therefore, the utility model has the characteristics of control simply, require low, the hydro-cylinder can independently finely tune, the cost of manufacture low to hydraulic system cleanliness.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the invention without limitation. The present invention will be described in detail with reference to the accompanying drawings and examples.
FIG. 1 is a schematic diagram of a hydraulic system of the present invention;
FIG. 2 is a diagram of a rollover moment test of an excavator employing a hydraulic system;
fig. 3 is a schematic diagram of a cylinder mounting position and a forward tipping position of the excavator.
In the figure, 1, a tilt angle sensor; 2. an excavator; 3. a groove I; 4. a groove II; 5. a hydraulic oil cylinder I; 6. a pressure sensor I; 7. a pressure sensor II; 8. a first hydraulic control check valve; 9. a second hydraulic control one-way valve; 10. a third hydraulic control check valve; 11. a fourth hydraulic control check valve; 12. a pressure sensor III; 13. a pressure sensor IV; 14. a hydraulic oil cylinder III; 15. a hydraulic oil cylinder II; 16. a pressure sensor V; 17. a pressure sensor VI; 18. a fifth hydraulic control check valve; 19. a sixth hydraulic control check valve; 20. a seventh hydraulic control check valve; 21. a pressure sensor VII; 22. a pressure sensor VIII; 23. a hydraulic oil cylinder IV; 24. an eighth hydraulic control check valve; 25. a flow distributing and collecting valve I; 26. a ninth pilot operated check valve; 27. a tenth pilot operated check valve; 28. a manual reversing valve I; 29. a flow distributing and collecting valve II; 30. a manual reversing valve II; 31. a hydraulic oil tank; 32. an eleventh pilot operated check valve; 33. a manual reversing valve III; 34. a twelfth hydraulic control check valve; 35. an electromagnetic directional valve; 36. a diverter valve; 37. a thirteenth pilot operated check valve; 38. a manual reversing valve IV; 39. a fourteenth hydraulic control check valve; 40. an overflow valve; 41. a hydraulic pump; 42. a one-way valve; 43. a manual reversing valve V; 44. a fifteenth hydraulic control check valve; 45. a sixteenth hydraulic control check valve; and 46 flow dividing and combining valve III.
Detailed Description
In order to make the purpose, technical solution and advantages of the present invention clearer, the following will combine the drawings in the embodiments of the present invention to perform more detailed description on the technical solution in the embodiments of the present invention. In the drawings, the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The described embodiments are only some, but not all embodiments of the invention. The embodiments described below with reference to the drawings are exemplary and intended to be used for explaining the present invention, and should not be construed as limiting the present invention. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention. Embodiments of the present invention will be described in detail below with reference to the accompanying drawings.
As shown in figures 2 and 3, a hydraulic oil cylinder I5 and a hydraulic oil cylinder II 15 are vertically arranged in the groove I3, and a hydraulic oil cylinder III 14 and a hydraulic oil cylinder IV 23 are vertically arranged in the groove II 4. 2 outside tracks of excavator are parallel and press on I3 of slot, and 1 inside tracks of excavator are parallel and press on II 4 of slot. The tilt sensor 1 is fixedly mounted on the excavator 2. The grooves I3 and II 4 are identical in shape. The length direction of the groove I3 is parallel to the length direction of the groove II 4, and the width direction of the groove I3 is parallel to the width direction of the groove II 4. The center connecting lines of the upper surfaces of the hydraulic oil cylinder I5, the hydraulic oil cylinder II 15, the hydraulic oil cylinder III 14 and the hydraulic oil cylinder IV 23 are rectangular.
As shown in figure 1, the hydraulic system for the excavator tilting moment test comprises a hydraulic oil cylinder I5, a pressure sensor I6, a pressure sensor II 7, a first hydraulic control one-way valve 8, a second hydraulic control one-way valve 9, a third hydraulic control one-way valve 10, a fourth hydraulic control one-way valve 11, a pressure sensor III 12, a pressure sensor IV 13, a hydraulic oil cylinder III 14, a hydraulic oil cylinder II 15, a pressure sensor V16, a pressure sensor VI 17, a fifth hydraulic control one-way valve 18, a sixth hydraulic control one-way valve 19, a seventh hydraulic control one-way valve 20, a pressure sensor VII 21, a pressure sensor VIII 22, a hydraulic oil cylinder IV 23, an eighth hydraulic control one-way valve 24, a flow dividing and collecting valve I25, a ninth hydraulic control one-way valve 26, a tenth hydraulic control one-way valve 27, a manual reversing valve I28, a flow dividing and collecting valve II 29, a manual reversing valve II 30, a hydraulic oil tank 31, and an eleventh hydraulic, The manual reversing valve III 33, the twelfth hydraulic control one-way valve 34, the electromagnetic reversing valve 35, the reversing valve 36, the thirteenth hydraulic control one-way valve 37, the manual reversing valve IV 38, the fourteenth hydraulic control one-way valve 39, the overflow valve 40, the hydraulic pump 41, the one-way valve 42, the manual reversing valve V43, the fifteenth hydraulic control one-way valve 44, the sixteenth hydraulic control one-way valve 45 and the flow dividing and collecting valve III 46. The inlet of the hydraulic pump 41 is connected with the hydraulic oil tank 31, and the outlet is respectively connected with the inlet of the overflow valve 40 and the inlet of the one-way valve 42; the outlet of the overflow valve 40 is connected with an oil tank; the outlet of the one-way valve 42 is connected with the inlet of the reversing valve 36, the left control oil port of the reversing valve 36 and the P port of the electromagnetic reversing valve 35; an outlet of the reversing valve 36 and a port T of the electromagnetic reversing valve 35 are connected with the hydraulic oil tank 31, and a port A of the electromagnetic reversing valve 35 and a right control oil port of the reversing valve 36 are connected with a port P of a manual reversing valve I28, a manual reversing valve II 30, a manual reversing valve III 33, a manual reversing valve IV 38 and a manual reversing valve V43; a port T of the manual reversing valve I28 is connected with the hydraulic oil tank 31, a port A of the manual reversing valve I28 is connected with an inlet of the ninth hydraulic control one-way valve 26 and a control port of the tenth hydraulic control one-way valve 27, and a port B of the manual reversing valve I28 is connected with an inlet of the tenth hydraulic control one-way valve 27 and a control port of the ninth hydraulic control one-way valve 26; an outlet of the ninth hydraulic control one-way valve 26 is connected with a small cavity oil inlet of the hydraulic oil cylinder IV 23; an outlet of the tenth hydraulic control one-way valve 27 is connected with a large cavity oil inlet of the hydraulic oil cylinder IV 23; a port T of the manual reversing valve III 33 is connected with the hydraulic oil tank 31, a port A of the manual reversing valve III 33 is connected with an inlet of a twelfth hydraulic control one-way valve 34 and a control port of the eleventh hydraulic control one-way valve 32, and a port B of the manual reversing valve III 33 is connected with an inlet of the eleventh hydraulic control one-way valve 32 and a control port of the twelfth hydraulic control one-way valve 34; an outlet of the eleventh hydraulic control one-way valve 32 is connected with a large cavity oil inlet of the hydraulic oil cylinder II 15; an outlet of the twelfth hydraulic control one-way valve 34 is connected with a small cavity oil inlet of the hydraulic oil cylinder II 15; a port T of the manual reversing valve IV 38 is connected with the hydraulic oil tank 31, a port A of the manual reversing valve IV 38 is connected with an inlet of a thirteenth pilot-controlled one-way valve 37 and a control port of a fourteenth pilot-controlled one-way valve 39, and a port B of the manual reversing valve IV 38 is connected with an inlet of the fourteenth pilot-controlled one-way valve 39 and a control port of the thirteenth pilot-controlled one-way valve 37; an outlet of the thirteenth hydraulic control one-way valve 37 is connected with a small cavity oil inlet of the hydraulic oil cylinder III 14; an outlet of the fourteenth hydraulic control one-way valve 39 is connected with an oil inlet of a large cavity of the hydraulic oil cylinder III 14; a port T of the manual reversing valve V43 is connected with the hydraulic oil tank 31, a port A of the manual reversing valve V43 is connected with an inlet of a fifteenth hydraulic control one-way valve 44 and a control port of a sixteenth hydraulic control one-way valve 45, and a port B of the manual reversing valve V43 is connected with an inlet of the fifteenth hydraulic control one-way valve 45 and a control port of the sixteenth hydraulic control one-way valve 44; a port T of the manual reversing valve II 30 is connected with a hydraulic oil tank 31, a port A of the manual reversing valve II 30 is connected with a port P of a flow distributing and collecting valve II 29, and a port B of the manual reversing valve II 30 is connected with an inlet of a second hydraulic control one-way valve 9, an inlet of a fourth hydraulic control one-way valve 11, an inlet of a fifth hydraulic control one-way valve 18, an inlet of a seventh hydraulic control one-way valve 20, a control port of a first hydraulic control one-way valve 8, a control port of a third hydraulic control one-way valve 10, a control port of a sixth hydraulic control one-way valve 19 and a control port of an eighth hydraulic control one-way valve 24; the port A of the flow distributing and collecting valve II 29 is connected with the port P of the flow distributing and collecting valve III 46, and the port B of the flow distributing and collecting valve II 29 is connected with the port P of the flow distributing and collecting valve I25; the port A of the flow collecting valve I25 is connected with an inlet of a sixth hydraulic control one-way valve 19 and a control port of a fifth hydraulic control one-way valve 18, and the port B of the flow collecting valve I25 is connected with an inlet of an eighth hydraulic control one-way valve 24 and a control port of a seventh hydraulic control one-way valve 20; an outlet of the sixth hydraulic control one-way valve 19 is connected with a large cavity oil inlet of the hydraulic oil cylinder II 15, an outlet of the eighth hydraulic control one-way valve 24 is connected with a large cavity oil inlet of the hydraulic oil cylinder IV 23, an outlet of the fifth hydraulic control one-way valve 18 is connected with a small cavity oil inlet of the hydraulic oil cylinder II 15, and an outlet of the seventh hydraulic control one-way valve 20 is connected with a small cavity oil inlet of the hydraulic oil cylinder IV 23; and a port A of the flow distribution and collection valve III 46 is connected with an inlet of the first hydraulic control one-way valve 8 and a control port of the second hydraulic control one-way valve 9, and a port B of the flow distribution and collection valve III 46 is connected with an inlet of the third hydraulic control one-way valve 10 and a control port of the fourth hydraulic control one-way valve 11. An outlet of the first hydraulic control one-way valve 8 is connected with a large cavity oil inlet of the hydraulic oil cylinder I5, an oil outlet of the second hydraulic control one-way valve 9 is connected with a small cavity oil inlet of the hydraulic oil cylinder I5, an outlet of the third hydraulic control one-way valve 10 is connected with a large cavity oil inlet of the hydraulic oil cylinder III 14, and an outlet of the fourth hydraulic control one-way valve 11 is connected with a small cavity oil inlet of the hydraulic oil cylinder III 14; a pressure sensor I6 is installed at a large cavity oil inlet of the hydraulic oil cylinder I5, and a pressure sensor II 7 is installed at a small cavity oil inlet of the hydraulic oil cylinder I5; a pressure sensor III 12 is arranged at an oil inlet of a large cavity of a hydraulic oil cylinder III 14, a pressure sensor IV 13 is arranged at an oil inlet of a small cavity of the hydraulic oil cylinder III 14, a pressure sensor VI 17 is arranged at an oil inlet of a large cavity of a hydraulic oil cylinder II 15, and a pressure sensor V16 is arranged at an oil inlet of a small cavity of the hydraulic oil cylinder II 15; and a pressure sensor VIII 22 is arranged at an oil inlet of a large cavity of the hydraulic oil cylinder IV 23, and a pressure sensor VII 21 is arranged at an oil inlet of a small cavity of the hydraulic oil cylinder IV 23.
It should be noted that (1), the electromagnetic directional valve 35 is a two-position three-way directional valve, the left position P port and the port a are communicated, and the port T is closed; the right T port is communicated with the A port, and the P port is closed; wherein the right position is a power-off working position.
(2) The reversing valve 36 is a hydraulic control two-position two-way normally closed reversing valve, the left position is normally open, and the right position is normally closed.
(3) The manual reversing valve I28, the manual reversing valve II 30, the manual reversing valve III 33, the manual reversing valve IV 38 and the manual reversing valve V43 are Y-shaped three-position four-way reversing valves, a left-position port P is communicated with a port B, and a port A is communicated with a port T; the right port P is communicated with the port A, and the port B is communicated with the port T.
By adopting the scheme, when the front tilting moment test is carried out, the hydraulic oil cylinder I5, the hydraulic oil cylinder II 15, the hydraulic oil cylinder III 14 and the hydraulic oil cylinder IV 23 are controlled by the manual reversing valve II 30 to lift the excavator 2, the positions of the hydraulic oil cylinders are finely adjusted by adjusting the manual reversing valve I28, the manual reversing valve III 33, the manual reversing valve IV 38 and the manual reversing valve V43, the excavator 2 is adjusted to be horizontal according to the tilt sensor 1, the excavator posture is adjusted to the tilting moment test posture when the stroke of the oil cylinder does not reach the tail end, the pressure reading P1 of the pressure sensor I6, the pressure reading P2 of the pressure sensor II 7, the pressure reading P3 of the pressure sensor III 12, the pressure reading P4 of the pressure sensor IV 13, the pressure reading P5 of the pressure sensor V16, the pressure reading P6 of the pressure sensor VI 17, the pressure reading P7 of the pressure sensor VII 21 and the pressure reading P8 of the pressure sensor VIII, and the distances from a hydraulic oil cylinder I5, a hydraulic oil cylinder II 15, a hydraulic oil cylinder III 14 and a hydraulic oil cylinder IV 23 to a tipping line are measured and respectively L1, L2, L3 and L4, the pressure-bearing area of a large cavity piston of the hydraulic oil cylinder is S1, the pressure-bearing area of a small cavity piston of the hydraulic oil cylinder is S2, the tipping force is F, and the distance from the tipping force to the tipping line is L.
Mt＝F×L＝M1+M2+M3+M4
M1＝(P1×S1-P2×S2)×L1
M2＝(P6×S1-P5×S2)×L2
M3＝(P3×S1-P4×S2)×L3
M4＝(P8×S1-P7×S2)×L4
Wherein: mt is the moment of tipping under the attitude
M1 is the moment generated by hydraulic cylinder I relative to the tipping line.
M2 is the moment generated by hydraulic cylinder II relative to the tipping line.
M3 is the moment generated by hydraulic ram iii against the tip line.
M2 is the moment generated by hydraulic ram iv against the tip line.
Therefore, the utility model has the characteristics of control simply, require low, the hydro-cylinder can independently finely tune, the cost of manufacture low to hydraulic system cleanliness.
Finally, it should be noted that the above embodiments are only used for illustrating the technical solutions of the present invention and not for limiting the same; although the present invention has been described in detail with reference to preferred embodiments, it should be understood by those skilled in the art that: the invention can be modified or equivalent substituted for some technical features; without departing from the spirit of the present invention, it should be understood that the scope of the claims is intended to cover all such modifications and variations.
Claims (10)
1. A hydraulic system for a tipping moment test of an excavator comprises a hydraulic pump and a hydraulic oil tank; the method is characterized in that: the hydraulic system also comprises a hydraulic oil cylinder I, a hydraulic oil cylinder II, a hydraulic oil cylinder III and a hydraulic oil cylinder IV;
the hydraulic oil cylinders I, II, III and IV are connected with a manual reversing valve II, and four oil cylinders are controlled by the manual reversing valve II to lift the excavator during testing;
the hydraulic oil cylinder I is connected with the manual reversing valve V, the hydraulic oil cylinder II is connected with the manual reversing valve III, the hydraulic oil cylinder III is connected with the manual reversing valve IV, and the hydraulic oil cylinder IV is connected with the manual reversing valve I;
pressure sensors are arranged at the large cavity oil inlet of the hydraulic oil cylinder I, the hydraulic oil cylinder II, the hydraulic oil cylinder III and the hydraulic oil cylinder IV, and pressure sensors are arranged at the small cavity oil inlet of the hydraulic oil cylinder I, the hydraulic oil cylinder II, the hydraulic oil cylinder III and the hydraulic oil cylinder IV;
the position of a hydraulic cylinder is finely adjusted by adjusting a manual reversing valve I, a manual reversing valve III, a manual reversing valve IV and a manual reversing valve V, so that the posture of the excavator is adjusted to a tipping moment testing posture, pressure data of each pressure sensor is recorded, the distance from the hydraulic cylinder I, the hydraulic cylinder II, the hydraulic cylinder III and the hydraulic cylinder IV to a tipping line is measured, the force borne by each hydraulic cylinder is calculated according to the pressure data and parameters of the hydraulic cylinders, and the tipping moment of the excavator under the posture is calculated according to the distance of each hydraulic cylinder relative to the tipping line.
2. The hydraulic system for excavator rollover moment testing as set forth in claim 1, wherein: a port T of the manual reversing valve I is connected with a hydraulic oil tank, a port A of the manual reversing valve I is connected with an inlet of a ninth hydraulic control one-way valve and a control port of a tenth hydraulic control one-way valve, and a port B of the manual reversing valve I is connected with an inlet of the tenth hydraulic control one-way valve and a control port of the ninth hydraulic control one-way valve; an outlet of the ninth hydraulic control one-way valve is connected with a small cavity oil inlet of a hydraulic oil cylinder IV; and an outlet of the tenth hydraulic control one-way valve is connected with an oil inlet of a large cavity of the hydraulic oil cylinder IV.
3. The hydraulic system for excavator rollover moment testing as set forth in claim 1, wherein: a port T of the manual reversing valve III is connected with a hydraulic oil tank, a port A of the manual reversing valve III is connected with an inlet of a twelfth hydraulic control one-way valve and a control port of the eleventh hydraulic control one-way valve, and a port B of the manual reversing valve III is connected with an inlet of the eleventh hydraulic control one-way valve and a control port of the twelfth hydraulic control one-way valve; an outlet of the eleventh hydraulic control one-way valve is connected with a large cavity oil inlet of the hydraulic oil cylinder II; and an outlet of the twelfth hydraulic control one-way valve is connected with a small cavity oil inlet of the hydraulic oil cylinder II.
4. The hydraulic system for excavator rollover moment testing as set forth in claim 1, wherein: a port T of the manual reversing valve IV is connected with a hydraulic oil tank, a port A of the manual reversing valve IV is connected with an inlet of a thirteenth hydraulic control one-way valve and a control port of a fourteenth hydraulic control one-way valve, and a port B of the manual reversing valve IV is connected with an inlet of the fourteenth hydraulic control one-way valve and a control port of the thirteenth hydraulic control one-way valve; an outlet of the thirteenth hydraulic control one-way valve is connected with a small cavity oil inlet of the hydraulic oil cylinder III; and an outlet of the fourteenth hydraulic control one-way valve is connected with an oil inlet of a large cavity of the hydraulic oil cylinder III.
5. The hydraulic system for excavator rollover moment testing as set forth in claim 1, wherein: and a port T of the manual reversing valve V is connected with a hydraulic oil tank, a port A of the manual reversing valve V is connected with an inlet of a fifteenth hydraulic control one-way valve and a control port of a sixteenth hydraulic control one-way valve, and a port B of the manual reversing valve V is connected with an inlet of the fifteenth hydraulic control one-way valve and a control port of the sixteenth hydraulic control one-way valve.
6. The hydraulic system for excavator rollover moment testing as set forth in claim 1, wherein: and a port T of the manual reversing valve II is connected with a hydraulic oil tank, a port A of the manual reversing valve II is connected with a port P of the flow dividing and collecting valve II, and a port B of the manual reversing valve II is connected with an inlet of the second hydraulic control one-way valve, an inlet of the fourth hydraulic control one-way valve, an inlet of the fifth hydraulic control one-way valve, an inlet of the seventh hydraulic control one-way valve, a control port of the first hydraulic control one-way valve, a control port of the third hydraulic control one-way valve, a control port of the sixth hydraulic control one-way valve and a control port of the eighth.
7. The hydraulic system for excavator rollover moment testing as set forth in claim 6, wherein: the port A of the flow distributing and collecting valve II is connected with the port P of the flow distributing and collecting valve III, and the port B of the flow distributing and collecting valve II is connected with the port P of the flow distributing and collecting valve I; the port A of the flow collecting valve I is connected with an inlet of a sixth hydraulic control one-way valve and a control port of a fifth hydraulic control one-way valve, and the port B of the flow collecting valve I is connected with an inlet of an eighth hydraulic control one-way valve and a control port of a seventh hydraulic control one-way valve; an outlet of the sixth hydraulic control one-way valve is connected with a large cavity oil inlet of the hydraulic oil cylinder II, an outlet of the eighth hydraulic control one-way valve is connected with a large cavity oil inlet of the hydraulic oil cylinder IV, an outlet of the fifth hydraulic control one-way valve is connected with a small cavity oil inlet of the hydraulic oil cylinder II, and an outlet of the seventh hydraulic control one-way valve is connected with a small cavity oil inlet of the hydraulic oil cylinder IV; and the port A of the flow distributing and collecting valve III is connected with the inlet of the first hydraulic control one-way valve and the control port of the second hydraulic control one-way valve, and the port B of the flow distributing and collecting valve III is connected with the inlet of the third hydraulic control one-way valve and the control port of the fourth hydraulic control one-way valve.
8. The hydraulic system for excavator rollover moment testing as set forth in claim 1, wherein: a pressure sensor I is arranged at an oil inlet of a large cavity of the hydraulic oil cylinder I, and a pressure sensor II is arranged at an oil inlet of a small cavity of the hydraulic oil cylinder I; a pressure sensor III is arranged at an oil inlet of a large cavity of the hydraulic oil cylinder III, and a pressure sensor IV is arranged at an oil inlet of a small cavity of the hydraulic oil cylinder III; a pressure sensor VI is arranged at an oil inlet of a large cavity of the hydraulic oil cylinder II, and a pressure sensor V is arranged at an oil inlet of a small cavity of the hydraulic oil cylinder II; and an oil inlet of a large cavity of the hydraulic oil cylinder IV is provided with a pressure sensor VIII, and an oil inlet of a small cavity of the hydraulic oil cylinder IV is provided with a pressure sensor VII.
9. The hydraulic system for excavator rollover moment testing as set forth in claim 1, wherein: the inlet of the hydraulic pump is connected with a hydraulic oil tank, and the outlet of the hydraulic pump is respectively connected with the inlet of an overflow valve and the inlet of a one-way valve; the outlet of the overflow valve is connected with an oil tank; the outlet of the one-way valve is connected with the inlet of the reversing valve, the left control oil port of the reversing valve and the P port of the electromagnetic reversing valve; the outlet of the reversing valve and the T port of the electromagnetic reversing valve are connected with a hydraulic oil tank, and the A port of the electromagnetic reversing valve and the right control oil port of the reversing valve are connected with the P ports of a manual reversing valve I, a manual reversing valve II, a manual reversing valve III, a manual reversing valve IV and a manual reversing valve V.
10. The hydraulic system for excavator rollover moment testing as set forth in claim 1, wherein: the manual reversing valve I, the manual reversing valve II, the manual reversing valve III, the manual reversing valve IV and the manual reversing valve V are Y-shaped three-position four-way reversing valves, a left-position port P is communicated with a port B, and a port A is communicated with a port T; the right port P is communicated with the port A, and the port B is communicated with the port T.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922082882.1U CN210949326U (en) | 2019-11-27 | 2019-11-27 | Hydraulic system for tipping moment test of excavator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922082882.1U CN210949326U (en) | 2019-11-27 | 2019-11-27 | Hydraulic system for tipping moment test of excavator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN210949326U true CN210949326U (en) | 2020-07-07 |
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ID=71389992
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201922082882.1U Active CN210949326U (en) | 2019-11-27 | 2019-11-27 | Hydraulic system for tipping moment test of excavator |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN210949326U (en) |
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2019
- 2019-11-27 CN CN201922082882.1U patent/CN210949326U/en active Active
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