CN102155447B - Rotating hydraulic system of crane and rotating buffer valve thereof - Google Patents
Rotating hydraulic system of crane and rotating buffer valve thereof Download PDFInfo
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- CN102155447B CN102155447B CN 201110061805 CN201110061805A CN102155447B CN 102155447 B CN102155447 B CN 102155447B CN 201110061805 CN201110061805 CN 201110061805 CN 201110061805 A CN201110061805 A CN 201110061805A CN 102155447 B CN102155447 B CN 102155447B
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Abstract
The invention discloses a rotating buffer valve which comprises a first back pressure valve, a second back pressure valve and a buffer reversing valve, at the moment of the start and stop of the rotation, hydraulic oil only can enter a rotating motor through a passageway which is provided with the back pressure valve, and then flows to an oil tank; and when in a steady rotating process, the hydraulic oil enters the rotating motor from the buffer reversing valve, then flows back the buffer reversing valve from the rotating motor, and further flows back an oil back tank. At the moment of the start and stop of the rotation, the hydraulic oil only can flow from the first back pressure valve and the second back pressure valve, thus the flow rate and pressure of the hydraulic oil can be controlled effectively, instant system high pressure caused by the instant start and stop of the rotation can be eliminated, the stability of rotation can be improved, and the aim of buffer can be achieved; and during the rotating process, the hydraulic oil can directly enter the rotating motor to work from the buffer reversing valve, thus the rotating efficiency can be improved. The invention also provides a rotating hydraulic system of a crane of the rotating buffer valve.
Description
Technical field
The present invention relates to technical field of engineering machinery, particularly a kind of rotary buffering valve.The invention still further relates to a kind of hydraulic system of crane that comprises above-mentioned rotary buffering valve.
Background technique
Along with the development of construction machinery industry, car load lifting weight and the lifting altitude of hoist increase gradually, and performance promotes gradually.
Take wheeled crane as example, wheeled crane for large tonnage, its arm is long, weight is large, and when car load turned round, the revolution moment of inertia was larger, cause turnability relatively poor, if take closed model pump control HYDRAULIC CONTROL SYSTEM car load revolution, the fine motion of this system, travelling comfort are better, but cost is higher, especially for medium tonnage wheeled crane, adopt the closed rotary system significantly to increase production cost.
Please refer to Fig. 1, Fig. 1 is a kind of hydraulic diagram of typical rotary buffering valve.
in prior art, the common open type Hydraulic slewing system of main employing, namely adopt common gear pump to add the revolution trimmer valve, as shown in Figure 1, this rotary buffering valve is comprised of four one-way valves and a leading type electricity proportional pressure-reducing valve 50, valve body the 3rd hydraulic fluid port C3 and the 4th hydraulic fluid port C4 are communicated with two hydraulic fluid ports of rotary motor D respectively, during the revolution of car load forward, the first hydraulic fluid port C1 of valve body be connected hydraulic fluid port C2 and be connected with fuel tank with the oil outlet of rotary pump respectively, during the car load reversed turning, the first hydraulic fluid port C1 of valve body be connected hydraulic fluid port C2 and be connected respectively oil outlet with fuel tank with rotary pump and be connected.The pilot port of leading type electricity proportional pressure-reducing valve 50 is obtained guide oil from valve inner, control the openings of sizes of main valve according to valve inner pressure, during revolution, system pressure is too high, partial pressure oil can be via the first one-way valve 10 or the second one-way valve 20, and leading type electricity proportional pressure-reducing valve 50 flows back to fuel tank, thereby plays rotating buffer function.The 3rd one-way valve 30 and the 4th one-way valve 40 below rotary buffering valve have the repairing function when revolution stops.
This rotary buffering valve is made of one-way valve and electric proportional pressure-reducing valve 50, and the stability that starts and stop moment in revolution is not enough, and especially for the hoist of large tonnage, because the revolution moment of inertia is larger, this rotary buffering valve can't satisfy the stationarity of rotary system.
Therefore, how improving a kind of rotary buffering valve with higher stability is those skilled in the art's technical issues that need to address.
Summary of the invention
The purpose of this invention is to provide a kind of rotary buffering valve, this rotary buffering valve makes revolution have stability preferably, and can improve revolution efficient.Another object of the present invention is to provide a kind of hydraulic system of crane that comprises above-mentioned rotary buffering valve.
For solving the problems of the technologies described above, the invention provides a kind of rotary buffering valve, have the first hydraulic fluid port, the second hydraulic fluid port, the 3rd hydraulic fluid port and the 4th hydraulic fluid port on its valve body, and be provided with in its valve body:
The buffering selector valve, in the first working position, its first hydraulic fluid port and the 3rd hydraulic fluid port conducting, the second hydraulic fluid port and the 4th hydraulic fluid port conducting, in the second working position, its first hydraulic fluid port, the second hydraulic fluid port, the 3rd hydraulic fluid port and the 4th hydraulic fluid port all disconnect; The first hydraulic fluid port of described buffering selector valve and the second hydraulic fluid port are communicated with the first hydraulic fluid port and second hydraulic fluid port of described valve body respectively; The 3rd hydraulic fluid port of described buffering selector valve and the 4th hydraulic fluid port are communicated with the 3rd hydraulic fluid port and the 4th hydraulic fluid port of described valve body respectively;
The first back pressure valve and the second back pressure valve, described the first back pressure valve and described buffering selector valve are parallel on the path of the first hydraulic fluid port of described valve body and described the 3rd hydraulic fluid port, and described the second back pressure valve and described buffering selector valve are parallel on the path of the second hydraulic fluid port of described valve body and the 4th hydraulic fluid port.
Preferably, the first electric proportional pressure-reducing valve and the second electric proportional pressure-reducing valve also are set in described valve body, described the first back pressure valve and described the second back pressure valve are the hydraulic-control throttling valve, and the pilot port of described the first back pressure valve and described the second back pressure valve is communicated with the oil outlet of the described first electric proportional pressure-reducing valve and described the second electric proportional pressure-reducing valve respectively.
Preferably, the 3rd electric proportional pressure-reducing valve is set also in described valve body, described buffering selector valve is pilot operated directional control valve, and the pilot port of described buffering selector valve is communicated with the oil outlet of described the 3rd electric proportional pressure-reducing valve.
Preferably, slewing directional control valve also is set in described valve body, in the first working position, its first hydraulic fluid port and the 3rd hydraulic fluid port conducting, the second hydraulic fluid port and the 4th hydraulic fluid port conducting, in the second working position, its first hydraulic fluid port and the 4th hydraulic fluid port conducting, the second hydraulic fluid port and the 3rd hydraulic fluid port conducting; The first hydraulic fluid port of described slewing directional control valve and the second hydraulic fluid port are communicated with the first hydraulic fluid port and second hydraulic fluid port of described valve body respectively, the first hydraulic fluid port of the 3rd hydraulic fluid port of described slewing directional control valve and described the first back pressure valve and described buffering selector valve is communicated with, and the second hydraulic fluid port of the 4th hydraulic fluid port of described slewing directional control valve and described the second back pressure valve and described buffering selector valve is communicated with.
Preferably, described slewing directional control valve is in the 3rd working position, and its first hydraulic fluid port and the second hydraulic fluid port all are communicated with the second hydraulic fluid port of described valve body, and described the second hydraulic fluid port is return opening.
Preferably, the 4th electric proportional pressure-reducing valve and the 5th electric proportional pressure-reducing valve also are set in described valve body, described slewing directional control valve is pilot operated directional control valve, and two pilot port of described slewing directional control valve are communicated with the oil outlet of the described the 4th electric proportional pressure-reducing valve and described the 5th electric proportional pressure-reducing valve respectively.
Preferably, described valve body also has control port, and the filler opening of the described first electric proportional pressure-reducing valve, the described second electric proportional pressure-reducing valve, the described the 3rd electric proportional pressure-reducing valve, the described the 4th electric proportional pressure-reducing valve and described the 5th electric proportional pressure-reducing valve all is communicated with described control port.
Preferably, be equipped with the first liquid resistance on the path of the oil outlet of the described the 4th electric proportional pressure-reducing valve and described the 5th electric proportional pressure-reducing valve and described slewing directional control valve pilot port.
Preferably, relief valve is set also in described valve body, the filler opening of described relief valve and oil outlet are communicated with respectively the 3rd hydraulic fluid port and the 4th hydraulic fluid port of described valve body.
Preferably, the precursor overflow valve of main relief valve and the described main relief valve pilot pressure of control is set also in described valve body, the filler opening of described main relief valve and oil outlet are communicated with the first hydraulic fluid port and second hydraulic fluid port of described valve body respectively.
Preferably, be provided with the second liquid resistance between the filler opening of the filler opening of described main relief valve and described precursor overflow valve.
Preferably, the feedback oil circuit of the 3rd hydraulic fluid port to the four hydraulic fluid ports of described valve body is provided with the 3rd liquid resistance.
Rotary buffering valve provided by the present invention comprises the first back pressure valve, the second back pressure valve and buffering selector valve, start moment in revolution, make the buffering selector valve be in the first working position, hydraulic oil only can enter rotary motor by the path that is provided with the first back pressure valve, again from rotary motor second back pressure valve of flowing through, then flow to fuel tank; When being in stable turning course, make the buffering selector valve be in the second working position, the conducting of buffering selector valve, because there is preset pressure in the first back pressure valve, hydraulic oil is selected from cushioning the selector valve rotary motor of flowing through, then flows back to the buffering selector valve from rotary motor, and then flows back to fuel tank; When revolution stops, again making the buffering selector valve be in the first working position, identical when the loop of hydraulic oil starts with revolution.During reversed turning, reversed turning starts to turning round in stopped process hydraulic oil fundamental circuit and the rotating process of above-mentioned forward just the opposite.This changes and turns trimmer valve in the revolution startup and turn round the moment that stops, hydraulic oil only can pass through from the first back pressure valve and the second back pressure valve, thereby can effectively control flow and the pressure of hydraulic oil, eliminate revolution startup and revolution and stop the instantaneous system high pressure that moment causes, promote rotating stability, reach the purpose of buffering; And in rotating process, hydraulic oil can directly enter rotary motor work from cushioning selector valve, thereby improves revolution efficient.
The present invention also provides a kind of hydraulic system of crane, comprises rotary pump, rotary motor and rotary buffering valve, and described rotary buffering valve is the described rotary buffering valve of above-mentioned any one.
Because above-mentioned rotary buffering valve has above-mentioned technique effect, the hydraulic system of crane with above-mentioned rotary buffering valve also has identical technique effect.
Description of drawings
Fig. 1 is a kind of hydraulic diagram of typical rotary buffering valve;
Fig. 2 is the hydraulic diagram of a kind of embodiment of rotary buffering valve provided by the present invention;
Fig. 3 is the hydraulic diagram of the another kind of embodiment of rotary buffering valve provided by the present invention.
Embodiment
Core of the present invention is to provide a kind of rotary buffering valve, and this rotary buffering valve makes revolution have stability preferably, and can improve revolution efficient.Another core of the present invention is to provide a kind of hydraulic system of crane that comprises above-mentioned rotary buffering valve.
In order to make those skilled in the art understand better technological scheme of the present invention, the present invention is described in further detail below in conjunction with the drawings and specific embodiments.
Please refer to Fig. 2, Fig. 2 is the hydraulic diagram of a kind of embodiment of rotary buffering valve provided by the present invention.
Have the first hydraulic fluid port B1, the second hydraulic fluid port A1, the 3rd hydraulic fluid port A and the 4th hydraulic fluid port B on the valve body of the rotary buffering valve in this embodiment, the 3rd hydraulic fluid port A and the 4th hydraulic fluid port B are communicated with the hydraulic fluid port of revolution executive component, and the 3rd hydraulic fluid port A shown in Fig. 2 and the 4th hydraulic fluid port B are communicated with the both sides hydraulic fluid port of executive component rotary motor 15; Also be provided with buffering selector valve 3, the first back pressure valve 1 and the second back pressure valve 2 in valve body.
The first back pressure valve 1 and the second back pressure valve 2, the first back pressure valve 1 and buffering selector valve 3 are parallel on the path of the first hydraulic fluid port B1 of valve body and the 3rd hydraulic fluid port A, the second back pressure valve 2 and buffering selector valve 3 are parallel on the path of the 3rd hydraulic fluid port A of valve body and the 4th hydraulic fluid port B, be that valve body the first hydraulic fluid port B1 and the 3rd hydraulic fluid port A, the second hydraulic fluid port and the 4th hydraulic fluid port B both can be communicated with by buffering selector valve 3, also can be communicated with by the path that back pressure valve is set.
during the forward revolution, start moment in revolution, the hydraulic oil of rotary motive power element enters from the first hydraulic fluid port B1 of valve body, make buffering selector valve 3 be in the first working position, namely be in the left position shown in Fig. 2, because left position is obstructed, hydraulic oil can't certainly cushion selector valve 3 and flow out, only can enter by the path that is provided with the first back pressure valve 1 the left side hydraulic fluid port (take Fig. 2 as the visual angle) of rotary motor 15, flow out from the right side of rotary motor 15 hydraulic fluid port again, flow through after the second back pressure valve 2, flow to again the second hydraulic fluid port A1 of valve body, this moment, the second hydraulic fluid port A1 of valve body was return opening, the first hydraulic fluid port B1 is filler opening, when being in stable turning course, make buffering selector valve 3 be in the second working position, namely be in the right position shown in Fig. 2,3 conductings of buffering selector valve, because there is preset pressure in the first back pressure valve 1, hydraulic oil is selected from cushioning the selector valve 3 left side hydraulic fluid port of rotary motor 15 of flowing through, then flows back to buffering selector valve 3 from the right side of rotary motor 15 hydraulic fluid port, and then flows out the second hydraulic fluid port A1 as the valve body of return opening, when revolution stops, again making buffering selector valve 3 be in the first working position, identical when the loop of hydraulic oil starts with revolution, be not repeated herein.During reversed turning, hydraulic oil enters from the second hydraulic fluid port A1 of valve body, and the first hydraulic fluid port B1 of valve body is as return opening, and reversed turning starts to turning round in stopped process hydraulic oil fundamental circuit and the rotating process of above-mentioned forward just the opposite, can be with reference to understanding.
This changes and turns trimmer valve in the revolution startup and turn round the moment that stops, hydraulic oil only can pass through from the first back pressure valve 1 and the second back pressure valve 2, thereby can effectively control flow and the pressure of hydraulic oil, eliminate revolution startup and revolution and stop the instantaneous system high pressure that moment causes, promote rotating stability, reach the purpose of buffering; And in rotating process, hydraulic oil can directly enter rotary motor 15 work from cushioning selector valve 3, thereby improves revolution efficient.
The first electric proportional pressure-reducing valve 4 and the second electric proportional pressure-reducing valve 5 can also be set in valve body, the first back pressure valve 1 and the second back pressure valve 2 are the hydraulic-control throttling valve, throttle valve can effectively be controlled hydraulic fluid flow rate and produce back pressure to system, and the pilot port of the first back pressure valve 1 and the second back pressure valve 2 is communicated with the oil outlet of the first electric proportional pressure-reducing valve 4 and the second electric proportional pressure-reducing valve 5 respectively.The electricity proportional pressure-reducing valve can provide according to the electrical signal of input size adjustable constant working pressure continuously, pari passu, thereby can accurately control according to actual needs the valve port opening degree of two back pressure valves, satisfies the fine motion requirement of operation.
The 3rd electric proportional pressure-reducing valve 6 also can be set in valve body, and buffering selector valve 3 adopts pilot operated directional control valve, and the pilot port that cushions selector valve 3 is communicated with the oil outlet of the 3rd electric proportional pressure-reducing valve 6, can improve equally the fine motion of operation.
Please refer to Fig. 3, Fig. 3 is the hydraulic diagram of the another kind of embodiment of rotary buffering valve provided by the present invention.
In this embodiment, slewing directional control valve 11 can be set in valve body, being about to slewing directional control valve 11 is integrated in the rotary buffering valve valve body, slewing directional control valve 11 has at least two working positions, in the first working position, and its first hydraulic fluid port and the 3rd hydraulic fluid port conducting, the second hydraulic fluid port and the 4th hydraulic fluid port conducting, left position as shown in Figure 3, in the second working position, its first hydraulic fluid port and the 4th hydraulic fluid port conducting, the second hydraulic fluid port and the 3rd hydraulic fluid port conducting, right position as shown in Figure 3; The first hydraulic fluid port of slewing directional control valve 11 and the second hydraulic fluid port are communicated with the first hydraulic fluid port B1 and the second hydraulic fluid port A1 of valve body respectively, because the revolution commutation function realizes in the valve body of rotary buffering valve, the first hydraulic fluid port B1 and the second hydraulic fluid port A1 of valve body are respectively filler opening and return opening; The first hydraulic fluid port of the 3rd hydraulic fluid port of slewing directional control valve 11 and the first back pressure valve 1 and buffering selector valve 3 is communicated with, the second hydraulic fluid port of the 4th hydraulic fluid port of slewing directional control valve 11 and the second back pressure valve 2 and buffering selector valve 3 is communicated with, and namely two back pressure valves and buffering selector valve 3 are all by slewing directional control valve 11 oil-feeds or oil return.Slewing directional control valve 11 is in left position namely during the first working position, hydraulic oil enters the left side hydraulic fluid port of rotary motor 15 through the first back pressure valve 1 or buffering selector valve 3, then is back to fuel tank through the right side of rotary motor 15 hydraulic fluid port, the second back pressure valve 2 or buffering selector valve 3, slewing directional control valve 11; Slewing directional control valve 11 is in right position namely during the second working position, and hydraulic oil flows into the left side hydraulic fluid port from the right side of rotary motor 15 hydraulic fluid port, realizes the change of gyratory directions.Hydraulic oil is same as the previously described embodiments through the control of back pressure valve or buffering selector valve 3, is not repeated herein.
Can adopt the slewing directional control valve 11 of three, be that slewing directional control valve 11 also has the 3rd working position, in the 3rd working position, its first hydraulic fluid port and the second hydraulic fluid port all are communicated with the second hydraulic fluid port A1 as the valve body of return opening, as shown in Figure 3, when slewing directional control valve 11 was in meta, its first hydraulic fluid port and the second hydraulic fluid port all were communicated with the second hydraulic fluid port A1 of valve body.When revolution stops, when rotary motor 15 quits work, make 11 times metas of slewing directional control valve under the break effect, the hydraulic oil of system can be back to fuel tank from return opening, thus the impact when reducing rotary braking further improves the stability that revolution is controlled.
Similar with buffering selector valve 3, the 4th electric proportional pressure-reducing valve 12 and the 5th electric proportional pressure-reducing valve 13 can also be set in valve body, slewing directional control valve 11 adopts pilot operated directional control valve, the slewing directional control valve 11 of three has two pilot port in left and right, two pilot port are communicated with the oil outlet of the 4th electric proportional pressure-reducing valve 12 and the 5th electric proportional pressure-reducing valve 13 respectively, during two equal no signal inputs of electric proportional pressure-reducing valve, 11 times metas of slewing directional control valve.By the commutation of electric proportional pressure-relief valve control slewing directional control valve 11, improve the fine motion of revolution operation.The 4th electric proportional pressure-reducing valve 12 and the 5th electric proportional pressure-reducing valve 13 can be taked push button, so that manual control electricity proportional pressure-reducing valve in case of emergency.
The related electric proportional pressure-reducing valve of above embodiment all can change in the valve body that turns trimmer valve certainly obtains pilot control.Preferably, rotary buffering valve can also have control port X, the filler opening of the first electric proportional pressure-reducing valve 4, the second electric proportional pressure-reducing valve 5, the 3rd electric proportional pressure-reducing valve 6, the 4th electric proportional pressure-reducing valve 12 and the 5th electric proportional pressure-reducing valve 13 all is communicated with control port X, control port X connects the external control oil sources, can carry out fuel feeding by independent external oil pump.The external control oil sources is not affected by system fluctuation, and the control that provides than own pressure oil in valve body has more superiority and flexibility, makes the control signal of electric proportional pressure-reducing valve more controlled, and the fine motion during crack mouthful of operation is better.Because inevitably there is internal leakage in hydrovalve, on valve body, drain tap Y can also be set, carry out draining for the electric proportional pressure-reducing valve in above-mentioned embodiment, the drain tap of each electric proportional pressure-reducing valve all is communicated with the drain tap Y of valve body as shown in Figure 3.
The liquid resistance can all be set on the path of the oil outlet of the 4th electric proportional pressure-reducing valve 12 and the 5th electric proportional pressure-reducing valve 13 and slewing directional control valve 11 pilot port.As shown in Figure 3, control oil through the 5th electric proportional pressure-reducing valve 13 and the first liquid resistance 14 pilot port that enter slewing directional control valve 11, the first liquid resistance 14 can make slewing directional control valve 11 obtain better pilot pressure oil of stability.
In valve body, relief valve 16 can also be set, the filler opening of relief valve 16 and oil outlet are communicated with respectively the 3rd hydraulic fluid port A and the 4th hydraulic fluid port B of valve body.Because the flow direction when the positive and negative revolution of the hydraulic oil in rotary buffering valve is opposite, therefore, as shown in Figure 3, relief valve 16 is by being set up in parallel and the first relief valve and second relief valve of overflow opposite direction form, when hydraulic oil when the first back pressure valve 1 flow to the 3rd hydraulic fluid port A, if hydraulic fluid pressure is still too high, unnecessary hydraulic oil can overflow back fuel tank by the first relief valve of bottom, equally, when hydraulic oil flow to the 4th hydraulic fluid port B through the second back pressure valve 2, unnecessary hydraulic oil can overflow back fuel tank by second relief valve on top, prevents system overload.
The precursor overflow valve 8 of main relief valve 7 and main relief valve 7 pilot pressures of control can also be set in valve body, and the filler opening of main relief valve 7 and oil outlet are communicated with the first hydraulic fluid port B1 and the second hydraulic fluid port A1 of valve body respectively.As shown in Figure 3, main relief valve 7 can adopt the three-way pressure compensating device, and namely constant difference overflow valve, when hydraulic oil enters low pressurized overflow after the three-way pressure compensating device from the first hydraulic fluid port B1 (being filler opening this moment), play a protective role to system.In addition, the second liquid resistance 10, the second liquid resistances 10 can be set between the filler opening of the filler opening of main relief valve 7 and precursor overflow valve 8 can play stabilization preferably to the three-way pressure compensating device, make the wave properties of load feedback pressure obtain good filtering.
The 3rd liquid resistance 9 also can be set on the feedback oil circuit of the 3rd hydraulic fluid port A to the four hydraulic fluid port B of valve body.As shown in Figure 3, the 3rd liquid resistance 9 can be carried out filtering with the high pressure oil that enters rotary motor 15, eliminates pressure surge, and the stability in the whole process of revolution is further promoted.
Except above-mentioned rotary buffering valve, the present invention also provides a kind of hydraulic system of crane, comprise rotary pump, rotary motor and rotary buffering valve, described rotary buffering valve is the described rotary buffering valve of above-mentioned arbitrary embodiment, and the 3rd hydraulic fluid port of rotary buffering valve and the 4th hydraulic fluid port are communicated with respectively the both sides hydraulic fluid port of rotary motor.Because the rotary buffering valve in above-described embodiment has above-mentioned technique effect, the hydraulic system of crane with above-mentioned rotary buffering valve also should have identical technique effect, is not repeated herein.
Above a kind of hydraulic system of crane provided by the present invention and rotary buffering valve thereof are described in detail.Used specific case herein principle of the present invention and mode of execution are set forth, above embodiment's explanation just is used for helping to understand method of the present invention and core concept thereof.Should be pointed out that for those skilled in the art, under the prerequisite that does not break away from the principle of the invention, can also carry out some improvement and modification to the present invention, these improvement and modification also fall in the protection domain of claim of the present invention.
Claims (13)
1. a rotary buffering valve, is characterized in that, has the first hydraulic fluid port (B1), the second hydraulic fluid port (A1), the 3rd hydraulic fluid port (A) and the 4th hydraulic fluid port (B) on its valve body, and be provided with in its valve body:
Buffering selector valve (3), in the first working position, its first hydraulic fluid port and the 3rd hydraulic fluid port conducting, the second hydraulic fluid port and the 4th hydraulic fluid port conducting, in the second working position, its first hydraulic fluid port, the second hydraulic fluid port, the 3rd hydraulic fluid port and the 4th hydraulic fluid port all disconnect; The first hydraulic fluid port of described buffering selector valve (3) and the second hydraulic fluid port are communicated with the first hydraulic fluid port (B1) and second hydraulic fluid port (A1) of described valve body respectively; The 3rd hydraulic fluid port of described buffering selector valve (3) and the 4th hydraulic fluid port are communicated with the 3rd hydraulic fluid port (A) and the 4th hydraulic fluid port (B) of described valve body respectively;
The first back pressure valve (1) and the second back pressure valve (2), described the first back pressure valve (1) and described buffering selector valve (3) are parallel on the path of first hydraulic fluid port (B1) of described valve body and described the 3rd hydraulic fluid port (A), and described the second back pressure valve (2) and described buffering selector valve (3) are parallel on the path of second hydraulic fluid port (A1) of described valve body and the 4th hydraulic fluid port (B).
2. rotary buffering valve according to claim 1, it is characterized in that, the first electric proportional pressure-reducing valve (4) and the second electric proportional pressure-reducing valve (5) also are set in described valve body, described the first back pressure valve (1) and described the second back pressure valve (2) are the hydraulic-control throttling valve, and the pilot port of described the first back pressure valve (1) and described the second back pressure valve (2) is communicated with the oil outlet of the described first electric proportional pressure-reducing valve (4) and the described second electric proportional pressure-reducing valve (5) respectively.
3. rotary buffering valve according to claim 2, it is characterized in that, the 3rd electric proportional pressure-reducing valve (6) also is set in described valve body, described buffering selector valve (3) is pilot operated directional control valve, and the pilot port of described buffering selector valve (3) is communicated with the oil outlet of the described the 3rd electric proportional pressure-reducing valve (6).
4. the described rotary buffering valve of according to claim 1 to 3 any one, it is characterized in that, slewing directional control valve (11) also is set in described valve body, in the first working position, its first hydraulic fluid port and the 3rd hydraulic fluid port conducting, the second hydraulic fluid port and the 4th hydraulic fluid port conducting, in the second working position, its first hydraulic fluid port and the 4th hydraulic fluid port conducting, the second hydraulic fluid port and the 3rd hydraulic fluid port conducting; The first hydraulic fluid port of described slewing directional control valve (11) and the second hydraulic fluid port are communicated with the first hydraulic fluid port (B1) and second hydraulic fluid port (A1) of described valve body respectively, the first hydraulic fluid port of the 3rd hydraulic fluid port of described slewing directional control valve (11) and described the first back pressure valve (1) and described buffering selector valve (3) is communicated with, and the second hydraulic fluid port of the 4th hydraulic fluid port of described slewing directional control valve (11) and described the second back pressure valve (2) and described buffering selector valve (3) is communicated with.
5. rotary buffering valve according to claim 4, it is characterized in that, described slewing directional control valve (11) is in the 3rd working position, and its first hydraulic fluid port and the second hydraulic fluid port all are communicated with second hydraulic fluid port (A1) of described valve body, and described the second hydraulic fluid port (A1) is return opening.
6. rotary buffering valve according to claim 5, it is characterized in that, the 4th electric proportional pressure-reducing valve (12) and the 5th electric proportional pressure-reducing valve (13) also are set in described valve body, described slewing directional control valve (11) is pilot operated directional control valve, and two pilot port of described slewing directional control valve (11) are communicated with the oil outlet of the described the 4th electric proportional pressure-reducing valve (12) and the described the 5th electric proportional pressure-reducing valve (13) respectively.
7. rotary buffering valve according to claim 6, it is characterized in that, described valve body also has control port (X), and the filler opening of the described first electric proportional pressure-reducing valve (4), the described second electric proportional pressure-reducing valve (5), the described the 3rd electric proportional pressure-reducing valve (6), the described the 4th electric proportional pressure-reducing valve (12) and the described the 5th electric proportional pressure-reducing valve (13) all is communicated with described control port (X).
8. rotary buffering valve according to claim 7, it is characterized in that, be equipped with the first liquid resistance (14) on the path of the oil outlet of the described the 4th electric proportional pressure-reducing valve (12) and the described the 5th electric proportional pressure-reducing valve (13) and described slewing directional control valve (11) pilot port.
9. rotary buffering valve according to claim 8, it is characterized in that, relief valve (16) also is set in described valve body, and the filler opening of described relief valve (16) and oil outlet are communicated with respectively the 3rd hydraulic fluid port (A) and the 4th hydraulic fluid port (B) of described valve body.
10. rotary buffering valve according to claim 9, it is characterized in that, the precursor overflow valve (8) of main relief valve (7) and control described main relief valve (7) pilot pressure also is set in described valve body, and the filler opening of described main relief valve (7) and oil outlet are communicated with the first hydraulic fluid port (B1) and second hydraulic fluid port (A1) of described valve body respectively.
11. rotary buffering valve according to claim 10 is characterized in that, is provided with the second liquid resistance (10) between the filler opening of the filler opening of described main relief valve (7) and described precursor overflow valve (8).
12. rotary buffering valve according to claim 11 is characterized in that, the feedback oil circuit of the 3rd hydraulic fluid port to the four hydraulic fluid ports of described valve body is provided with the 3rd liquid resistance (9).
13. a hydraulic system of crane comprises rotary pump, rotary motor and rotary buffering valve, it is characterized in that, described rotary buffering valve is the described rotary buffering valve of claim 1 to 12 any one.
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| CN 201110061805 CN102155447B (en) | 2011-03-15 | 2011-03-15 | Rotating hydraulic system of crane and rotating buffer valve thereof |
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| CN 201110061805 CN102155447B (en) | 2011-03-15 | 2011-03-15 | Rotating hydraulic system of crane and rotating buffer valve thereof |
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| CN102320520B (en) * | 2011-08-18 | 2013-05-22 | 南通润邦重机有限公司 | Wind power installation crane hydraulic control circuit |
| CN102493967A (en) * | 2011-11-21 | 2012-06-13 | 三一汽车起重机械有限公司 | Crane, rotation control system thereof and rotation buffering valve of crane |
| CN102602830B (en) * | 2012-03-06 | 2013-11-20 | 中联重科股份有限公司 | Hydraulic rotary system and engineering vehicle |
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