CN102602830B - Hydraulic rotary system and engineering vehicle - Google Patents
Hydraulic rotary system and engineering vehicle Download PDFInfo
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- CN102602830B CN102602830B CN2012100572976A CN201210057297A CN102602830B CN 102602830 B CN102602830 B CN 102602830B CN 2012100572976 A CN2012100572976 A CN 2012100572976A CN 201210057297 A CN201210057297 A CN 201210057297A CN 102602830 B CN102602830 B CN 102602830B
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Abstract
The invention discloses a hydraulic rotary system comprising a rotary variable-capacity pump, an oil replenishing loop connected to both ends of the rotary variable-capacity pump in parallel, a rotary motor which is directly communicated with the rotary variable-capacity pump, and a rotary buffering device, wherein the rotary buffering device is connected to both ends of the rotary motor in parallel, is also communicated with the oil replenishing loop and is used for buffering pressure fluctuation in the hydraulic rotary system. By adding a control valve and a vibration damping valve according to the hydraulic rotary system, the pressure fluctuation generated in the rotary process of the rotary system can be effectively eliminated, and the stability and the comfort of the operation of the rotary system are enhanced. Meanwhile, pressure oil in the hydraulic rotary system disclosed by the invention flows out of the vibration damping valve after the pressure of the system is constructed by the pressure oil through a damping component on the vibration damping valve, and also flows into an oil outlet of an oil replenishing pump. In this way, the pressure oil also enters the oil replenishing loop of the system. The problem of needing to select an oil replenishing pump with larger output volume because the oil replenishing quantity of the system is insufficient is avoided.
Description
Technical field
The present invention relates to the hydraulic efficiency pressure system field, particularly relate to a kind of Control in Hydraulic Rotation System and be equipped with the engineering truck of this system.
Background technology
Swing type mechanism, as one of important actuating unit of crane hoisting heavy, is used for driving the upper frame part do revolution action of hoisting crane.The crane rotation mechanism control system generally uses the hydraulic gyration closed system that consists of rotary pump and rotary motor at present, and rotary pump directly is connected by pipeline with rotary motor, and is middle without any control cock.This rotary system provides pressure oil by rotary pump, drives the rotary motor running, and hydraulic oil recycles in rotary pump, rotary motor and connecting line.Consider the heating of fluid and the leakage of oil pump and motor, be provided with the feed circuit that is formed by slippage pump and by pass valve in system, the leakage of fluid in the compensation hydraulic efficiency pressure system, simultaneously at the rotary motor two ends, be connected with flush valve, be used for upgrading the fluid medium, unnecessary deep fat in overflow passage, a small amount of deep fat of rotary pump and rotary motor overflow are by another pipeline through the cooling recovery fuel tank that flows back to of radiator, and slippage pump is drawn fresh oil again in the system hydraulic tubing from the repairing fuel tank.
in actual use, operating environment more complicated due to hoisting crane, the rotor inertia that gets on the bus is large, loading in the swing type mechanism turning course of lifting is subjected to external interference or framing member to make precision, the impact of the oneself factors such as assembly error and produce change, thereby cause the fluctuation of load pressure, especially starting, braking or can cause very large hydraulic efficiency impact while commutating suddenly, if rotary pump is directly controlled two or more rotary motors, when fluctuation occurs in load pressure, existing hydraulic closed rotary system is difficult to make corresponding adjustment in good time, the filtering fluctuation of pressure, the Control in Hydraulic Rotation System traveling comfort can not be guaranteed, also can be had a strong impact on the service life of Hydraulic Elements.
Simultaneously, for the large-tonnage hoisting crane, the revolution moment of inertia is larger, because rotary pump directly is connected with rotary motor, Control in Hydraulic Rotation System is not enough in the moment stability that quick gear shift stage especially starts and stops, easily produce pressure peak, make swing type mechanism produce shaking phenomenon in this process, thereby affected the traveling comfort that hoisting crane is handled.
Summary of the invention
The invention provides a kind of Control in Hydraulic Rotation System, be mainly used in solving the problem of the hydraulic system pressure fluctuation that causes due to the interference of load pressure at Control in Hydraulic Rotation System in turning course.
The present invention solves the problems of the technologies described above the technical scheme that adopts: a kind of Control in Hydraulic Rotation System is provided, described Control in Hydraulic Rotation System comprises: the revolution controllable capacity pump, be connected in parallel on the feed circuit at described revolution controllable capacity pump two ends, the rotary motor that directly is communicated with described revolution controllable capacity pump and turn round shock absorber, described revolution shock absorber is connected in parallel on the two ends of described rotary motor and with described feed circuit, is communicated with, and is used for cushioning the fluctuation of pressure of described Control in Hydraulic Rotation System; Described revolution shock absorber comprises control cock and damper valve, described control cock is used for controlling selects the high-voltage oil liquid of described Control in Hydraulic Rotation System to enter described damper valve, described damper valve is used for the amplitude of cutting down described fluctuation of pressure, make described Control in Hydraulic Rotation System steady, improve the handling of described Control in Hydraulic Rotation System.
Wherein, described damper valve comprises valve body, valve pocket, with described valve body, coordinates plug, the spool that is placed in described valve pocket and the elastomeric element that forms described valve pocket, the damper valve oil outlet with described valve pocket connection, the damper valve oil inlet that is connected with described spool, and described damper valve oil inlet is communicated with described control cock; Described spool connects described damper valve oil inlet, and described valve core inside is provided with the liquid flow channel for oil of axial perforation, and the two ends of described liquid flow channel for oil are communicated with respectively described damper valve oil inlet and described valve pocket; Wherein, high-voltage oil liquid enters described damper valve oil inlet from described control cock, and during greater than system back pressure, the pressure that acts on the high-voltage oil liquid on described damper valve promotes the described elastomeric element of described spool compression and moves towards described plug direction when load pressure.
Wherein, described control cock is shuttle valve, and described shuttle valve has two oil inlets and an oil outlet, and the oil outlet of described shuttle valve is communicated with described damper valve oil inlet.
Wherein, described control cock is two check valves, and the oil outlet of described two check valves is connected and is connected with described damper valve oil inlet together.
Wherein, described elastomeric element is Compress Spring, and an end of described Compress Spring is connected to described plug, and the other end is plugged on described spool.
Wherein, offer the passage of axial perforation on described spool, described passage is symmetrically distributed in the described liquid flow channel for oil both sides on described spool, makes the described valve pocket of being separated by described spool be connected, to keep equilibrium of pressure.
Wherein, be provided with damping piece in described liquid flow channel for oil, described damping piece quantity is at least one.
Wherein, described feed circuit comprises: slippage pump, and described slippage pump and described revolution controllable capacity pump coaxial drive, the two ends of described slippage pump are connected with the repairing safety overflow valve, and the oil outlet of described slippage pump is communicated with described damper valve oil outlet; Two repairing by pass valves, be connected to the two ends of described revolution controllable capacity pump; Oil compensation pressure by pass valve, described oil compensation pressure by pass valve are located between described repairing by pass valve and with the oil outlet of described slippage pump and are communicated with; The quantity of described rotary motor is more than one, and the two ends of described rotary motor are parallel with flush valve.
Wherein, described Control in Hydraulic Rotation System further comprise oil sump tank, the radiator that is communicated with described oil sump tank and the check valve in parallel with described radiator; Described radiator, described check valve are communicated with described revolution controllable capacity pump, described rotary motor and described flush valve respectively, are used for reclaiming the unnecessary deep fat of overflow.
The present invention also provides a kind of engineering truck, and it is equipped with above-mentioned Control in Hydraulic Rotation System.
Compared with prior art, control program of the present invention is simple, and dismounting is easy to maintenance, by increase control cock and damper valve in Control in Hydraulic Rotation System, can eliminate rotary system produces in turning course fluctuation of pressure by actv., promote stationarity and traveling comfort that rotary system is handled.
Description of drawings
In order to be illustrated more clearly in the technical scheme in the embodiment of the present invention, in below describing embodiment, the accompanying drawing of required use is briefly described, apparently, accompanying drawing in the following describes is only some embodiments of the present invention, for those of ordinary skills, under the prerequisite of not paying creative work, can also obtain other accompanying drawing according to these accompanying drawings, wherein:
Fig. 1 is the hydraulic principle schematic diagram of the Control in Hydraulic Rotation System of the embodiment of the present invention one;
Structural representation when Fig. 2 is the damper valve off working state of Control in Hydraulic Rotation System shown in Figure 1;
Structural representation when Fig. 3 is the damper valve mode of operation of Control in Hydraulic Rotation System shown in Figure 1;
Fig. 4 is the hydraulic principle schematic diagram of the Control in Hydraulic Rotation System of the embodiment of the present invention two.
The specific embodiment
Below in conjunction with the accompanying drawing in the embodiment of the present invention, the technical scheme in the embodiment of the present invention is clearly and completely described, obviously, described embodiment is only a part of embodiment of the present invention, rather than whole embodiment.Based on the embodiment in the present invention, those of ordinary skills, not making under the creative work prerequisite the every other embodiment that obtains, belong to the scope of protection of the invention.
Embodiment one,
Please refer to Fig. 1, it has shown according to the present invention the hydraulic schematic diagram of a kind of embodiment of Control in Hydraulic Rotation System.This Control in Hydraulic Rotation System comprises: revolution controllable capacity pump 10, be connected in parallel on the feed circuit at revolution controllable capacity pump 10 two ends, with the revolution rotary motor 11 that directly is communicated with of controllable capacity pump 10 and turn round shock absorber, the quantity of rotary motor 11 is more than one, the two ends of rotary motor 11 are parallel with flush valve 110, the revolution shock absorber is connected in parallel on the two ends of rotary motor 11 and with feed circuit, is communicated with, and is used for the fluctuation of pressure of buffering hydraulic rotary system.Wherein, feed circuit comprises slippage pump 12 and oil compensation pressure by pass valve 13, slippage pump 12 and revolution controllable capacity pump 10 coaxial drive, and the two ends of slippage pump 12 are connected with repairing safety overflow valve 121.Two repairing by pass valves 14 are connected to the two ends of revolution controllable capacity pump 10, and oil compensation pressure by pass valve 13 is located between two repairing by pass valves 14 and with the oil outlet of slippage pump 12 and is communicated with.Wherein, radiator 16 and the check valve 17 in parallel with radiator 16 that Control in Hydraulic Rotation System also comprises oil sump tank 15, with oil sump tank 15, is communicated with, radiator 16, check valve 17 are communicated with revolution controllable capacity pump 10, rotary motor 11 and flush valve 110 respectively, are used for reclaiming the unnecessary deep fat of overflow.
As shown in Figures 2 and 3, in the present embodiment, this revolution shock absorber comprises: control cock and damper valve 19, wherein, control cock is shuttle valve 18, two oil inlet P 0 and an oil outlet P1 are arranged, and two oil inlet P 0 of shuttle valve 18 are connected on two end loops of rotary motor 10, are used for controlling selecting the high-voltage oil liquid of Control in Hydraulic Rotation System to enter this revolution shock absorber.Damper valve 19 comprise valve body 191, valve pocket 192, with valve body 191 coordinate the plug 193, the spool 194 that is placed in valve pocket 192 and the elastomeric element that form valve pockets 192, with damper valve oil outlet A1, the damper valve oil inlet A0 that is connected with spool 194 that valve pocket 192 is communicated with, damper valve oil inlet A0 is communicated with the oil outlet P1 of shuttle valve.Wherein, in the present embodiment, elastomeric element is Compress Spring 195, and an end of Compress Spring 195 is connected to described plug 193, and the other end is plugged on spool 194.This damper valve 19 also is provided with the side chamber 196 that is connected with valve pocket 192, spool 194 comprises first 1941, second portion 1942 and third part 1943, its first 1941 is suitable with side chamber 196 and be connected damper valve oil inlet A0, its second portion 1942 is divided into elastic cavity 1921 and non-resilient chamber 1922 with valve pocket 192, Compress Spring 195 is positioned at elastic cavity 1921, the one end is inserted on the second portion 1942 of spool 194, and the third part 1943 of spool 194 is socketed on Compress Spring 195.Spool 194 inside are provided with the liquid flow channel for oil 1944 of axial perforation, and the two ends of liquid flow channel for oil 1944 are communicated with respectively the elastic cavity 1921 of damper valve oil inlet A0 and valve pocket 192.Offer the passage 1945 of axial perforation on spool 194, passage 1945 is symmetrically distributed in liquid flow channel for oil 1944 both sides on spool 194, makes the elastic cavity 1921 of the valve pocket 192 of being separated by spool 194 and non-resilient chamber 1922 be connected, to keep equilibrium of pressure.Wherein, high-voltage oil liquid enters damper valve oil inlet A0 from shuttle valve 18, the high-voltage oil liquid pressure-acting makes part fluid enter valve pocket 192 via liquid flow channel for oil 1944 in damper valve oil inlet A0, and the difference of pressure at liquid flow channel for oil 1944 two ends makes spool 194 endwisely slipping along valve pocket 192.During greater than system back pressure, the pressure that acts on the high-voltage oil liquid on damper valve 19 promotes spool 194 extruding Compress Springs 195 towards plug 193 directions motions when load pressure.
Please continue to consult Fig. 2 and Fig. 3, in embodiments of the present invention, the inside of liquid flow channel for oil 1944 also is equipped with damping piece 197.When damper valve 19 was in running order, this damping piece 197 was followed spool 194 and is moved together.This damping piece 197 can be a damping piece, can be also that a plurality of damping pieces are arranged and formed side by side; The shape of damping piece 197 can be that hollow cylinder, inside are provided with the cylinder of stepped hole, also can are spheroid or the centrum that inside is provided with one or more apertures; the structure of concrete damping piece has multiple; those skilled in the art can be as required adjusts the shape of damping piece, size, quantity etc., includes within protection scope of the present invention.
Below introduce the specific works principle of damper valve.
When the two ends of the liquid flow channel for oil 1944 of spool 194 do not have difference of pressure, see also Fig. 2, hydraulic efficiency pressure system is in stabilized conditions, damper valve 19 is in off working state, it is free state, at this moment, spool 194, Compress Spring 195 are positioned at fixing position transfixion according to the size of loaded work piece pressure, fluid enters elastic cavity 1921 through liquid flow channel for oil 1944, the damping piece 197 of damper valve oil inlet A0, spool 194 successively, then flow out damper valve 19 through damper valve oil outlet A1, the operation pressure of load relies on fluid to flow through the pressure drop decompression that liquid flow channel for oil 1944 produces.
When the load of hydraulic efficiency pressure system owing to disturbing or other unpredictable factors while causing load pressure to raise, see also Fig. 3, when difference of pressure appearred in the two ends of the liquid flow channel for oil 1944 of spool 194 and the both sides of damping piece 197, this difference of pressure made spool 194 axially to plug 193 directions, sliding along valve pocket 192.at this moment, the first 1941 of spool is in the interior slip in side chamber 196, the second portion 1942 of spool is divided into elastic cavity 1921 and non-resilient chamber 1922 with valve pocket 192, Compress Spring 195 is positioned at elastic cavity 1921, the one end is inserted on the second portion of spool 194, the third part 1943 of spool is socketed in Compress Spring 195, when spool 194 slides, Compress Spring 195 compresses towards plug 193 directions under the squeezing action of the second portion 1942 of spool, the liquid that the while elastic cavity is 1921 li also is subject to the extruding of spool 194, discharge damper valve 19 from damper valve oil outlet A1.In embodiments of the present invention, be subject to the buffer action of liquid flow channel for oil 1944, damping piece 197, Compress Spring 195 due to the fluctuation of load pressure, cut down the amplitude of fluctuation of pressure, filtering the interference pressure in the system work process, assurance system works force value is reliably set up, make system works more steady, submissive, improved the handling of hydraulic efficiency pressure system.
The specific works process of this Control in Hydraulic Rotation System is as follows.
please in the lump with reference to figure 1, Fig. 2 and Fig. 3, revolution controllable capacity pump 10 directly is communicated with rotary motor 11, high-voltage oil liquid out enters the high pressure chargine line and then drives rotary motor 11 actings from revolution controllable capacity pump 10, the low pressure fluid of finishing merit recycles by the import that the low-pressure oil return pipe road enters revolution controllable capacity pump 10, revolution controllable capacity pump 10 overflows in the work engineering fluid flows into oil sump tank 15 by radiator 16, it is cooling that rotary motor 11 and the flush valve 110 that is connected to its two ends are also flowed back to oil sump tank 15 with the unnecessary deep fat of overflow by radiator 16, the effect of check valve 17 is to prevent that radiator 16 from stopping up.Slippage pump 12 and revolution controllable capacity pump 10 coaxial drive, when Control in Hydraulic Rotation System needs repairing, slippage pump 12 extracts fresh oil in fuel tank, middle from two repairing by pass valves 14 that the oil outlet outflow of slippage pump 12 is come feed circuit, when one of them repairing by pass valve 14 connect be the low-pressure oil return pipe road time, the fresh oil that supplements this repairing by pass valve 14 of just flowing through enters the low-pressure oil return pipe road and finally flows into revolution controllable capacity pump 10, and then has supplemented new fluid for whole Control in Hydraulic Rotation System.Wherein, feed circuit pressure is regulated by oil compensation pressure by pass valve 13, and the repairing amount of slippage pump 12 is regulated by repairing safety overflow valve 121.
When damper valve 19 is in off working state, Control in Hydraulic Rotation System is in stable state, load torque is constant, the fluid of the rotary motor 11 both sides oil inlet P 0 that shuttle valve 18 two ends enter shuttle valve 18 of flowing through, the shuttle valve 18 relatively pressure selection high-voltage oil liquid of two ends fluid flows into the liquid flow channel for oil 1944 that damper valve oil inlet A0 enters damper valve 19, flow out damper valve 19 during damping 197 when high-voltage oil liquid on liquid flow channel for oil 1944 and enter the outlet of slippage pump 12 after overdamping, and then enter feed circuit and continue to the system repairing.This moment, whole hydraulic efficiency pressure system was set up certain system pressure, and when load pressure was constant, the Compress Spring 195 on damper valve 19 and spool 194 all were in certain fixing position.
When being subject to the interference in the external world or the fluctuation of load itself and the factor impact that some can not be met, Control in Hydraulic Rotation System cause load torque to change, the oil pressure at rotary motor 11 two ends fluctuates, when pressure peak appears in oil pressure generation fluctuation rising, high-voltage oil liquid after shuttle valve 18 enters damper valve 19 through the damping 197 of damper valve 19 and the buffer action of Compress Spring 195, the peak value of the fluctuating pressure of fluid is cut down, avoided the vibration of system, stationarity and the traveling comfort of Control in Hydraulic Rotation System are controlled better.
Embodiment two,
See also Fig. 4, it has shown according to the present invention the hydraulic principle schematic diagram of second embodiment of Control in Hydraulic Rotation System.This Control in Hydraulic Rotation System comprises: revolution controllable capacity pump 20, be connected in parallel on the feed circuit at revolution controllable capacity pump 20 two ends, with the revolution rotary motor 21 that directly is communicated with of controllable capacity pump 20 and turn round shock absorber, the quantity of rotary motor 21 is more than one, the two ends of rotary motor 21 are parallel with flush valve 210, the revolution shock absorber is connected in parallel on the two ends of rotary motor 21 and with feed circuit, is communicated with, and is used for the fluctuation of pressure of buffering hydraulic rotary system.Wherein, feed circuit comprises slippage pump 22 and oil compensation pressure by pass valve 23, slippage pump 22 and revolution controllable capacity pump 20 coaxial drive, and the two ends of slippage pump 22 are connected with repairing safety overflow valve 221.Two repairing by pass valves 24 are connected to the two ends of revolution controllable capacity pump 20, and oil compensation pressure by pass valve 23 is located between repairing by pass valve 24 and with the oil outlet of slippage pump 20 and is communicated with.Wherein, radiator 26 and the check valve 27 in parallel with radiator 26 that Control in Hydraulic Rotation System also comprises oil sump tank 25, with oil sump tank 25, is communicated with, radiator 26, check valve 27 are communicated with revolution controllable capacity pump 20, rotary motor 21 and flush valve 210 respectively, are used for reclaiming the unnecessary deep fat of overflow.
In the present embodiment, the revolution shock absorber comprises: control cock and damper valve 29.Wherein, control cock is that the oil outlet of 28, two check valves 28 of two check valves is connected and is connected with the oil inlet of damper valve 29 together.Two oil inlets of check valve 28 are connected on two end loops of rotary motor 21, are used for controlling selecting the high-voltage oil liquid of Control in Hydraulic Rotation System to enter this revolution shock absorber.In the present embodiment, the structure of damper valve 29 is identical with the damper valve 19 in principle of work and embodiment one, and aunt repeats no more herein.
The specific works process of this Control in Hydraulic Rotation System is as follows.
please refer to Fig. 4, revolution controllable capacity pump 20 directly is communicated with rotary motor 21, high-voltage oil liquid out enters the high pressure chargine line and then drives rotary motor 21 actings from revolution controllable capacity pump 20, the low pressure fluid of finishing merit recycles by the import that the low-pressure oil return pipe road enters revolution controllable capacity pump 20, revolution controllable capacity pump 20 overflows in the work engineering fluid flows into oil sump tank 25 by radiator 26, it is cooling that rotary motor 21 and the flush valve 210 that is connected to its two ends are also flowed back to oil sump tank 25 with the unnecessary deep fat of overflow by radiator 26, the effect of check valve 27 is to prevent that radiator 26 from stopping up.Slippage pump 22 and revolution controllable capacity pump 20 coaxial drive, when Control in Hydraulic Rotation System needs repairing, slippage pump 22 extracts fresh oil in fuel tank, middle from two repairing by pass valves 24 that the oil outlet outflow of slippage pump 22 is come feed circuit, when one of them repairing by pass valve 24 connect be the low-pressure oil return pipe road time, the fresh oil that supplements this repairing by pass valve 24 of just flowing through enters the low-pressure oil return pipe road and finally flows into revolution controllable capacity pump 20, and then has supplemented new fluid for whole Control in Hydraulic Rotation System.Wherein, feed circuit pressure is regulated by oil compensation pressure by pass valve 23, and the repairing amount of slippage pump 22 is regulated by repairing safety overflow valve 221.
When damper valve 29 is in off working state, Control in Hydraulic Rotation System is in stable state, load torque is constant, the fluid of rotary motor 21 both sides enters respectively the oil inlet of two check valves 28, flow through two check valves and then flow into the liquid flow channel for oil that the oil inlet of damper valve 29 enters damper valve 29 again of high-voltage oil liquid and low pressure fluid, flow out damper valve 29 when high-voltage oil liquid during through the damping on liquid flow channel for oil and enter the outlet of slippage pump 22 after overdamping, and then enter feed circuit and continue to the system repairing.This moment, whole hydraulic efficiency pressure system was set up certain system pressure, and when load pressure was constant, the Compress Spring on damper valve 29 and spool all were in certain fixing position.
When being subject to the interference in the external world or the fluctuation of load itself and the factor impact that some can not be met, Control in Hydraulic Rotation System cause load torque to change, the oil pressure at rotary motor 21 two ends fluctuates, when pressure peak appears in oil pressure generation fluctuation rising, high-voltage oil liquid after two check valves 28 enter damper valve 29 through the damping of damper valve 29 and the buffer action of Compress Spring, the peak value of the fluctuating pressure of fluid is cut down, avoided the vibration of system, stationarity and the traveling comfort of Control in Hydraulic Rotation System are controlled better.
In embodiment one and embodiment two above, elastomeric element can be spring, also can according to circumstances adopt other to have and similar elastically-deformable object can occur.Plug 193 in embodiment one can arrange set screw, is used for regulating the deformation quantity of Compress Spring 195.In addition, the shape of Compress Spring 195 and position arrange and also are not limited to shown in figure, one end of Compress Spring 195 can directly be fixed on the third part 1943 of spool 194, also can be looped around on spool 194, all be not construed as limiting the invention, those skilled in the art can carry out the phase strain type in conjunction with actual conditions.
In sum, the present invention, by increase control cock and damper valve in Control in Hydraulic Rotation System, can eliminate rotary system produces in turning course fluctuation of pressure by actv., promotes stationarity and traveling comfort that rotary system is handled.Simultaneously, pressure oil in Control in Hydraulic Rotation System of the present invention flows out damper valve after setting up system pressure by the damping piece on damper valve, flow into again the oil outlet of slippage pump, entered so again the feed circuit of system, avoided system repairing amount need select the problem of the slippage pump of larger discharge capacity not.In addition, two check valves in shuttle valve in embodiment one and embodiment two be arranged so that no matter rotary motor is clickwise or left-hand revolution, load pressure can be chosen the oil inlet of damper valve, thereby can guarantee hydraulic gyration mechanism no matter while being forward or counter-rotating, Control in Hydraulic Rotation System can guarantee rotating function of vibration.
The present invention also provides a kind of engineering truck, and it is equipped with above-mentioned Control in Hydraulic Rotation System.
These are only embodiments of the invention; not thereby limit the scope of the claims of the present invention; every equivalent structure or equivalent flow process conversion that utilizes specification sheets of the present invention and accompanying drawing content to do; or directly or indirectly be used in other relevant technical fields, all in like manner be included in scope of patent protection of the present invention.
Claims (10)
1. Control in Hydraulic Rotation System, it is characterized in that, described Control in Hydraulic Rotation System comprises: the revolution controllable capacity pump, be connected in parallel on the feed circuit at described revolution controllable capacity pump two ends, the rotary motor that directly is communicated with described revolution controllable capacity pump and turn round shock absorber, described revolution shock absorber is connected in parallel on the two ends of described rotary motor and with described feed circuit, is communicated with, and is used for cushioning the fluctuation of pressure of described Control in Hydraulic Rotation System;
Described revolution shock absorber comprises control cock and damper valve, described control cock is used for controlling selects the high-voltage oil liquid of described Control in Hydraulic Rotation System to enter described damper valve, described damper valve is used for the amplitude of cutting down described fluctuation of pressure, make described Control in Hydraulic Rotation System steady, improve the handling of described Control in Hydraulic Rotation System.
2. Control in Hydraulic Rotation System according to claim 1, is characterized in that,
Described damper valve comprises valve body, valve pocket, with described valve body, coordinates plug, the spool that is placed in described valve pocket and the elastomeric element that forms described valve pocket, the damper valve oil outlet with described valve pocket connection, the damper valve oil inlet that is connected with described spool, and described damper valve oil inlet is communicated with described control cock;
Described spool connects described damper valve oil inlet, and described valve core inside is provided with the liquid flow channel for oil of axial perforation, and the two ends of described liquid flow channel for oil are communicated with respectively described damper valve oil inlet and described valve pocket;
Wherein, high-voltage oil liquid enters described damper valve oil inlet from described control cock, and during greater than system back pressure, the pressure that acts on the high-voltage oil liquid on described damper valve promotes the described elastomeric element of described spool compression and moves towards described plug direction when load pressure.
3. Control in Hydraulic Rotation System according to claim 2, is characterized in that, described control cock is shuttle valve, and described shuttle valve has two oil inlets and an oil outlet, and the oil outlet of described shuttle valve is communicated with described damper valve oil inlet.
4. Control in Hydraulic Rotation System according to claim 2, is characterized in that, described control cock is two check valves, and the oil outlet of described two check valves is connected and is connected with described damper valve oil inlet together.
5. according to claim 2 or 3 or 4 described Control in Hydraulic Rotation Systems, is characterized in that, described elastomeric element is Compress Spring, and an end of described Compress Spring is connected to described plug, and the other end is plugged on described spool.
6. want 5 described Control in Hydraulic Rotation Systems according to right, it is characterized in that, offer the passage of axial perforation on described spool, described passage is symmetrically distributed in the described liquid flow channel for oil both sides on described spool, make the described valve pocket of being separated by described spool be connected, to keep equilibrium of pressure.
7. Control in Hydraulic Rotation System according to claim 2, is characterized in that, is provided with damping piece in described liquid flow channel for oil, and described damping piece quantity is at least one.
8. Control in Hydraulic Rotation System according to claim 2, is characterized in that, described feed circuit comprises:
Slippage pump, described slippage pump and described revolution controllable capacity pump coaxial drive, the two ends of described slippage pump are connected with the repairing safety overflow valve, and described slippage pump oil outlet is communicated with described damper valve oil outlet;
Two repairing by pass valves, be connected to the two ends of described revolution controllable capacity pump;
Oil compensation pressure by pass valve, described oil compensation pressure by pass valve are located between described repairing by pass valve and with described slippage pump oil outlet and are communicated with;
The quantity of described rotary motor is more than one, and the two ends of described rotary motor are parallel with flush valve.
9. Control in Hydraulic Rotation System according to claim 8, is characterized in that, radiator and the check valve in parallel with described radiator that described Control in Hydraulic Rotation System further comprises oil sump tank, with described oil sump tank, is communicated with; Described radiator, described check valve are communicated with described revolution controllable capacity pump, described rotary motor and described flush valve respectively, are used for reclaiming the unnecessary deep fat of overflow.
10. an engineering truck, is characterized in that, comprises according to claim 1-9 described Control in Hydraulic Rotation Systems of any one.
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| CN2012100572976A CN102602830B (en) | 2012-03-06 | 2012-03-06 | Hydraulic rotary system and engineering vehicle |
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| CN2012100572976A CN102602830B (en) | 2012-03-06 | 2012-03-06 | Hydraulic rotary system and engineering vehicle |
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| CN108506256A (en) * | 2018-03-27 | 2018-09-07 | 江苏恒立液压科技有限公司 | Drive hydraulic control system |
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| CN114320818B (en) * | 2021-12-20 | 2024-01-23 | 湖南道依茨动力有限公司 | Pumping system control method, pumping system and engineering machinery |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DD116875A1 (en) * | 1974-11-08 | 1975-12-12 | ||
| US5062266A (en) * | 1990-08-23 | 1991-11-05 | Kabushiki Kaisha Kobe Seiko Sho | Slewing control device for crane |
| CN201166020Y (en) * | 2008-03-05 | 2008-12-17 | 赵铁栓 | Hydraulic constant velocity switching device |
| CN201317637Y (en) * | 2008-12-23 | 2009-09-30 | 常德信诚液压有限公司 | Turning control assembly of hydraulic truck crane |
| CN102155447A (en) * | 2011-03-15 | 2011-08-17 | 徐州重型机械有限公司 | Rotating hydraulic system of crane and rotating buffer valve thereof |
| CN102229416A (en) * | 2011-06-29 | 2011-11-02 | 三一汽车起重机械有限公司 | Closed-type rotary hydraulic system for crane and crane |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4475442A (en) * | 1982-02-08 | 1984-10-09 | Vickers, Incorporated | Power transmission |
-
2012
- 2012-03-06 CN CN2012100572976A patent/CN102602830B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DD116875A1 (en) * | 1974-11-08 | 1975-12-12 | ||
| US5062266A (en) * | 1990-08-23 | 1991-11-05 | Kabushiki Kaisha Kobe Seiko Sho | Slewing control device for crane |
| CN201166020Y (en) * | 2008-03-05 | 2008-12-17 | 赵铁栓 | Hydraulic constant velocity switching device |
| CN201317637Y (en) * | 2008-12-23 | 2009-09-30 | 常德信诚液压有限公司 | Turning control assembly of hydraulic truck crane |
| CN102155447A (en) * | 2011-03-15 | 2011-08-17 | 徐州重型机械有限公司 | Rotating hydraulic system of crane and rotating buffer valve thereof |
| CN102229416A (en) * | 2011-06-29 | 2011-11-02 | 三一汽车起重机械有限公司 | Closed-type rotary hydraulic system for crane and crane |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102602830A (en) | 2012-07-25 |
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