CN201729610U - Rotary hydraulic system of crane and crane - Google Patents
Rotary hydraulic system of crane and crane Download PDFInfo
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- CN201729610U CN201729610U CN2010202744282U CN201020274428U CN201729610U CN 201729610 U CN201729610 U CN 201729610U CN 2010202744282 U CN2010202744282 U CN 2010202744282U CN 201020274428 U CN201020274428 U CN 201020274428U CN 201729610 U CN201729610 U CN 201729610U
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Abstract
The utility model discloses a rotary hydraulic system of a crane, which is applied to a traveling crane and comprises a hydraulic pump, a rotary motor and a brake cylinder. The rotating hydraulic system further comprises a flow-adjustable hydraulic-control reversing valve, a first flow control valve, a second flow control valve and a brake reversing valve. The system adopts independent control loops of oil intake, return oil and bypass, that is, the oil intake passage, the return oil passage and the bypass oil passage are independent from one another. According to the change in external load, the three loops are controlled independently by adjusting the opening degree of the hydraulic-control reversing valve, the first flow control valve and the second flow control valve under the complex loading conditions, so that the crane runs more stably and the cost is controlled within a certain range with significant economic benefit. The utility model also discloses a crane with the rotary hydraulic system.
Description
Technical field
The utility model relates to technical field of hydraulic, particularly relates to a kind of hydraulic efficiency pressure system that rotating platform of crane is done gyroscopic movement that is used to drive.The utility model also relates to the hoisting crane that is provided with above-mentioned hydraulic efficiency pressure system.
Background technology
Along with the fast development of China's economic construction, market for wheel crane particularly in the demand of large-tonnage wheel crane increase day by day.
Wheel crane work the time utilizes the arm weight of slinging, rely on turntable revolution with the weight task of finishing the work from a position transfer to another one position then, therefore rotating stationarity is to weigh an important indicator of hoisting crane quality, wheel crane revolution action is controlled by Hydraulic slewing system, and the quality of design of Hydraulic System will determine rotating stationarity.
According to the cycle mode of hydraulic oil, the Hydraulic slewing system of hoisting crane can be divided into two kinds of open-circuit system and closed systems, and these two kinds of systems cut both ways, and can select according to actual needs.
Open-circuit system is meant Hydraulic Pump from the fuel tank oil suction, and hydraulic oil drives hydraulic actuator after various control cock, flow back to fuel tank then.This system architecture is comparatively simple, can bring into play heat radiation, the precipitated impurities effect of fuel tank.Owing to there is reversing impact, and fluid often contacts with air, makes air be easy to the infiltration system, causes the rotary stability of mechanism poor.But because cost is lower, medium and small tonnage (＜100t) use on the hoisting crane comparatively extensive.
In the closed system, the oil inlet of Hydraulic Pump directly links to each other with the oil return pipe of power element, and hydraulic oil carries out close cycle in the pipeline of system; Its compact conformation, few with the air touch opportunity, air is difficult for the infiltration system, owing to do not contain change-over valve, has reduced reversing impact, helps realizing rotating stability, has avoided the hydraulic efficiency impact and the degradation of energy that are occurred in the open-circuit system commutation process.But than higher, so cost increases closed system greatly to the performance requriements of Hydraulic Pump, generally is used for large-tonnage (＞100t) hoisting crane; In addition, closed system is than the open-circuit system complexity, owing to lack fuel tank, the heat radiation and the filtercondition of hydraulic oil are relatively poor.
Along with domestic, international hoisting crane market competition is more and more fierce, the hoisting crane product is towards high stability, direction develops cheaply.As can be seen from the above analysis, adopt closed system can guarantee the rotary stability of hoisting crane to a certain extent, but its manufacturing cost is too high, generally be applicable to hoister in large tonnage, for middle or small tonnage hoisting crane, owing to be subjected to the restriction of manufacturing cost, generally all adopt open-circuit system, in turntable startup, braking procedure,, be easy to generate phenomenons such as vibration, impact because load variations is comparatively complicated.
For improving the rotary stability of hoisting crane, in open-circuit system, generally adopt hydraulic circuit as shown in Figure 1 at present, this Hydraulic slewing system passing ratio direction valve 1-1, slow supply oil device A, brake cylinder 1-2 realize the work of motor 1-3.
When requiring motor to turn right, Hydraulic Pump 1-4 pressure oil output, right work of change-over valve 1-5, pressure enters brake cylinder 1-2, removes the motor braking, proportion directional valve 1-1 right side position work simultaneously, pressure oil enters chamber, a motor 1-3 left side, realizes the motor right-hand rotation; When requiring motor to stop, the work of proportional reversing valve 1-1 meta, stop to provide pressure oil to motor, the position work of a change-over valve 1-5 left side, brake cylinder begins braking, and this moment is because the inertia of turntable, motor still will rotate certain distance, motor right side oil pressure raises by by pass valve 1-6 off-load, passes on left check valve 1-7 repairing, realizes that motor stops operating.
When requiring motor to turn left, the position work of a proportional reversing valve 1-1 left side, other is identical during with right-hand rotation.
Above-mentioned slow supply oil device A adopts four check valves to be connected the oil inlet and outlet on HM Hydraulic Motor both sides with a by pass valve, if parking or steering resistance increase suddenly, when causing the right oil circuit overload, by pass valve 1-6 opens, and the part high pressure oil flows back to fuel tank by check valve 1-10 and by pass valve 1-6, simultaneously, the motor left side is that negative pressure is opened check valve 1-7, fluid to the repairing of the motor left side, is finished a safe buffering repairing short circle by check valve 1-7, and vice versa.This loop structure is simple, repairing is abundant, but has the following disadvantages:
1) though hydraulic efficiency pressure system can be by changing the valve port opening of proportional reversing valve 1-1, regulate pressure, the flow of oil circuit, but reason owing to proportional reversing valve 1-1 configuration aspects, oil inlet aperture and return opening aperture change simultaneously, so be unfavorable for the stability of the system that realizes, promptly motor is rotating stable.
When 2) requiring motor to quit work, slow supply oil device A can be played a role to the stability of motor.But,, when load variations is big, can not realize effectively that motor is stable to quit work because the instant modulability of each valve is relatively poor in the device.
Therefore, how improving the rotary stability of the medium tonnage hoisting crane that adopts open-circuit system, is the present technical issues that need to address of those skilled in the art.
The utility model content
The purpose of this utility model provides a kind of crane rotation hydraulic efficiency pressure system.This system is the open-circuit system that has adopted oil inlet and oil return independence mode, can make the hoisting crane running more steady, and with cost control within the specific limits, have very high economic benefit.
Another purpose of the present utility model provides a kind of hoisting crane that is provided with above-mentioned crane rotation hydraulic efficiency pressure system.
In order to realize above-mentioned first purpose, the utility model provides a kind of crane rotation hydraulic efficiency pressure system, be used for movable crane, comprise Hydraulic Pump, rotary motor, brake cylinder, also comprise the adjustable pilot operated directional control valve of flow, first flow control cock, second flow control valve and braking change-over valve;
The oil outlet of described Hydraulic Pump is told two fuel feeding branch roads, and wherein one the tunnel for driving oil circuit, and another road is a control oil channel;
The driving oil circuit of described Hydraulic Pump connects first oil inlet of described pilot operated directional control valve, and first oil outlet of described pilot operated directional control valve connects the oil inlet of described rotary motor, and second oil outlet of described pilot operated directional control valve connects the return opening of described rotary motor;
The control oil channel of described Hydraulic Pump connects the oil inlet of described braking change-over valve, and the oil outlet of described braking change-over valve connects described brake cylinder; The return opening of described braking change-over valve is communicated with fuel tank;
The oil inlet of described rotary motor is communicated with the oil inlet of described first flow control cock, and the oil outlet of described first flow control cock is communicated with fuel tank;
The return opening of described rotary motor is communicated with the oil inlet of described second flow control valve, and the oil outlet of described second flow control valve is communicated with fuel tank.
Preferably, the control oil channel between the oil outlet of the oil inlet of described braking change-over valve and described Hydraulic Pump is provided with solenoid directional control valve; The oil inlet of described solenoid directional control valve is communicated with the oil outlet of described Hydraulic Pump, the oil outlet of described solenoid directional control valve is communicated with the oil inlet of the first electric proportional pressure-reducing valve, the second electric proportional pressure-reducing valve, and the oil outlet of the described first electric proportional pressure-reducing valve and the second electric proportional pressure-reducing valve is connected two control ends of described pilot operated directional control valve respectively; The drain tap of the described first electric proportional pressure-reducing valve and the second electric proportional pressure-reducing valve is communicated with fuel tank respectively; The return opening of described solenoid directional control valve is communicated with fuel tank.
Preferably, described first flow control cock is specially hydraulicchange-over valve, and and be provided with the 4th electric proportional pressure-reducing valve between the described solenoid directional control valve, the oil inlet of described the 4th electric proportional pressure-reducing valve is communicated with the oil outlet of described solenoid directional control valve, and the oil outlet of described the 4th electric proportional pressure-reducing valve connects the control end of described hydraulicchange-over valve; The drain tap of described the 4th electric proportional pressure-reducing valve is communicated with fuel tank.
Preferably, described second flow control valve is specially hydraulicchange-over valve, and and be provided with the 3rd electric proportional pressure-reducing valve between the described solenoid directional control valve, the oil inlet of described the 3rd electric proportional pressure-reducing valve is communicated with the oil outlet of described solenoid directional control valve, and the oil outlet of described the 3rd electric proportional pressure-reducing valve connects the control end of described hydraulicchange-over valve; The drain tap of described the 3rd electric proportional pressure-reducing valve is communicated with fuel tank.
Preferably, described first flow control cock is provided with the first unidirectional by pass valve that is in parallel with it on oil circuit.
Preferably, described second flow control valve is provided with the second unidirectional by pass valve that is in parallel with it on oil circuit.
Preferably, oil circuit between described braking change-over valve and the described brake cylinder is provided with conducting valve, the oil inlet of described conducting valve is communicated with the oil outlet of described braking change-over valve, and the oil outlet of described conducting valve connects described brake cylinder, and the hydraulic fluid port that ends of described conducting valve is communicated with fuel tank.
Preferably, be provided with precursor overflow valve between the driving oil circuit of described hydraulic oil pump and the fuel tank, the oil inlet of described precursor overflow valve is communicated with the oil outlet of described hydraulic oil pump, and the oil outlet of described precursor overflow valve and Y mouth all are communicated with fuel tank.
Preferably, be provided with by pass valve between described pilot operated directional control valve and the fuel tank, the oil inlet of described by pass valve is communicated with the 3rd oil outlet of described pilot operated directional control valve, and the oil outlet of described by pass valve is communicated with fuel tank; The control port of described by pass valve is communicated with the 4th oil outlet of described pilot operated directional control valve; Second oil inlet of described pilot operated directional control valve is communicated with fuel tank; The 3rd oil inlet of described pilot operated directional control valve is communicated with the oil outlet of described hydraulic oil pump.
Preferably, be provided with mutual series connected flow regulating valve and check valve on oil circuit between the 4th oil outlet of the control port of described by pass valve and described pilot operated directional control valve.
Preferably, described pilot operated directional control valve is specially three six-way transfer valves, has three control positioies in left, center, right;
When described pilot operated directional control valve was in meta, its second oil inlet was communicated with the 4th oil outlet, and the 3rd oil inlet is communicated with the 3rd oil outlet, and all the other each hydraulic fluid ports are in off condition;
When described pilot operated directional control valve was in position, a left side, its first oil inlet was communicated with second oil outlet, and first oil inlet is communicated with the 4th oil outlet simultaneously, and all the other each hydraulic fluid ports are in off condition;
When described pilot operated directional control valve was in right position, its first oil inlet was communicated with first oil outlet, and first oil inlet is communicated with the 4th oil outlet simultaneously, and all the other each hydraulic fluid ports are in off condition.
Crane rotation hydraulic efficiency pressure system provided by the utility model adopts oil-feed, oil return, bypass independence speed control loop, be that in-line, oil return line and bleed off circuit are separate, can be according to the variation of outer load, under the loading condition of complexity, realize the independent control in three loops by the opening amount of regulating pilot operated directional control valve, first flow control cock, second flow control valve, realize the polynary adjusting of hydraulic circuit, can realize the speed setting of hydraulic circuit by controller automatically.Therefore rotate more steadily during rotating platform of crane work, shake, impact phenomenon obviously reduce, and helps improving the stability of hoisting crane.
In order to realize above-mentioned second purpose, the utility model also provides a kind of hoisting crane, the hydraulic efficiency pressure system that comprises turntable, is installed in the arm on the described turntable and drives described turntable is characterized in that, described hydraulic efficiency pressure system is specially above-mentioned each described crane rotation hydraulic efficiency pressure system.
The control method that the utility model provides is by control cock control electric current, to pilot operated directional control valve, the first flow control cock, the opening amount of second flow control valve is regulated, thereby realize independent control to three loops, turntable is starting, revolution, deboost phase, if the input pressure instability of turntable rotary motor, then realize entrance throttle governing circuit by the opening amount of regulating pilot operated directional control valve, realize oil return (being bypass during contrarotation) throttling governing by the opening amount of regulating the first flow control cock, realize bypass (being oil return line during contrarotation) throttling governing by the opening amount of regulating second flow control valve, hydraulic efficiency pressure system is utilized pilot operated directional control valve, the first flow control cock, second flow control valve is realized oil-feed, oil return, the by-pass throttle speed governing makes hydraulic efficiency pressure system have big rigidity and stable preferably.
Description of drawings
Fig. 1 is the principle schematic that a kind of hoisting crane is used hydraulic control system in the prior art;
Fig. 2 is the principle schematic of a kind of specific embodiment of crane rotation hydraulic efficiency pressure system provided by the utility model;
Fig. 3 is the simplified model scheme drawing of crane rotation hydraulic efficiency pressure system provided by the utility model;
Fig. 4 is the diagram of circuit of crane rotation hydraulic system control method provided by the utility model.
Among Fig. 1: 1-1. proportion directional valve 1-2. brake cylinder 1-3. motor 1-4. Hydraulic Pump 1-5. change-over valve 1-6. by pass valve 1-7. check valve 1-8. check valve 1-9. check valve 1-10. check valve
Among Fig. 2: 1. first electric proportional pressure-reducing valve 2. second electric proportional pressure-reducing valve 3. the 3rd electric proportional pressure-reducing valve 4. the 4th electric proportional pressure-reducing valve 5. pilot operated directional control valves 6. first flow control cocks 7. second flow control valves 8. solenoid directional control valves 9. second unidirectional by pass valve 10. first unidirectional by pass valve 11. Hydraulic Pumps 12. precursor overflow valves 13. rotary motors 14. brake cylinders 15. fuel tanks 16. by pass valves 17,17 '. check valve 18. conducting valves 19. braking change-over valves 20. flow regulating valve
Among Fig. 3: q1. flow regulating valve q2. flow regulating valve q3. flow regulating valve flow regulating valve
The specific embodiment
Core of the present utility model provides a kind of crane rotation hydraulic efficiency pressure system.This system is the open-circuit system that has adopted oil inlet and oil return independence mode, can make the hoisting crane running more steady, and with cost control within the specific limits, have very high economic benefit.
Another core of the present utility model provides a kind of control method of above-mentioned crane rotation hydraulic efficiency pressure system.
In order to make those skilled in the art person understand the utility model scheme better, the utility model is described in further detail below in conjunction with the drawings and specific embodiments.
Terms such as herein " first, second " only is for convenience of description, with the different constituent elementss that differentiation has same names, does not represent successively or the primary and secondary relation.
Please referring to Fig. 2, Fig. 2 is the principle schematic of a kind of specific embodiment of crane rotation hydraulic efficiency pressure system provided by the utility model.
As shown in Figure 2, the crane rotation hydraulic efficiency pressure system that the utility model provides, be used for movable crane, comprise Hydraulic Pump 11, rotary motor 13, brake cylinder 14, also comprise the adjustable pilot operated directional control valve of flow 5, first flow control cock 6, second flow control valve 7 and braking change-over valve 19.
The oil outlet of Hydraulic Pump 11 is told two fuel feeding branch roads, and wherein one the tunnel for driving oil circuit, and another road is a control oil channel; The driving oil circuit of Hydraulic Pump 11 connects first oil inlet of pilot operated directional control valve 5, and first oil outlet of pilot operated directional control valve 5 connects the oil inlet of rotary motor 13, and second oil outlet of pilot operated directional control valve 5 connects the return opening of rotary motor 13; The control oil channel of Hydraulic Pump 11 connects the oil inlet of braking change-over valve 19, and the oil outlet of braking change-over valve 19 connects brake cylinder 14.
First flow control cock 6 is specially the bi-bit bi-pass hydraulicchange-over valve, and the oil inlet of rotary motor 13 is communicated with the oil inlet of first flow control cock 6, and the oil outlet of first flow control cock 6 is communicated with fuel tank; Be provided with the 4th electric proportional pressure-reducing valve 4 between first flow control cock 6 and the solenoid directional control valve 8, the oil inlet of the 4th electric proportional pressure-reducing valve 4 is communicated with the oil outlet of solenoid directional control valve 8, the oil outlet of the 4th electric proportional pressure-reducing valve 4 connects the control end of first flow control cock 6, by the opening amount of the 4th electric proportional pressure-reducing valve 4 may command first flow control cocks 6, thereby reach the purpose that flow is regulated.
First flow control cock 6 is provided with the first unidirectional by pass valve 10 that is in parallel with it.Here, the first unidirectional by pass valve 10 in use can play the effect of restriction pressure and repairing.
Second flow control valve 7 is similarly the bi-bit bi-pass hydraulicchange-over valve, and the return opening of rotary motor 13 is communicated with the oil inlet of second flow control valve 7, and the oil outlet of second flow control valve 7 is communicated with fuel tank; Be provided with the 3rd electric proportional pressure-reducing valve 3 between second flow control valve 7 and the solenoid directional control valve 8, the oil inlet of the 3rd electric proportional pressure-reducing valve 3 is communicated with the oil outlet of solenoid directional control valve 8, the oil outlet of the 3rd electric proportional pressure-reducing valve 3 connects the control end of second flow control valve 7, by the opening amount of the 3rd electric proportional pressure-reducing valve 3 may command second flow control valve 7, thereby reach the purpose that flow is regulated.
Second flow control valve 7 is provided with the second unidirectional by pass valve 9 that is in parallel with it.Here, the second unidirectional by pass valve 9 in use can play the effect of restriction pressure and repairing.
The oil inlet of solenoid directional control valve 8 is communicated with the oil outlet of Hydraulic Pump 11, the oil outlet of solenoid directional control valve 8 is communicated with the oil inlet of first electric proportional pressure-reducing valve 1, the second electric proportional pressure-reducing valve 2, and the oil outlet of the first electric proportional pressure-reducing valve 1 and the second electric proportional pressure-reducing valve 2 is connected two control ends of pilot operated directional control valve 5 respectively.Can make pilot operated directional control valve 5 be in different control positioies by the first electric proportional pressure-reducing valve 1 with the second electric proportional pressure-reducing valve 2, and the opening amount can control pilot operated directional control valve 5 and be in each control position the time, thereby reach the purpose that flow is regulated.
Oil circuit between braking change-over valve 19 and the brake cylinder 14 is provided with conducting valve 18, and the oil inlet of conducting valve is communicated with the oil outlet of braking change-over valve 19, and the oil outlet of conducting valve 18 connects brake cylinder 14, and the hydraulic fluid port that ends of conducting valve 18 is communicated with fuel tank.
In order to guarantee the safety of whole turntable Hydraulic slewing system, between the driving oil circuit of hydraulic oil pump 11 and fuel tank, be provided with precursor overflow valve 12, the oil inlet of precursor overflow valve 12 is communicated with the oil outlet of hydraulic oil pump 11, the oil outlet of precursor overflow valve 12 and Y mouth all are communicated with fuel tank, when system pressure reaches the settling pressure of precursor overflow valve, precursor overflow valve 12 will be opened release.
Pilot operated directional control valve 5 is specially three six-way transfer valves, has three control positioies in left, center, right;
When being in meta, its second oil inlet is communicated with the 4th oil outlet, and the 3rd oil inlet is communicated with the 3rd oil outlet, and all the other each hydraulic fluid ports are in off condition;
When being in position, a left side, its first oil inlet is communicated with second oil outlet, and first oil inlet is communicated with the 4th oil outlet at valve inner simultaneously, and all the other each hydraulic fluid ports are in off condition;
When being in right position, its first oil inlet is communicated with first oil outlet, and first oil inlet is communicated with the 4th oil outlet at valve inner simultaneously, and itself and each hydraulic fluid port are in off condition.
Be provided with by pass valve 16 between pilot operated directional control valve 5 and the fuel tank, the oil inlet of by pass valve 16 is communicated with the 3rd oil outlet of pilot operated directional control valve 5, and the oil outlet of by pass valve 16 is communicated with fuel tank; The control port of by pass valve 16 is communicated with the 4th oil outlet of pilot operated directional control valve 5, and second oil inlet of pilot operated directional control valve 5 is communicated with fuel tank, and the 3rd oil inlet of pilot operated directional control valve 5 is communicated with the oil outlet of Hydraulic Pump 11.
Oil circuit between the 4th oil outlet of the control port of by pass valve 16 and pilot operated directional control valve 5 is provided with mutual series throttle 20 and check valve 17.
Below introduce the working process of the rotating platform of crane Hydraulic slewing system that the utility model provides.
When turntable was in halted state: Hydraulic Pump 11 was by direct motor drive rotation, oil suction from fuel tank 15; The control position of pilot operated directional control valve 5, two-position three way solenoid directional control valve 8, bi-bit bi-pass hydraulic operated valve 6, bi-bit bi-pass hydraulic operated valve 7 all is in off condition as shown in the figure; Fluid is from Hydraulic Pump 11 output, successively pass through check valve 17 ', the 3rd oil inlet of pilot operated directional control valve 5, the 3rd oil outlet of pilot operated directional control valve 5, flow back to fuel tank from by pass valve 16.At this moment, the left and right sides of rotary motor 13 does not all have pressure oil and passes through, and brake cylinder 14 is in braking mode.
When the turntable anti-clockwise rotation: in control oil channel (dotted line is represented), two-position three way solenoid directional control valve 8 is after the electromagnet energising, its position, left side work, from the pressure oil of Hydraulic Pump 11 output by the road a be divided into some branch roads by solenoid directional control valve 8, enter braking change-over valve 19, first electric proportional pressure-reducing valve 1, second electric proportional pressure-reducing valve the 2, the 3rd electric proportional pressure-reducing valve the 3, the 4th electric proportional pressure-reducing valve 4 respectively.At this moment, the energising of braking change-over valve 19 electromagnet, the upper work of change-over valve, the conducting brake circuit, pressure oil enters brake cylinder 14 after braking change-over valve 19, remove the braking to rotary motor 13; The first electric proportional pressure-reducing valve 1 electromagnet energising simultaneously, the pressure oil of control oil channel enters the right control end of pilot operated directional control valve 5 after through the first electric proportional pressure-reducing valve 1, the promotion spool moves, make the right position work of pilot operated directional control valve 5, hydraulic oil is from first oil inlet of Hydraulic Pump 11 output process pilot operated directional control valves 5, the right side that first oil outlet enters rotary motor 13; The electromagnet energising of the 3rd electric proportional pressure-reducing valve 3, the pressure oil of control oil channel enters hydraulicchange-over valve 7 through this, the promotion spool moves, hydraulicchange-over valve 7 the next work are in conducting state, and the hydraulic oil in rotary motor 13 left sides can flow back to fuel tank through hydraulicchange-over valve 7, realize brake cylinder 14 brake offs thus, hydraulic oil enters the motor right side through pilot operated directional control valve 5 simultaneously, and pressure oil promotes rotary motor 13 anti-clockwise rotations, and turntable rotary motor 13 left side low pressure oil flow back to fuel tank through hydraulicchange-over valve 7.
When the turntable right-hand revolution: in control oil channel (dotted line is represented), two-position three way solenoid directional control valve 8 is in position, the left side work of electromagnet energising back, from the pressure oil of Hydraulic Pump 11 output by the road a be divided into some branch roads by solenoid directional control valve 8, enter braking change-over valve 19, first electric proportional pressure-reducing valve 1, second electric proportional pressure-reducing valve the 2, the 3rd electric proportional pressure-reducing valve the 3, the 4th electric proportional pressure-reducing valve 4 respectively.At this moment, the electromagnet energising of the second electric proportional pressure-reducing valve 2, the pressure oil of control oil channel enters the left control end of pilot operated directional control valve 5, the promotion spool moves, make the position work of pilot operated directional control valve 5 left side, hydraulic oil is from first oil inlet of Hydraulic Pump 11 output process pilot operated directional control valves 5, the left side that second oil outlet enters turntable rotary motor 13; Brake the electromagnet energising of change-over valve 19 simultaneously, the upper work of change-over valve, pressure oil enters brake fluid pressure cylinder 14 after braking change-over valve 19, remove the braking to turntable rotary motor 13; The electromagnet energising of the 4th electric proportional pressure-reducing valve 4, the pressure oil of control oil channel enters hydraulicchange-over valve 6 promotion spools through this and moves, make the upper work of change-over valve, be in conducting state, the hydraulic oil that drives oil circuit can flow back to fuel tank through hydraulicchange-over valve 6, realizes brake cylinder 14 brake offs thus, and hydraulic oil enters turntable rotary motor 13 left sides through pilot operated directional control valve 5 simultaneously, pressure oil promotes rotary motor 13 right-hand revolutions, and the low pressure oil on rotary motor 13 right sides flows back to fuel tank through hydraulicchange-over valve 6.
Please refer to Fig. 3, Fig. 3 is the simplified model scheme drawing of crane rotation hydraulic efficiency pressure system provided by the utility model.
Introduce the utility model oil-feed, oil return, bypass throttling speed control principle below.When the motor anti-clockwise rotation (it is identical with the left-hand rotation principle to turn right), the first electric proportional pressure-reducing valve 1 is realized entrance throttle governing circuit by the opening amount of control pilot operated directional control valve 5; The 3rd electric proportional pressure-reducing valve 3 is realized the meter out speed governing by the opening amount of control hydraulicchange-over valve 7; The 4th electric proportional pressure-reducing valve 4 makes a part of pressure oil flow back to fuel tank through hydraulicchange-over valve 6 by the opening amount of control hydraulicchange-over valve 6, realizes the by-pass throttle speed governing.Simplified model of the present utility model as shown in Figure 3, hydraulic efficiency pressure system utilizes flow regulating valve q1, q2, q3 to realize oil-feed, oil return, by-pass throttle speed governing, realizes the big rigidity of hydraulic efficiency pressure system and stable preferably.
On the basis of above-mentioned crane rotation hydraulic efficiency pressure system, the utility model also provides a kind of control method, and following examples are simply introduced it.
Please referring to Fig. 4, Fig. 4 is the diagram of circuit of crane rotation hydraulic system control method provided by the utility model.
According to formula (1) as can be known hydraulic system pressure and motor output torque have certain relation, i.e. system pressure and load exists necessarily and concerns.Therefore can realize the stable operation of turntable according to the valve port opening of each valve in the variation control system of hydraulic system pressure.
p＝2πnT/q (1)
P---hydraulic system pressure;
The output torque of T---motor;
Q---flow rate of hydraulic system.
As shown in Figure 4, the control method of the crane rotation hydraulic efficiency pressure system that the utility model provides, its control flow following (is example with the rotary motor left-hand rotation):
Step 1 is opened the turntable hydraulic efficiency pressure system, brake cylinder 14 brake offs;
Step 2, whether the oil inlet pressure that detects rotary motor 13 is stable, if unstable rule changes step 3 over to; If it is stable then change step 4 over to;
Step 3, regulate according to following rule: the control current of the 4th electric proportional pressure-reducing valve 4 changes from big to small, thereby reduces the aperture of hydraulicchange-over valve 6; The control current of the 3rd electric proportional pressure-reducing valve 3 changes from small to large, thereby increases the aperture of hydraulicchange-over valve 7; The control current of the first electric proportional pressure-reducing valve 1 changes from small to large, thereby increases the aperture of pilot operated directional control valve 5, reaches to reduce the impact of flow sudden change to system; Change step 2 then over to;
Step 4, turntable enter normal rotary phase;
Step 5, whether the oil inlet pressure that detects rotary motor 13 is stable, if unstable rule changes step 6 over to; If stablize then normally operation;
Step 6, regulate according to following rule: the control current of the 3rd electric proportional pressure-reducing valve 3 transfers to maximum, thereby makes hydraulicchange-over valve 7 be in full-gear; The control current of the 4th electric proportional pressure-reducing valve 4 changes from big to small, thereby reduces the aperture of hydraulicchange-over valve 6; The control current of the first electric proportional pressure-reducing valve 1 changes from big to small, thereby reduces the aperture of pilot operated directional control valve 5; Make rotary motor 13 slow-roll stabilizations;
Step 8, whether the oil inlet pressure that detects rotary motor 13 is stable, if unstable rule changes step 9 over to; If it is stable then change step 10 over to;
Step 9, regulate according to following rule: the control current of the 4th electric proportional pressure-reducing valve 4 changes from small to large, thereby increases the aperture of hydraulicchange-over valve 6; The control current of the 3rd electric proportional pressure-reducing valve 3 changes from big to small, thereby the aperture that reduces hydraulicchange-over valve 7 is to closed condition; The control current of the first electric proportional pressure-reducing valve 1 changes from big to small, thereby the aperture that reduces pilot operated directional control valve 5 is to closed condition; Brake cylinder 14 begins braking simultaneously, makes that the compression shock when rotary motor 13 stops to minimize;
Except above-mentioned crane rotation hydraulic efficiency pressure system, the utility model also provides a kind of hoisting crane, the hydraulic efficiency pressure system that comprises turntable, is installed in the arm on the turntable and drives turntable, hydraulic efficiency pressure system is specially above-mentioned each described crane rotation hydraulic efficiency pressure system, the structure of other each several parts please refer to prior art, and this paper repeats no more.
More than crane rotation hydraulic efficiency pressure system provided by the utility model and hoisting crane are described in detail.Used specific case herein principle of the present utility model and embodiment are set forth, the explanation of above embodiment just is used for helping to understand core concept of the present utility model.Should be understood that; for those skilled in the art; under the prerequisite that does not break away from the utility model principle, can also carry out some improvement and modification to the utility model, these improvement and modification also fall in the protection domain of the utility model claim.
Claims (12)
1. crane rotation hydraulic efficiency pressure system, be used for movable crane, comprise Hydraulic Pump, rotary motor, brake cylinder, it is characterized in that, also comprise the adjustable pilot operated directional control valve of flow, first flow control cock, second flow control valve and braking change-over valve;
The oil outlet of described Hydraulic Pump is told two fuel feeding branch roads, and wherein one the tunnel for driving oil circuit, and another road is a control oil channel;
The driving oil circuit of described Hydraulic Pump connects first oil inlet of described pilot operated directional control valve, and first oil outlet of described pilot operated directional control valve connects the oil inlet of described rotary motor, and second oil outlet of described pilot operated directional control valve connects the return opening of described rotary motor;
The control oil channel of described Hydraulic Pump connects the oil inlet of described braking change-over valve, and the oil outlet of described braking change-over valve connects described brake cylinder;
The oil inlet of described rotary motor is communicated with the oil inlet of described first flow control cock, and the oil outlet of described first flow control cock is communicated with fuel tank;
The return opening of described rotary motor is communicated with the oil inlet of described second flow control valve, and the oil outlet of described second flow control valve is communicated with fuel tank.
2. crane rotation hydraulic efficiency pressure system according to claim 1 is characterized in that, the control oil channel between the oil inlet of described braking change-over valve and the oil outlet of described Hydraulic Pump is provided with solenoid directional control valve; The oil inlet of described solenoid directional control valve is communicated with the oil outlet of described Hydraulic Pump, the oil outlet of described solenoid directional control valve is communicated with the oil inlet of the first electric proportional pressure-reducing valve, the second electric proportional pressure-reducing valve, and the oil outlet of the described first electric proportional pressure-reducing valve and the second electric proportional pressure-reducing valve is connected two control ends of described pilot operated directional control valve respectively.
3. crane rotation hydraulic efficiency pressure system according to claim 2, it is characterized in that, described first flow control cock is specially hydraulicchange-over valve, and and be provided with the 4th electric proportional pressure-reducing valve between the described solenoid directional control valve, the oil inlet of described the 4th electric proportional pressure-reducing valve is communicated with the oil outlet of described solenoid directional control valve, and the oil outlet of described the 4th electric proportional pressure-reducing valve connects the control end of described hydraulicchange-over valve.
4. crane rotation hydraulic efficiency pressure system according to claim 2, it is characterized in that, described second flow control valve is specially hydraulicchange-over valve, and and be provided with the 3rd electric proportional pressure-reducing valve between the described solenoid directional control valve, the oil inlet of described the 3rd electric proportional pressure-reducing valve is communicated with the oil outlet of described solenoid directional control valve, and the oil outlet of described the 3rd electric proportional pressure-reducing valve connects the control end of described hydraulicchange-over valve.
5. according to each described crane rotation hydraulic efficiency pressure system of claim 1 to 4, it is characterized in that described first flow control cock is provided with the first unidirectional by pass valve that is in parallel with it on oil circuit.
6. according to each described crane rotation hydraulic efficiency pressure system of claim 1 to 4, it is characterized in that described second flow control valve is provided with the second unidirectional by pass valve that is in parallel with it on oil circuit.
7. crane rotation hydraulic efficiency pressure system according to claim 6, it is characterized in that, oil circuit between described braking change-over valve and the described brake cylinder is provided with conducting valve, the oil inlet of described conducting valve is communicated with the oil outlet of described braking change-over valve, the oil outlet of described conducting valve connects described brake cylinder, and the hydraulic fluid port that ends of described conducting valve is communicated with fuel tank.
8. crane rotation hydraulic efficiency pressure system according to claim 7, it is characterized in that, be provided with precursor overflow valve between the driving oil circuit of described hydraulic oil pump and the fuel tank, the oil inlet of described precursor overflow valve is communicated with the oil outlet of described hydraulic oil pump, and the oil outlet of described precursor overflow valve and Y mouth all are communicated with fuel tank.
9. crane rotation hydraulic efficiency pressure system according to claim 8, it is characterized in that, be provided with by pass valve between described pilot operated directional control valve and the fuel tank, the oil inlet of described by pass valve is communicated with the 3rd oil outlet of described pilot operated directional control valve, and the oil outlet of described by pass valve is communicated with fuel tank; The control port of described by pass valve is communicated with the 4th oil outlet of described pilot operated directional control valve; Second oil inlet of described pilot operated directional control valve is communicated with fuel tank; The 3rd oil inlet of described pilot operated directional control valve is communicated with the oil outlet of described hydraulic oil pump.
10. crane rotation hydraulic efficiency pressure system according to claim 9 is characterized in that, is provided with mutual series connected flow regulating valve and check valve on oil circuit between the 4th oil outlet of the control port of described by pass valve and described pilot operated directional control valve.
11. crane rotation hydraulic efficiency pressure system according to claim 10 is characterized in that, described pilot operated directional control valve is specially three six-way transfer valves, has three control positioies in left, center, right;
Be communicated with the 4th oil outlet at its second oil inlet of meta, the 3rd oil inlet is communicated with the 3rd oil outlet, and all the other each hydraulic fluid ports end;
Be communicated with second oil outlet at its first oil inlet of left side position, and first oil inlet is communicated with the 4th oil outlet, all the other each hydraulic fluid ports end;
Its first oil inlet is communicated with first oil outlet in right position, and first oil inlet is communicated with the 4th oil outlet, and all the other each hydraulic fluid ports end.
12. a hoisting crane, the hydraulic efficiency pressure system that comprises turntable, is installed in the arm on the described turntable and drives described turntable is characterized in that, described hydraulic efficiency pressure system is specially aforesaid right requirement 1 to 11 each described crane rotation hydraulic efficiency pressure system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010202744282U CN201729610U (en) | 2010-07-26 | 2010-07-26 | Rotary hydraulic system of crane and crane |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010202744282U CN201729610U (en) | 2010-07-26 | 2010-07-26 | Rotary hydraulic system of crane and crane |
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| CN201729610U true CN201729610U (en) | 2011-02-02 |
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| CN2010202744282U Expired - Lifetime CN201729610U (en) | 2010-07-26 | 2010-07-26 | Rotary hydraulic system of crane and crane |
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| 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 |
| CN102275824A (en) * | 2011-07-07 | 2011-12-14 | 长沙中联重工科技发展股份有限公司 | Control method and control system for rotary motion of slewing crane |
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| CN104214148A (en) * | 2014-08-29 | 2014-12-17 | 徐州徐工基础工程机械有限公司 | Intelligent buffering and overflowing device |
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| CN110630570A (en) * | 2019-09-10 | 2019-12-31 | 中国船舶重工集团公司第七一五研究所 | Multi-degree-of-freedom hydraulic damping system |
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