CN201228608Y - Plunger piston hydraulic motor of mechanical-hydraulic leading switch torque-variable rotating cylinder - Google Patents
Plunger piston hydraulic motor of mechanical-hydraulic leading switch torque-variable rotating cylinder Download PDFInfo
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- CN201228608Y CN201228608Y CNU2008200889896U CN200820088989U CN201228608Y CN 201228608 Y CN201228608 Y CN 201228608Y CN U2008200889896 U CNU2008200889896 U CN U2008200889896U CN 200820088989 U CN200820088989 U CN 200820088989U CN 201228608 Y CN201228608 Y CN 201228608Y
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Abstract
The utility model relates to a hydraulic motor and aims to provide a hydraulic pilot switch variable torque rotating cylinder plunger hydraulic motor. The motor comprises a torque output mechanism, a quantitative swash plate, a plunger case, plungers and a plunger cavity, and further comprises a distributor valve block and a hydraulic pilot variable torque driving mechanism, wherein the distributor valve block comprises high-speed switch high-pressure oil supply valves of identical number with the plungers, a high-speed switch oil drainage-oil compensating valve, a pilot valve and a common distributor valve body; and the hydraulic pilot variable torque driving mechanism comprises a housing, a variable driving ring and a variable adjuster. The utility model has the advantages that the variable torque control is realized; when the load torque is smaller, the energy consumption can be greatly reduced; when the duty ratio of replacement of the plungers is less than 0.5, the hydraulic motor can smoothly enter under the operating condition of the pump, the zero discharge is not required, and the problem of instability near to zero point does not exist; and the response speed of variable of the hydraulic motor is increased by one order of magnitude.
Description
Technical field
The utility model relates to oil hydraulic motor, and in particular, the utility model relates to a kind of machine solution guide switch changing torque rotating cylinder barrel plunger piston hydraulic slave motor.
Background technique
Thereby plunger piston hydraulic motor is to rely on pressure oil to act on to make motor output shaft obtain certain torque on the plunger, for plunger can alternately be communicated with pressure hydraulic fluid port and return opening, must adopt flow distribution apparatus, plunger piston hydraulic motor adopts valve plate distribution more at present, and the main devices that is adopted in the valve plate distribution is exactly an oil distribution casing.The similar plate valve of oil distribution casing, be fitted in the cylinder body end face that has assignment hole by plane with two arcs (" waist shape ") window, make cylinder body and oil distribution casing relative rotation on face perpendicular to motor drive shaft, the relative position of window on the oil distribution casing and the perforate of cylinder body end face is arranged according to certain rules, so that be in plunger case in fuel feeding or the oil extraction stroke can replace with the motor body on confession, oil extraction communicates, and guarantees isolation and sealing between each oil pocket.Because the angle of release of two arc-shaped windows, position all can not real time alterings on the oil distribution casing, thereby oil hydraulic motor can't realize variable by oil distribution mechanism, promptly to the continuous adjusting of output torque and discharge capacity.Up to the present, all can only realize variable by the swash plate angle of inclination of real-time regulated oil hydraulic motor opposite side at the formal variable hydraulic motor of selling on the market.And there are two weakness in the variable mode that the swash plate angle of inclination is regulated in this traditional passing through:
1. the hydraulic coupling that each plunger produces in the oil hydraulic motor, when driving the oil hydraulic motor rotation, its power on the swash plate of acting on also can produce one with swash plate angle of inclination controlling party to consistent moment of torsion, and this moment of torsion changes along with the change of oil hydraulic motor corner, a plurality of plungers are arranged as far as possible but still can't cancel out each other in inside fully, the moment of torsion of this part fluctuation finally all has been added on the stroking mechanism at control swash plate angle of inclination.Stroking mechanism needs sizable area and drives in order to overcome the moment of torsion of this fluctuation, has seriously limited the speed of response of oil hydraulic motor.
2. to switch to the transition point of pump operating mode be that discharge capacity is zero point to oil hydraulic motor.Therefore, for switch to the pump operating mode with reclaim to slow down, the energy of braking process, the discharge capacity controlling mechanism of oil hydraulic motor must Zero Crossing Point, not only the stroke of stroking mechanism is big, speed of response is slow, but also is easy to cause near the instability zero point.
The model utility content
The purpose of this utility model is to overcome deficiency of the prior art, and a kind of machine solution guide switch changing torque rotating cylinder barrel plunger piston hydraulic slave motor is provided.
In order to overcome the above problems, the utility model is to be achieved through the following technical solutions.
The utility model provides a kind of machine solution guide switch changing torque rotating cylinder barrel plunger piston hydraulic slave motor, comprises moment of torsion output mechanism, quantitative swash plate, plunger case, plunger and plunger cavity, comprises that also oil distributing valve group and machine solution guide become torque driving mechanism;
Described oil distributing valve group by with speed-sensitive switch high-pressure oil feed valve, the speed-sensitive switch oil extraction-Fill valve of number of plungers equal number, pilot valve and public oil distributing valve body constitute; Each plunger and the corresponding speed-sensitive switch high-pressure oil feed valve of corresponding plunger cavity, a speed-sensitive switch oil extraction-Fill valve and a pilot valve; Each speed-sensitive switch high-pressure oil feed valve and each speed-sensitive switch oil extraction-Fill valve include spool, spring, spring chamber, axial hydraulic fluid port, circumferential hydraulic fluid port separately; The speed-sensitive switch high-pressure oil feed valve and the speed-sensitive switch oil extraction-Fill valve of each plunger correspondence all are arranged side by side, and its axial hydraulic fluid port all is communicated with corresponding plunger cavity; The circumferential hydraulic fluid port of each speed-sensitive switch high-pressure oil feed valve all is communicated with the high pressure hydraulic fluid port, and the circumferential hydraulic fluid port of each speed-sensitive switch oil extraction-Fill valve all is communicated with the return opening of band back pressure; Each pilot valve includes high-pressure oil feed control step, oil extraction-repairing control step separately; The spring chamber of each speed-sensitive switch high-pressure oil feed valve all is communicated with high-pressure oil feed control step on the corresponding pilot valve, the spring chamber of each speed-sensitive switch oil extraction-Fill valve all with pilot valve accordingly on oil extraction-repairing control step and be communicated with; Between the end face and oil extraction-repairing control step of each pilot valve, between oil extraction-repairing control step and the high-pressure oil feed control step, between high-pressure oil feed control step and the annular end face cavity volume is arranged respectively near housing; Each pilot valve is communicated with the return opening of band back pressure at the end face near case side, and opposite side has two end faces, and the high pressure end face is communicated with the high pressure hydraulic fluid port, and annular end face is communicated with the return opening of band back pressure; Each pilot valve is controlled step and is communicated with near the return opening of the cavity volume between the case side end face with the band back pressure in oil extraction-repairing, is communicated with guide's high pressure hydraulic fluid port with cavity volume between the annular end face at high-pressure oil feed control step, the cavity volume of controlling between the step in high-pressure oil feed control step and oil extraction-repairing is communicated with plunger cavity accordingly; All pilot valves all are positioned on the same cross section;
Described machine solution guide becomes torque driving mechanism by housing, the variable driving ring, and quantity governor is formed; The axial end of described housing and described oil distributing valve body are positioned at and are provided with static pressure between the end face of plunger opposite side and support; The axial centre position of described variable driving ring is consistent with cross section, described pilot valve place, and inwall contacts and relatively rotates near case side with described all pilot valves; The inwall center of variable driving ring is parallel with the central axis of described plunger case, and along suction oil content boundary line direction a fixed bias is being arranged; The outer wall of variable driving ring is positioned at housing, can and only can be along moving freely perpendicular to suction oil content boundary line direction in housing; It is circumferential that described quantity governor is positioned at housing, and central axis is perpendicular to suction oil content boundary line direction.
As a kind of improvement, described quantity governor is any one in mechanical variables regulator, single hydraulic fluid port hydraulic pressure quantity governor, two hydraulic fluid port list control hydraulic pressure quantity governor, four kinds of structures of two control hydraulic pressure quantity governors, wherein:
The mechanical variables regulator comprises the variable adjustable lever, and variable adjustable lever and variable driving ring are rigidly connected;
Single hydraulic fluid port hydraulic pressure quantity governor comprises variable piston, the Variable Control hydraulic fluid port, and Returnning spring and spring seat, variable piston one side contacts with the variable driving ring, and opposite side is communicated with the Variable Control hydraulic fluid port; Spring seat one side contacts with the variable driving ring, and opposite side contacts with the spring-go position that resets; Spring chamber passes spring seat and is communicated with the return opening of band back pressure;
Two hydraulic fluid port list control hydraulic pressure quantity governors comprise 2 variable pistons, the Variable Control hydraulic fluid port, and Returnning spring and Variable Control return opening, variable piston one side contacts with the variable driving ring, and opposite side is communicated with the Variable Control hydraulic fluid port; Spring seat one side contacts with the variable driving ring, and opposite side contacts with the spring-go position that resets; Spring chamber is communicated with the Variable Control return opening;
Two control hydraulic pressure quantity governors comprise 2 variable pistons, and 2 Variable Control hydraulic fluid ports and 2 Returnning springs, variable piston and Variable Control hydraulic fluid port, Returnning spring are corresponding one by one; One side of each variable piston all contacts with the variable driving ring, and opposite side all contacts with corresponding Returnning spring; 2 spring chambers all are communicated with the Variable Control hydraulic fluid port.
As a kind of improvement, the charge oil pressure of described guide's high pressure hydraulic fluid port is slightly higher than the charge oil pressure of high pressure hydraulic fluid port, and flow guarantees that just in time all high-pressure oil feed valve core quick closedowns are required, makes that all speed-sensitive switch high-pressure oil feed valves can both quick closedown.
As a kind of improvement, described oil distributing valve body axially is being divided into three: plunger cavity separating valve body, main valve body, guide's valve body; Plunger cavity separating valve body, main valve body, guide's valve body are rigidly connected on the plunger case by pin; The outer rim of all hydraulic fluid ports all is provided with seal ring between plunger cavity separating valve body and main valve body, main valve body and guide's valve body, plunger cavity separating valve body and the plunger case.
As a kind of improvement, the high-pressure oil feed of described pilot valve control step is just in time opposite with the concave and convex direction of oil extraction-repairing control step, makes a pilot valve can simultaneously, synchronously control a high-pressure oil feed valve and an oil extraction-repairing control valve.
As a kind of improvement, the width of the high-pressure oil feed of described pilot valve control step and oil extraction-repairing control step makes pilot valve can respond the variation of plunger position fast all with the undercut groove width is consistent accordingly on guide's valve body.
As a kind of improvement, when described pilot valve is in meta, cavity volume between high-pressure oil feed control step and oil extraction-repairing control step, from the covering amount that is covered by high-pressure oil feed control step, just in time equal the inwall center of variable driving ring and the fixed bias displacement between the plunger case central axis, make the high-pressure oil feed valve that just in time is positioned on the suction oil content boundary line just in time to open oil suction in this position; Cavity volume between oil extraction-repairing control step and the close case side end face, from covering amount by oil extraction-repairing control step covers, just in time equal the inwall center of variable driving ring and the fixed bias displacement between the plunger case central axis, make the oil extraction-Fill valve that just in time is positioned on the suction oil content boundary line just in time to open oil extraction in this position.
Attached: a kind of change torque control method that is used for above-mentioned machine solution guide switch changing torque rotating cylinder barrel plunger piston hydraulic slave motor may further comprise the steps:
(1) according to the requirement to the output torque size, Moderator Variable regulator; When quantity governor is the mechanical variables regulator, regulate the position of its variable adjustable lever; When quantity governor is single hydraulic fluid port hydraulic pressure quantity governor, two hydraulic fluid port list control hydraulic pressure quantity governor or two control hydraulic pressure quantity governor wherein during any one hydraulic pressure quantity governor, regulate the pressure of its Variable Control hydraulic fluid port; In order to change dutycycle switching time of each speed-sensitive switch high-pressure oil feed valve;
(2) opening time of control speed-sensitive switch high-pressure oil feed valve, make only when speed-sensitive switch high-pressure oil feed opening of valves, can promote corresponding plunger acting by the plunger cavity that is positioned at the oil suction district from the oil suction of high pressure hydraulic fluid port; Be positioned at other plunger cavities in oil suction district, equal speed-sensitive switch oil extraction-Fill valves by communicating with return opening, directly from the return opening oil suction, replenish the cavity that plunger motion produces, but can not promote the plunger acting, guarantee that average output torque is directly proportional with the dutycycle of displacement in whole plunger oil suction stroke of speed-sensitive switch high-pressure oil feed valve opening time section inner plunger;
(3) by the real-time regulated to displacement dutycycle in whole plunger oil suction stroke of speed-sensitive switch high-pressure oil feed valve opening time section inner plunger, the average torque that output is directly proportional with dutycycle is realized becoming moment of torsion and is controlled; Pass between dutycycle and the average torque is:
Make plunger displacement dutycycle D=X
Open/ X
Max
T=(2D-1) * (D
m* P * η
Machine* η
Valve)
The pilot valve displacement amplitude is that the displacement y of variable driving ring and the pass between the plunger displacement dutycycle are:
Plunger displacement dutycycle D=X
Open/ X
Max=1-cos[2tg (y/y0)] }/2
Wherein: D is the plunger displacement dutycycle, X
OpenBe the plunger displacement in the speed-sensitive switch high-pressure oil feed valve opening time section, X
MaxBe the total travel of plunger displacement, T is for needing the average torque of output, D
mBe the discharge capacity of oil hydraulic motor, P is the pressure of pressure hydraulic fluid port, η
MachineBe the mechanical efficiency of oil hydraulic motor, η
ValveBe the efficient of oil distributing valve group control plunger cavity, y0 is the inwall center of variable driving ring and the fixed bias displacement between the plunger case central axis, and y is the displacement of variable driving ring for the pilot valve displacement amplitude;
(4) direction of y is consistent with the sense of rotation of oil hydraulic motor, if oil hydraulic motor counter-rotating, then variable driving ring reverse direction actuation.
By said structure and controlling method, each plunger whenever turns around, and has all experienced 6 states (4 major states and 2 transition states):
(1) state 1: the high drive state: the pilot valve displacement is greater than the fixed bias between variable driving ring and the plunger case central axis, and plunger advancement; Under the effect of pilot valve, the spring chamber of plunger cavity and high-pressure oil feed valve is linked up, the high-pressure oil feed valve is opened under the pressure effect of high pressure hydraulic fluid port, thereby the pressure of plunger cavity approaches the pressure of high pressure hydraulic fluid port, plunger cavity is linked up with the spring chamber of oil extraction-Fill valve simultaneously, and oil extraction-Fill valve keeps closing under the pressure effect of plunger cavity;
(2) state 2,3: the idle stroke state: the pilot valve displacement is between the fixed bias between positive and negative variable driving ring and the plunger case central axis, and plunger advancement; Under the effect of pilot valve, the spring chamber of guide's high pressure hydraulic fluid port and high-pressure oil feed valve is linked up, the quick closedown under the pressure effect of guide's high pressure oil mouth of high-pressure oil feed valve, plunger moves on and causes the plunger cavity volume to increase, pressure drops to the back pressure that is lower than return opening fast, plunger cavity is linked up with the spring chamber of oil extraction-Fill valve simultaneously, and oil extraction-Fill valve is opened after the pressure of plunger cavity is reduced to below the return opening back pressure; Wherein state 2 is oil extraction-this transition state of Fill valve opening process;
(3) state 4: normal oil return state: the pilot valve displacement is less than negative variable driving ring and the fixed bias between the plunger case central axis, and plunger retreats; Under the effect of pilot valve, the return opening of band back pressure and the spring chamber of oil extraction-Fill valve are linked up, oil extraction-Fill valve is opened under the pressure effect of plunger cavity, thereby the pressure of plunger cavity approaches the back pressure of return opening, the spring chamber of guide's high pressure hydraulic fluid port and high-pressure oil feed valve is linked up simultaneously, and the high-pressure oil feed valve keeps cutting out under the pressure effect of guide's high pressure oil mouth;
(4) state 5,6: the pump operating mode: the pilot valve displacement is between the fixed bias between positive and negative variable driving ring and the plunger case central axis, and plunger retreats; Under the effect of pilot valve, the spring chamber of plunger cavity and oil extraction-Fill valve is linked up, oil extraction-Fill valve is closed under the pressure effect of plunger cavity, plunger continues to retreat and causes the plunger cavity volume to reduce, pressure is climbed to the pressure above guide's high pressure hydraulic fluid port, guide's high pressure hydraulic fluid port is linked up with the spring chamber of high-pressure oil feed valve simultaneously, and the high-pressure oil feed valve is opened after the pressure of plunger cavity rises to more than guide's high pressure oil mouth pressure; Wherein state 5 is this transition state of high-pressure oil feed opening of valves process.
Compared with prior art, the beneficial effects of the utility model are:
(1) become moment of torsion control: the utility model can be by the real-time regulated to the dutycycle in whole plunger oil suction stroke of the plunger displacement in the speed-sensitive switch high-pressure oil feed valve opening time section, the average torque that output is directly proportional with dutycycle, realize that switch becomes moment of torsion control, switch becomes the discharge capacity of moment of torsion control both change oil hydraulic motor, also do not change charge oil pressure, but it has finally directly changed the output torque of oil hydraulic motor;
(2) it is energy-conservation: when load torque is less, part is positioned at the plunger cavity in oil suction district no longer from the oil suction of high pressure hydraulic fluid port, but by oil extraction-Fill valve from the return opening oil suction, do not need pressure oil is wasted on the extra throttling control valve mouth, thereby saved a large amount of energy consumptions;
(3) pump operating mode: when the plunger displacement dutycycle less than 0.5 the time, oil hydraulic motor has just entered the operating mode of pump reposefully, i.e. the output torque opposite with sense of rotation is simultaneously to high pressure hydraulic fluid port discharge high pressure oil;
(4) speed of response improves an order of magnitude: the hydraulic coupling that each plunger produces in the conventional hydraulic motors, when driving the oil hydraulic motor rotation, its power on the swash plate of acting on also can produce one with swash plate angle of inclination controlling party to consistent moment of torsion, and this moment of torsion changes along with the change of oil hydraulic motor corner, a plurality of plungers are arranged as far as possible but still can't cancel out each other in inside fully, the moment of torsion of this part fluctuation finally all has been added on the stroking mechanism at control swash plate angle of inclination, stroking mechanism is in order to overcome the moment of torsion of this fluctuation, need sizable area and drive, seriously limited the speed of response of oil hydraulic motor; And the utility model frees the variable driving mechanism from the huge unbalanced moment of swash plate, only need overcome each pilot valve and act on unbalanced force on the variable driving ring, unbalanced force has dwindled an order of magnitude, thereby the variable speed of response of oil hydraulic motor has been improved an order of magnitude;
(5) avoided the zero passage problem: the transition point that conventional hydraulic motors switches to the pump operating mode is that discharge capacity is zero point, therefore the pump operating mode is slowed down to reclaim, the energy of braking process in order to switch to, the necessary Zero Crossing Point of the discharge capacity controlling mechanism of oil hydraulic motor, not only the stroke of stroking mechanism is big, speed of response is slow, but also is easy to cause near the instability zero point; And the utility model only need be transferred to the plunger displacement dutycycle less than 0.5, and oil hydraulic motor has just entered the operating mode of pump reposefully, does not need through discharge capacity zero point, thereby does not also have near zero point unstable problem.
Description of drawings
Fig. 1 is the utility model structural representation.
Fig. 2 is the structural representation that oil distributing valve group and machine solution guide become torque driving mechanism in the utility model.
Fig. 3 is a pilot valve and the structural representation that becomes torque driving mechanism place section (adopting the mechanical variables regulator) in the utility model.
Fig. 4 is a pilot valve and the structural representation that becomes torque driving mechanism place section (adopting single hydraulic fluid port hydraulic pressure quantity governor) in the utility model.
Fig. 5 is a pilot valve and the structural representation that becomes torque driving mechanism place section (adopting two hydraulic fluid port list control hydraulic pressure quantity governors) in the utility model.
Fig. 6 is a pilot valve and the structural representation that becomes torque driving mechanism place section (adopting two control hydraulic pressure quantity governors) in the utility model.
Fig. 7 is each main valve and the scheme of installation that becomes torque driving mechanism in the utility model.
Fig. 8 is the scheme of installation that each guide's spool is installed in guide's valve body in the utility model.
Fig. 9 is the scheme of installation that each part of quantity governor is installed in housing in the utility model (is example with two hydraulic fluid port list control hydraulic pressure quantity governors).
Figure 10 is in the utility model above guide's valve body, the corresponding relation figure of each valve port step and hydraulic oil port.
Figure 11 be in the utility model each above guide's spool, the corresponding relation figure of each valve port step and hydraulic oil port.
Figure 12 is the motion flow control graph of each plunger position of the utility model and its related valves.
Figure 13 is each main valve of the utility model and the pilot valve position view at state A.
Figure 14 be each main valve of the utility model and pilot valve at state B, the position view of C.
Figure 15 is each main valve of the utility model and the pilot valve position view at state D.
Figure 16 be each main valve of the utility model and pilot valve at state E, the position view of F.
Among the figure, 1 plunger case, 2 plungers, 3 plunger cavities, 4 seal rings, 5 plunger cavity separating valve bodies, 6 speed-sensitive switch high-pressure oil feed valve shafts are to hydraulic fluid port, 7 speed-sensitive switch high-pressure oil feed valves, the circumferential hydraulic fluid port of 8 speed-sensitive switch high-pressure oil feed valves, 9 speed-sensitive switch high-pressure oil feed valve spring chambeies, the axial hydraulic fluid port of 10 speed-sensitive switch oil extraction-Fill valves, 11 speed-sensitive switch oil extraction-Fill valves, the circumferential hydraulic fluid port of 12 speed-sensitive switch oil extraction-Fill valves, 13 speed-sensitive switches oil extraction-Fill valve spring chamber, 14 main valve bodies, 15 guide's valve bodies, 16 pilot valves, 17 variable driving rings, 18 housings, the return opening of 19 band back pressures, 20 high pressure hydraulic fluid ports, 21 guide's high pressure hydraulic fluid ports, 22 variable adjustable levers, 23 Variable Control hydraulic fluid ports, 24 variable pistons, 25 spring seats, 26 Returnning springs, 27 Variable Control return openings, 28 speed-sensitive switch high-pressure oil feed valve cores, 29 speed-sensitive switch high-pressure oil feed valve springs, 30 speed-sensitive switches oil extraction-Fill valve spool, 31 speed-sensitive switches oil extraction-Fill valve spring, 32 pilot valve high-pressure oil feeds control step, 33 pilot valves oil extraction-repairing control step, 34 pilot valves are near the end face of case side, 35 pilot valve high pressure end faces, 36 pilot valves are at oil extraction-repairing control step and near the cavity volume between the case side end face, the cavity volume of 37 pilot valves between high-pressure oil feed control step and annular end face, the cavity volume of 38 pilot valves between high-pressure oil feed control step and oil extraction-repairing control step, 39 pins, 40 moment of torsion output mechanisms, 41 quantitative swash plates, 42 oil distributing valve groups, 43 machine liquid become torque driving mechanism, 44 pilot valve annular end faces.
Embodiment
In conjunction with the accompanying drawings, below by specific embodiment the utility model is elaborated.
A kind of machine solution guide switch changing torque in this specific embodiment is joined the quantitative plunger piston hydraulic motor of oil type rotating cylinder cartridge type, by a quantitative plunger piston hydraulic motor repacking of common rotating cylinder cartridge type.
Remove the bonnet and the oil distribution casing of plunger-type quantitative hydraulic motor, the end face of plunger case be processed into the plane, and between per two plunger cavities of plunger case pin hole processings all, the pin-and-hole position is consistent with the oil distributing valve body in the utility model.Oil-distribution component of the present utility model is installed to original bonnet of oil hydraulic motor and oil distribution casing position, and pin is inserted in the fresh processed pin-and-hole of plunger case.A common rotating sleeve plunger-type quantitative hydraulic motor has just been repacked into one and has been had the plunger variable oil hydraulic motor of machine solution guide switch changing torque function.
According to foregoing structure, the working procedure of this plunger variable oil hydraulic motor is shown in accompanying drawing 13～16.Each plunger whenever turns around, and has all experienced 6 states (4 major states and 2 transition states):
(1) state A: high drive state: the pilot valve displacement is greater than the fixed bias between variable driving ring and the plunger case central axis, and plunger advancement; Under the effect of pilot valve, the spring chamber of plunger cavity and high-pressure oil feed valve is linked up, the high-pressure oil feed valve is opened under the pressure effect of high pressure hydraulic fluid port, thereby the pressure of plunger cavity approaches the pressure of high pressure hydraulic fluid port, plunger cavity is linked up with the spring chamber of oil extraction-Fill valve simultaneously, and oil extraction-Fill valve keeps closing under the pressure effect of plunger cavity;
(2) state B, C: idle stroke state: the pilot valve displacement is between the fixed bias between positive and negative variable driving ring and the plunger case central axis, and plunger advancement; Under the effect of pilot valve, the spring chamber of guide's high pressure hydraulic fluid port and high-pressure oil feed valve is linked up, the quick closedown under the pressure effect of guide's high pressure oil mouth of high-pressure oil feed valve, plunger moves on and causes the plunger cavity volume to increase, pressure drops to the back pressure that is lower than return opening fast, plunger cavity is linked up with the spring chamber of oil extraction-Fill valve simultaneously, and oil extraction-Fill valve is opened after the pressure of plunger cavity is reduced to below the return opening back pressure; Wherein state 2 is oil extraction-this transition state of Fill valve opening process;
(3) state D: normal oil return state: the pilot valve displacement is less than negative variable driving ring and the fixed bias between the plunger case central axis, and plunger retreats; Under the effect of pilot valve, the return opening of band back pressure and the spring chamber of oil extraction-Fill valve are linked up, oil extraction-Fill valve is opened under the pressure effect of plunger cavity, thereby the pressure of plunger cavity approaches the back pressure of return opening, the spring chamber of guide's high pressure hydraulic fluid port and high-pressure oil feed valve is linked up simultaneously, and the high-pressure oil feed valve keeps cutting out under the pressure effect of guide's high pressure oil mouth;
(4) state E, F: pump operating mode: the pilot valve displacement is between the fixed bias between positive and negative variable driving ring and the plunger case central axis, and plunger retreats; Under the effect of pilot valve, the spring chamber of plunger cavity and oil extraction-Fill valve is linked up, oil extraction-Fill valve is closed under the pressure effect of plunger cavity, plunger continues to retreat and causes the plunger cavity volume to reduce, pressure is climbed to the pressure above guide's high pressure hydraulic fluid port, guide's high pressure hydraulic fluid port is linked up with the spring chamber of high-pressure oil feed valve simultaneously, and the high-pressure oil feed valve is opened after the pressure of plunger cavity rises to more than guide's high pressure oil mouth pressure; Wherein state 5 is this transition state of high-pressure oil feed opening of valves process.
At last, it should be noted that above what enumerate only is specific embodiment of the utility model.Obviously, the utility model is not limited to above embodiment, and a lot of distortion can also be arranged.All distortion that those of ordinary skill in the art can directly derive or associate from the disclosed content of the utility model all should be thought protection domain of the present utility model.
Claims (7)
1, a kind of machine solution guide switch changing torque rotating cylinder barrel plunger piston hydraulic slave motor comprises moment of torsion output mechanism, quantitative swash plate, plunger case, plunger and plunger cavity, it is characterized in that, comprises that also oil distributing valve group and machine solution guide become torque driving mechanism;
Described oil distributing valve group by with speed-sensitive switch high-pressure oil feed valve, the speed-sensitive switch oil extraction-Fill valve of number of plungers equal number, pilot valve and public oil distributing valve body constitute; Each plunger and the corresponding speed-sensitive switch high-pressure oil feed valve of corresponding plunger cavity, a speed-sensitive switch oil extraction-Fill valve and a pilot valve; Each speed-sensitive switch high-pressure oil feed valve and each speed-sensitive switch oil extraction-Fill valve include spool, spring, spring chamber, axial hydraulic fluid port and circumferential hydraulic fluid port separately; The speed-sensitive switch high-pressure oil feed valve and the speed-sensitive switch oil extraction-Fill valve of each plunger correspondence all are arranged side by side, and its axial hydraulic fluid port all is communicated with corresponding plunger cavity; The circumferential hydraulic fluid port of each speed-sensitive switch high-pressure oil feed valve all is communicated with the high pressure hydraulic fluid port, and the circumferential hydraulic fluid port of each speed-sensitive switch oil extraction-Fill valve all is communicated with the return opening of band back pressure; Each pilot valve includes high-pressure oil feed control step, oil extraction-repairing control step separately; The spring chamber of each speed-sensitive switch high-pressure oil feed valve all is communicated with high-pressure oil feed control step on the corresponding pilot valve, the spring chamber of each speed-sensitive switch oil extraction-Fill valve all with pilot valve accordingly on oil extraction-repairing control step and be communicated with; Between the end face and oil extraction-repairing control step of each pilot valve, between oil extraction-repairing control step and the high-pressure oil feed control step, between high-pressure oil feed control step and the annular end face cavity volume is arranged respectively near housing; Each pilot valve is communicated with the return opening of band back pressure at the end face near case side, and opposite side has two end faces, and the high pressure end face is communicated with the high pressure hydraulic fluid port, and annular end face is communicated with the return opening of band back pressure; Each pilot valve is controlled step and is communicated with near the return opening of the cavity volume between the case side end face with the band back pressure in oil extraction-repairing, is communicated with guide's high pressure hydraulic fluid port with cavity volume between the annular end face at high-pressure oil feed control step, the cavity volume of controlling between the step in high-pressure oil feed control step and oil extraction-repairing is communicated with plunger cavity accordingly; All pilot valves all are positioned on the same cross section;
Described machine solution guide becomes torque driving mechanism and is made up of housing, variable driving ring, quantity governor; The axial end of described housing and described oil distributing valve body are positioned at and are provided with static pressure between the end face of plunger opposite side and support; The axial centre position of described variable driving ring is consistent with cross section, described pilot valve place, and inwall contacts and relatively rotates near case side with described all pilot valves; The inwall center of variable driving ring is parallel with the central axis of described plunger case, and along suction oil content boundary line direction a fixed bias is being arranged; The outer wall of variable driving ring is positioned at housing, can and only can be along moving freely perpendicular to suction oil content boundary line direction in housing; It is circumferential that described quantity governor is positioned at housing, and central axis is perpendicular to suction oil content boundary line direction.
2, machine solution guide switch changing torque rotating cylinder barrel plunger piston hydraulic slave motor according to claim 1, it is characterized in that, described quantity governor is any one in mechanical variables regulator, single hydraulic fluid port hydraulic pressure quantity governor, two hydraulic fluid port list control hydraulic pressure quantity governor, four kinds of structures of two control hydraulic pressure quantity governors, wherein:
The mechanical variables regulator comprises the variable adjustable lever, and variable adjustable lever and variable driving ring are rigidly connected;
Single hydraulic fluid port hydraulic pressure quantity governor comprises variable piston, the Variable Control hydraulic fluid port, and Returnning spring and spring seat, variable piston one side contacts with the variable driving ring, and opposite side is communicated with the Variable Control hydraulic fluid port; Spring seat one side contacts with the variable driving ring, and opposite side contacts with the spring-go position that resets; Spring chamber passes spring seat and is communicated with the return opening of band back pressure;
Two hydraulic fluid port list control hydraulic pressure quantity governors comprise 2 variable pistons, the Variable Control hydraulic fluid port, and Returnning spring and Variable Control return opening, variable piston one side contacts with the variable driving ring, and opposite side is communicated with the Variable Control hydraulic fluid port; Spring seat one side contacts with the variable driving ring, and opposite side contacts with the spring-go position that resets; Spring chamber is communicated with the Variable Control return opening;
Two control hydraulic pressure quantity governors comprise 2 variable pistons, and 2 Variable Control hydraulic fluid ports and 2 Returnning springs, variable piston and Variable Control hydraulic fluid port, Returnning spring are corresponding one by one; One side of each variable piston all contacts with the variable driving ring, and opposite side all contacts with corresponding Returnning spring; 2 spring chambers all are communicated with the Variable Control hydraulic fluid port.
3, machine solution guide switch changing torque rotating cylinder barrel plunger piston hydraulic slave motor according to claim 1, it is characterized in that, the charge oil pressure of described guide's high pressure hydraulic fluid port is slightly higher than the charge oil pressure of high pressure hydraulic fluid port, flow guarantees that just in time all high-pressure oil feed valve core quick closedowns are required, makes that all speed-sensitive switch high-pressure oil feed valves can both quick closedown.
4, machine solution guide switch changing torque rotating cylinder barrel plunger piston hydraulic slave motor according to claim 1 is characterized in that, described oil distributing valve body axially is being divided into three: plunger cavity separating valve body, main valve body, guide's valve body; Plunger cavity separating valve body, main valve body, guide's valve body are rigidly connected on the plunger case by pin; The outer rim of all hydraulic fluid ports all is provided with seal ring between plunger cavity separating valve body and main valve body, main valve body and guide's valve body, plunger cavity separating valve body and the plunger case.
5, machine solution guide switch changing torque rotating cylinder barrel plunger piston hydraulic slave motor according to claim 1, it is characterized in that, the high-pressure oil feed control step of described pilot valve is just in time opposite with the concave and convex direction of oil extraction-repairing control step, makes a pilot valve can simultaneously, synchronously control a high-pressure oil feed valve and an oil extraction-repairing control valve.
6, machine solution guide switch changing torque rotating cylinder barrel plunger piston hydraulic slave motor according to claim 1, it is characterized in that, the width that step is controlled in the high-pressure oil feed control step of described pilot valve and oil extraction-repairing all with the undercut groove width is consistent accordingly on guide's valve body, makes pilot valve can respond the variation of plunger position fast.
7, machine solution guide switch changing torque rotating cylinder barrel plunger piston hydraulic slave motor according to claim 1, it is characterized in that, when described pilot valve is in meta, cavity volume between high-pressure oil feed control step and oil extraction-repairing control step, from the covering amount that is covered by high-pressure oil feed control step, just in time equal the inwall center of variable driving ring and the fixed bias displacement between the plunger case central axis, make the high-pressure oil feed valve that just in time is positioned on the suction oil content boundary line just in time to open oil suction in this position; Cavity volume between oil extraction-repairing control step and the close case side end face, from covering amount by oil extraction-repairing control step covers, just in time equal the inwall center of variable driving ring and the fixed bias displacement between the plunger case central axis, make the oil extraction-Fill valve that just in time is positioned on the suction oil content boundary line just in time to open oil extraction in this position.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008200889896U CN201228608Y (en) | 2008-06-20 | 2008-06-20 | Plunger piston hydraulic motor of mechanical-hydraulic leading switch torque-variable rotating cylinder |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008200889896U CN201228608Y (en) | 2008-06-20 | 2008-06-20 | Plunger piston hydraulic motor of mechanical-hydraulic leading switch torque-variable rotating cylinder |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201228608Y true CN201228608Y (en) | 2009-04-29 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2008200889896U Expired - Fee Related CN201228608Y (en) | 2008-06-20 | 2008-06-20 | Plunger piston hydraulic motor of mechanical-hydraulic leading switch torque-variable rotating cylinder |
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| Country | Link |
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| CN (1) | CN201228608Y (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104405575A (en) * | 2014-11-03 | 2015-03-11 | 南京萨伯工业设计研究院有限公司 | Improved hydraulic motor and assembly test method thereof |
-
2008
- 2008-06-20 CN CNU2008200889896U patent/CN201228608Y/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104405575A (en) * | 2014-11-03 | 2015-03-11 | 南京萨伯工业设计研究院有限公司 | Improved hydraulic motor and assembly test method thereof |
| CN104405575B (en) * | 2014-11-03 | 2017-04-26 | 桂林理工大学 | Improved hydraulic motor and assembly test method thereof |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20090429 Termination date: 20110620 |