CN101302992A - Plunger piston hydraulic slave motor machine solution guide switch changing torque oil distributing component as well as method for changing torque - Google Patents
Plunger piston hydraulic slave motor machine solution guide switch changing torque oil distributing component as well as method for changing torque Download PDFInfo
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- CN101302992A CN101302992A CNA2008100635451A CN200810063545A CN101302992A CN 101302992 A CN101302992 A CN 101302992A CN A2008100635451 A CNA2008100635451 A CN A2008100635451A CN 200810063545 A CN200810063545 A CN 200810063545A CN 101302992 A CN101302992 A CN 101302992A
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- 238000006073 displacement reaction Methods 0.000 claims abstract description 42
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- 239000012530 fluid Substances 0.000 claims description 47
- 230000001276 controlling effect Effects 0.000 claims description 9
- 230000001105 regulatory effect Effects 0.000 claims description 5
- 238000000605 extraction Methods 0.000 claims description 4
- 230000007246 mechanism Effects 0.000 abstract description 12
- 239000007788 liquid Substances 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 184
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- 238000013459 approach Methods 0.000 description 4
- 230000008878 coupling Effects 0.000 description 2
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- 238000005859 coupling reaction Methods 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
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- 230000009286 beneficial effect Effects 0.000 description 1
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- 238000004134 energy conservation Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
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Abstract
The invention relates to an oil distribution mechanism of a hydraulic motor and a control method thereof, aiming at providing a machine liquid pilot switch changeable torque oil distribution component of a plunger hydraulic motor, which comprises a plunger cylinder barrel, plungers and a plunger cavity. The component also comprises an oil distribution valve set and a variable driving loop, wherein, the oil distribution valve set is composed of high speed switch high pressure oil supply valves, high speed switch oil drain-oil recharging valves, pilot valves and public oil distribution valve bodies, the quantity of which is the same as the plungers and the variable driving loop is used for driving the oil distribution valve set to work. The invention also provides a method for changing the torque of the oil distribution component: the variable driving loop is adjusted according to the requirements for output torque to change the duty ratio of the opening and closing time of varied high speed switch high pressure oil supply valves; the opening time of the high speed switch high pressure oil supply valves is controlled to guarantee that average output torque is in direct proportion to the duty ratio of the displacement of the plungers in the whole stroke when the plungers absorb oil within the time period when the high speed switch high pressure oil supply valves are opened; and an average torque that is in direct proportion to the duty ratio is output so as to realize the control over changeable torque.
Description
Technical field
The present invention relates to a kind of oil hydraulic motor oil distribution mechanism and controlling method thereof, in particular, relate to plunger hydraulic motor mechanical-hydraulic leading switch variable-torque oil-distribution component and method for changing torque.
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.
Summary of the invention
The objective of the invention is to overcome deficiency of the prior art, a kind of plunger hydraulic motor mechanical-hydraulic leading switch variable-torque oil-distribution component is provided, further object of the present invention is to provide the method for changing torque of this oil-distribution component.
In order to overcome the above problems, the present invention is achieved through the following technical solutions.
The invention provides a kind of plunger hydraulic motor mechanical-hydraulic leading switch variable-torque oil-distribution component, comprise plunger case, plunger, plunger cavity, also comprise oil distributing valve group and variable driving ring;
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 variable driving ring is used to drive the work of oil distributing valve group, and its axial centre position 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 variable driving ring can and only can be along moving freely perpendicular to suction oil content boundary line direction;
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.
The present invention also provides a kind of method for changing torque that is applicable to the plunger hydraulic motor mechanical-hydraulic leading switch variable-torque oil-distribution component, may further comprise the steps:
(1) according to the requirement to the output torque size, the Moderator Variable driving ring is 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 invention has the beneficial effects as follows:
(1) become moment of torsion control: the present invention is 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, realized 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 present invention 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 present invention 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 a structural representation of the present invention.
Fig. 2 is the structural representation of pilot valve and variable driving ring place section among the present invention.
Fig. 3 is the scheme of installation of each main valve and variable driving ring among the present invention.
Fig. 4 is the scheme of installation that each guide's spool is installed in guide's valve body among the present invention.
Fig. 5 is among the present invention above guide's valve body, the corresponding relation figure of each valve port step and hydraulic oil port.
Fig. 6 be among the present invention each above guide's spool, the corresponding relation figure of each valve port step and hydraulic oil port.
Fig. 7 is the motion flow control graph of each plunger position of the present invention and its related valves.
Fig. 8 is each main valve of the present invention and the pilot valve position view at state A.
Fig. 9 be each main valve of the present invention and pilot valve at state B, the position view of C.
Figure 10 is each main valve of the present invention and the pilot valve position view at state D.
Figure 11 be each main valve of the present invention 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, the return opening of 19 band back pressures, 20 high pressure hydraulic fluid ports, 21 guide's high pressure hydraulic fluid ports, 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, 44 pilot valve annular end faces.
Embodiment
In conjunction with the accompanying drawings, the present invention is described in detail below by specific embodiment.
Specific embodiments of the invention have specifically been discussed a kind of oil hydraulic motor that has adopted machine solution guide switch changing torque oil-distribution component provided by the invention when saying something, be described in detail as follows:
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 among the present invention.Oil-distribution component of the present invention 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 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 and controlling method, the working procedure of this plunger variable oil hydraulic motor is shown in accompanying drawing 7～11.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 embodiments of the invention.Obviously, the invention is not restricted to above embodiment, a lot of distortion can also be arranged.All distortion that those of ordinary skill in the art can directly derive from content disclosed by the invention or associate all should be thought protection scope of the present invention.
Claims (7)
1, a kind of plunger hydraulic motor mechanical-hydraulic leading switch variable-torque oil-distribution component comprises plunger case, plunger, and plunger cavity is characterized in that, also comprises oil distributing valve group and variable driving ring;
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 variable driving ring is used to drive the work of oil distributing valve group, and its axial centre position 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 variable driving ring can and only can be along moving freely perpendicular to suction oil content boundary line direction;
2, plunger hydraulic motor mechanical-hydraulic leading switch variable-torque oil-distribution component 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.
3, plunger hydraulic motor mechanical-hydraulic leading switch variable-torque oil-distribution component 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.
4, plunger hydraulic motor mechanical-hydraulic leading switch variable-torque oil-distribution component 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.
5, plunger hydraulic motor mechanical-hydraulic leading switch variable-torque oil-distribution component 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.
6, plunger hydraulic motor mechanical-hydraulic leading switch variable-torque oil-distribution component 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.
7, a kind of method for changing torque that is applied to the described plunger hydraulic motor mechanical-hydraulic leading switch variable-torque oil-distribution component of claim 1 is characterized in that, may further comprise the steps:
(1) according to the requirement to the output torque size, the Moderator Variable driving ring is 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.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2008100635451A CN101302992A (en) | 2008-06-20 | 2008-06-20 | Plunger piston hydraulic slave motor machine solution guide switch changing torque oil distributing component as well as method for changing torque |
| CN2008101777229A CN101403366B (en) | 2008-06-20 | 2008-11-12 | Plunger hydraulic motor mechanical-hydraulic leading switch variable-torque oil-distribution component and torque-changing method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2008100635451A CN101302992A (en) | 2008-06-20 | 2008-06-20 | Plunger piston hydraulic slave motor machine solution guide switch changing torque oil distributing component as well as method for changing torque |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101302992A true CN101302992A (en) | 2008-11-12 |
Family
ID=40113038
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2008100635451A Pending CN101302992A (en) | 2008-06-20 | 2008-06-20 | Plunger piston hydraulic slave motor machine solution guide switch changing torque oil distributing component as well as method for changing torque |
| CN2008101777229A Expired - Fee Related CN101403366B (en) | 2008-06-20 | 2008-11-12 | Plunger hydraulic motor mechanical-hydraulic leading switch variable-torque oil-distribution component and torque-changing method |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008101777229A Expired - Fee Related CN101403366B (en) | 2008-06-20 | 2008-11-12 | Plunger hydraulic motor mechanical-hydraulic leading switch variable-torque oil-distribution component and torque-changing method |
Country Status (1)
| Country | Link |
|---|---|
| CN (2) | CN101302992A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112253374A (en) * | 2020-10-09 | 2021-01-22 | 宁波真格液压科技有限公司 | Variable hydraulic motor |
| CN114483674A (en) * | 2022-02-28 | 2022-05-13 | 浙江工业大学 | Radial digital pump capable of adjusting pressure impact and control method thereof |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3557054A1 (en) * | 2018-04-19 | 2019-10-23 | Dana Motion Systems Italia S.R.L. | Piston hydraulic device |
-
2008
- 2008-06-20 CN CNA2008100635451A patent/CN101302992A/en active Pending
- 2008-11-12 CN CN2008101777229A patent/CN101403366B/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112253374A (en) * | 2020-10-09 | 2021-01-22 | 宁波真格液压科技有限公司 | Variable hydraulic motor |
| CN112253374B (en) * | 2020-10-09 | 2023-12-12 | 宁波真格液压科技有限公司 | Variable hydraulic motor |
| CN114483674A (en) * | 2022-02-28 | 2022-05-13 | 浙江工业大学 | Radial digital pump capable of adjusting pressure impact and control method thereof |
| CN114483674B (en) * | 2022-02-28 | 2024-03-19 | 浙江工业大学 | Radial digital pump capable of adjusting pressure impact and control method thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101403366B (en) | 2011-06-15 |
| CN101403366A (en) | 2009-04-08 |
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