CN201306322Y - Hydraulic transformer for machine liquid pilot virtual displacement variables - Google Patents
Hydraulic transformer for machine liquid pilot virtual displacement variables Download PDFInfo
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- CN201306322Y CN201306322Y CNU2008201665572U CN200820166557U CN201306322Y CN 201306322 Y CN201306322 Y CN 201306322Y CN U2008201665572 U CNU2008201665572 U CN U2008201665572U CN 200820166557 U CN200820166557 U CN 200820166557U CN 201306322 Y CN201306322 Y CN 201306322Y
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Abstract
The utility model relates to a hydraulic transformer, which aims to provide a hydraulic transformer for machine liquid pilot virtual displacement variables. The hydraulic transformer comprises a torque filtering mechanism, a quantitative inclined plate, a plunger cylinder tube, a plunger and a plunger cavity, and further comprises an oil distribution valve group, an oil distribution disc and a machine liquid pilot virtual displacement variable driving mechanism. Compared with the prior art, the hydraulic transformer has the beneficial effects that the structure is simplified, the control range of high-efficiency variables is multiply improved, the energy is saved, and the continuous variables and the response speed of voltage lifting and voltage reducing working conditions are improved to an order of magnitude, so as to avoid the zero crossing problem.
Description
Technical field
The utility model relates to hydraulic transformer, and in particular, the utility model relates to a kind of mechanical-hydraulic guiding virtual displacement variable hydraulic transformer.
Background technique
The conventional construction of hydraulic transformer is made of plunger variable hydraulic pump of a plunger variable oil hydraulic motor band.At first the plunger variable oil hydraulic motor relies on pressure oil to act on the plunger of motor, thereby makes motor output shaft obtain certain torque, and then by plunger variable hydraulic pump torque to the plunger of pump, be converted to pressure oil again again.The change of variable ratio can realize by the variable of oil hydraulic motor and oil hydraulic pump.
No matter be the plunger variable oil hydraulic motor, or plunger variable hydraulic pump, all need to make plunger alternately to communicate with pressure hydraulic fluid port and return opening, thereby must adopt flow distribution apparatus, plunger variable oil hydraulic motor and plunger variable hydraulic pump adopt 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 and oil hydraulic pump opposite side at formal plunger variable oil hydraulic motor and the plunger variable hydraulic pump of selling on the market.And there are three weakness in the hydraulic transformer variable mode that the swash plate angle of inclination is regulated in this traditional passing through:
1. the efficient of oil hydraulic motor and oil hydraulic pump itself is just not high, and the higher relatively range of variables of efficient is very narrow, and the overall efficiency that series connection becomes after the hydraulic transformer is lower, and range of variables is narrower.
2. the hydraulic coupling that each plunger produces in oil hydraulic motor and the oil hydraulic pump, 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 and oil hydraulic pump.
3. for traditional hydraulic transformer with public return opening, the transition point that switches to the Power Recovery operating mode from the forward transformation is that pump and motor displacement are zero point.Therefore, the pump operating mode is slowed down to reclaim in order to switch to, the energy of braking process, the all necessary Zero Crossing Point of oil hydraulic motor and hydraulic pressure pump delivery controlling mechanism, simultaneously the filler opening of follow-up final controlling element and oil outlet are also exchanged, 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 mechanical-hydraulic guiding virtual displacement variable hydraulic transformer 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 mechanical-hydraulic guiding virtual displacement variable hydraulic transformer, comprises moment of torsion filtering mechanism, quantitative swash plate, plunger case, plunger and plunger cavity, also comprises oil distributing valve group, oil distribution casing and machine solution guide virtual displacement variable driving mechanism;
Described oil distributing valve group by with speed-sensitive switch high-pressure oil feed valve, speed-sensitive switch oil extraction-Fill valve, the pilot valve of number of plungers equal number, and public axially support force compensating plunger, compensation piston spring, compensation plunger cavity and 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; Be in the circumferential hydraulic fluid port of each speed-sensitive switch high-pressure oil feed valve in oil suction district, all pass pilot valve, be communicated with the high pressure oil-feed runner of oil distribution casing at high-pressure oil feed control step and near the cavity volume between the central side end face; Be in the circumferential hydraulic fluid port of each speed-sensitive switch high-pressure oil feed valve in oil extraction district, all pass pilot valve, be communicated with the fuel-displaced runner of the high pressure of oil distribution casing at high-pressure oil feed control step and near the cavity volume between the central side end face; The circumferential hydraulic fluid port of each speed-sensitive switch oil extraction-Fill valve all passes pilot valve at oil extraction-repairing control step and near the cavity volume between the case side end face, is communicated with the oil return runner of oil distribution casing; 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 each pilot valve was near case side end face and oil extraction-repairing control step, between oil extraction-repairing control step and the high-pressure oil feed control step, high-pressure oil feed was controlled step and near between the central side end face cavity volume is arranged respectively; Each pilot valve is controlled step and is communicated with the oil return runner of oil distribution casing near the cavity volume between the case side end face in oil extraction-repairing, and the cavity volume between high-pressure oil feed control step and oil extraction-repairing control step is communicated with corresponding plunger cavity; Each pilot valve that is in the oil suction district is controlled step and all is communicated with the high pressure oil-feed runner of oil distribution casing near the cavity volume between the central side end face in high-pressure oil feed, and the pilot valve that is in the oil extraction district all is communicated with the fuel-displaced runner of the high pressure of oil distribution casing at high-pressure oil feed control step and near the cavity volume between the central side end face; Two end faces of each pilot valve (near case side end face and close central side end face) all are communicated with the leakage hydraulic fluid port; All pilot valves all are positioned on the same cross section; The end face center of quantitative swash plate is led at the center that compensation plunger cavity one end passes axially support force compensating plunger, and the end face center of oil distribution casing is led at the center that the other end passes the oil distributing valve body.
On housing, opposite side and described oil distributing valve body are positioned at and are provided with the support and relatively rotating of floating between the end face of plunger opposite side with dowel fixes for described oil distribution casing; There are high pressure oil-feed runner, the fuel-displaced runner of high pressure, oil return runner in inside and leak oily runner, all pilot valves that are in the oil suction district are communicated with cavity volume between the close central side end face at high-pressure oil feed control step on one end of its mesohigh oil-feed runner and the described oil distributing valve group, and the other end is communicated with high pressure filler opening on the housing; All pilot valves that are in the oil extraction district are communicated with cavity volume between the close central side end face at high-pressure oil feed control step on one end of the fuel-displaced runner of high pressure and the described oil distributing valve group, and the other end is communicated with high pressure oil outlet on the housing; All pilot valves are communicated with cavity volume between the close case side end face at oil extraction-repairing control step on one end of oil return runner and the described oil distributing valve group, and the other end is communicated with return opening on the housing; Leaking oily runner is communicated with the leakage hydraulic fluid port; The differentiation mode of high pressure oil-feed runner and the fuel-displaced runner of high pressure is, what be positioned at the oil suction district is high pressure oil-feed runner, and what be positioned at the oil extraction district is the fuel-displaced runner of high pressure, and when hydraulic transformer reversed, the fuel-displaced runner of high pressure oil-feed runner and high pressure exchanged.
Described machine solution guide virtual displacement variable driving mechanism is made up of housing, variable driving bearing, quantity governor; The axial end of described housing is fixedlyed connected with described oil distribution casing, and the return opening of its high pressure filler opening, high pressure oil outlet and band back pressure is communicated with high pressure oil-feed runner, the fuel-displaced runner of high pressure, the oil return runner of oil distribution casing respectively; The differentiation mode of high pressure filler opening and high pressure oil outlet is, what be positioned at the oil suction district is the high pressure filler opening, and what be positioned at the oil extraction district is the high pressure oil outlet, and when hydraulic transformer reversed, high pressure filler opening and high pressure oil outlet exchanged.
As a kind of improvement, the axial centre position of described variable driving bearing is consistent with cross section, described pilot valve place, and inwall contacts near case side with described all pilot valves and provides rotation to support; The inwall center of variable driving bearing 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 bearing 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 bearing 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 bearing, and opposite side is communicated with the Variable Control hydraulic fluid port; Spring seat one side contacts with the variable driving bearing, 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 bearing, and opposite side is communicated with the Variable Control hydraulic fluid port; Spring seat one side contacts with the variable driving bearing, 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 bearing, 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, described pilot valve is near the end face of central side, its diameter is more smaller than the diameter of pilot valve high-pressure oil feed control step, and this area difference provides a pressure radially to pilot valve, makes all pilot valves can both be pressed on the described variable driving bearing.
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 bearing 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 bearing 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 virtual displacement variable method that is used for mechanical-hydraulic guiding virtual displacement variable hydraulic transformer in the utility model may further comprise the steps:
(1) according to the requirement to delivery pressure and incoming pressure ratio, 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 filler opening; Be positioned at other plunger cavities in oil suction district, all the speed-sensitive switch oil extraction-Fill valve by communicating with return opening directly from the return opening oil suction, replenishes the cavity that plunger motion produces, but can not promote the plunger acting; Meanwhile, be positioned at the plunger cavity in oil extraction district, also only when speed-sensitive switch high-pressure oil feed opening of valves, can become the pressure energy to torque axis to the oil extraction of high pressure oil outlet; Be positioned at other plunger cavities in oil extraction district, all the speed-sensitive switch oil extraction-Fill valve by communicating with return opening directly is discharged to return opening, does not hinder plunger motion, but can not consume moment of torsion; Guarantee the ratio of the average delivery pressure of high pressure oil outlet, be directly proportional divided by the ratio of speed-sensitive switch high-pressure oil feed valve in the displacement of oil extraction district opening time section inner plunger with of the displacement of speed-sensitive switch high-pressure oil feed valve in oil suction district opening time section inner plunger divided by high pressure filler opening pressure;
(3) account for the dutycycle of whole plunger oil suction stroke in the displacement of oil suction district opening time section inner plunger by real-time regulated speed-sensitive switch high-pressure oil feed valve, output high pressure filler opening pressure multiply by dutycycle again divided by the middle pressure of 1-dutycycle, realizes the virtual displacement Variable Control; Pass between dutycycle and the delivery pressure is:
Make plunger displacement dutycycle D=X
Open/ X
Max, high pressure filler opening pressure P
1, delivery pressure P
2,
P
1＝DP
2(1-D)
The pilot valve displacement amplitude is that the displacement y of variable driving bearing 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, η
MachineBe the mechanical efficiency of hydraulic transformer, η
ValveBe the efficient of oil distributing valve group control plunger cavity, y0 is the inwall center of variable driving bearing and the fixed bias displacement between the plunger case central axis, and y is the displacement of variable driving bearing for the pilot valve displacement amplitude;
(4) direction of y is consistent with the sense of rotation of hydraulic transformer, if hydraulic transformer counter-rotating, variable driving bearing reverse direction actuation then, the fluid flow direction of high pressure filler opening and high pressure oil outlet switches mutually.
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 A: the effective drive condition of motor: the pilot valve displacement is greater than the fixed bias between variable driving bearing 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 filler opening, thereby the pressure of plunger cavity approaches the pressure of high pressure filler opening, 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: motor virtual displacement drive condition: the pilot valve displacement is between the fixed bias between positive and negative variable driving bearing 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: pump virtual displacement output state: the pilot valve displacement is less than negative variable driving bearing 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 high pressure oil outlet 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 high pressure oil outlet;
(4) state E, F: the effective output state of pump: the pilot valve displacement is between the fixed bias between positive and negative variable driving bearing 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 the high pressure oil outlet, the high pressure oil outlet 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 the high pressure oil outlet 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) designs simplification: the utility model unites two into one oil hydraulic motor and oil hydraulic pump, has avoided the loss of unnecessary energy consumption and range of variables;
(2) high efficiency Variable Control scope significantly improves: 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, square middle pressure that the is directly proportional ratio of output and the displacement of variable bar, realized switch virtual displacement Variable Control, switch virtual displacement Variable Control had not both changed the discharge capacity of hydraulic motor/pump, also do not change charge oil pressure, but it has finally directly changed the output/incoming pressure ratio of hydraulic transformer;
(3) energy-conservation: when requiring to export lower pressure, the part be positioned at the oil suction district plunger cavity no longer from the oil suction of high pressure filler opening, 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; Otherwise, when requiring to export than higher pressure, the plunger cavity that part is positioned at the oil extraction district is no longer to the oil extraction of high pressure oil outlet, but by oil extraction-Fill valve to the return opening oil extraction, do not need pressure oil is wasted on the extra throttling control valve mouth yet, thereby saved a large amount of energy consumptions;
(4) boost continuous variable with the step-down operating mode: when the plunger displacement dutycycle less than 0.5 the time, hydraulic transformer has just changed the operating mode of boosting over to from the step-down operating mode reposefully, i.e. delivery pressure height and incoming pressure;
(5) speed of response improves an order of magnitude: the hydraulic coupling that each plunger produces in conventional hydraulic motors and the oil hydraulic pump, when driving the oil hydraulic motor rotation or being with the oil hydraulic pump 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 and oil hydraulic pump 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 oil hydraulic pump stroking mechanism; 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 bearing, unbalanced force has dwindled an order of magnitude, thereby the variable speed of response of hydraulic transformer has been improved an order of magnitude;
(6) avoided the zero passage problem: tradition has the hydraulic transformer of public return opening, the transition point that the forward transformation switches to the Power Recovery operating mode is that pump and motor displacement are zero point, therefore the Power Recovery operating mode is slowed down to reclaim, the energy of braking process in order to switch to, the all necessary Zero Crossing Point of oil hydraulic motor and hydraulic pressure pump delivery controlling mechanism, simultaneously the filler opening of follow-up final controlling element and oil outlet are also exchanged, 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 utility model then only need be high pressure filler opening and the exchange of high pressure oil outlet, simultaneously the filler opening of follow-up final controlling element and oil outlet are also exchanged, just can allow hydraulic transformer enter the Power Recovery operating mode reposefully, do not need through discharge capacity zero point, thereby do not have near zero point unstable problem yet.
Description of drawings
Fig. 1 is the utility model structural representation.
Fig. 2 is the structural representation of oil distributing valve group and machine solution guide virtual displacement variable driving mechanism in the utility model.
Fig. 3 is the structural representation of pilot valve and virtual displacement variable driving mechanism place section in the utility model (adopting the mechanical variables regulator).
Fig. 4 is the structural representation of pilot valve and virtual displacement variable driving mechanism place section (adopting single hydraulic fluid port hydraulic pressure quantity governor) in the utility model.
Fig. 5 is the structural representation of pilot valve and virtual displacement variable driving mechanism place section in the utility model (adopting two hydraulic fluid port list control hydraulic pressure quantity governors).
Fig. 6 is the structural representation of pilot valve and virtual displacement variable driving mechanism place section in the utility model (adopting two control hydraulic pressure quantity governors).
Fig. 7 is the scheme of installation of each main valve and virtual displacement variable 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 above guide's valve body in oil suction district the corresponding relation figure of each valve port step and hydraulic oil port in the utility model.
Figure 11 be in the oil suction district 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 bearings, 18 housings, the return opening of 19 band back pressures, 20 high pressure filler openings, 21 high pressure oil outlets, 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 valves are near the end face of central side, 36 pilot valves are at oil extraction-repairing control step and near the cavity volume between the case side end face, 37 pilot valves are at high-pressure oil feed control step and near the cavity volume between the central side 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 filtering mechanisms, 41 quantitative swash plates, 42 oil distributing valve groups, 43 machine liquid become torque driving mechanism, 44 flywheels, 45 oil distribution casings, the oil return runner of 46 oil distribution casings, the high pressure oil-feed runner of 47 oil distribution casings, the fuel-displaced runner of the high pressure of 48 oil distribution casings, the leakage oil runner of 49 oil distribution casings, 50 leak hydraulic fluid port, 51 axially support force compensating plungers, 52 compensation piston springs, 53 compensation plunger cavities, 54 screws.
Embodiment
In conjunction with the accompanying drawings, below by specific embodiment the utility model is elaborated.
A kind of mechanical-hydraulic guiding virtual displacement variable hydraulic transformer in this specific embodiment is by a quantitative plunger piston hydraulic motor repacking of common rotating cylinder cartridge type.
The flywheel that rotary inertia is bigger is installed, as moment of torsion filtering mechanism on the plunger-type quantitative hydraulic motor output shaft; Remove the bonnet and the oil distribution casing of this oil hydraulic motor simultaneously, 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 hydraulic transformer of machine solution guide virtual displacement variable function.
According to foregoing structure and controlling method, the working procedure of this hydraulic transformer 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: the effective drive condition of motor: the pilot valve displacement is greater than the fixed bias between variable driving bearing 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 filler opening, thereby the pressure of plunger cavity approaches the pressure of high pressure filler opening, 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: motor virtual displacement drive condition: the pilot valve displacement is between the fixed bias between positive and negative variable driving bearing 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: pump virtual displacement output state: the pilot valve displacement is less than negative variable driving bearing 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 high pressure oil outlet 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 high pressure oil outlet;
(4) state E, F: the effective output state of pump: the pilot valve displacement is between the fixed bias between positive and negative variable driving bearing 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 the high pressure oil outlet, the high pressure oil outlet 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 the high pressure oil outlet 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 (8)
1, a kind of mechanical-hydraulic guiding virtual displacement variable hydraulic transformer comprises moment of torsion filtering mechanism, quantitative swash plate, plunger case, plunger and plunger cavity, it is characterized in that, also comprises oil distributing valve group, oil distribution casing and machine solution guide virtual displacement variable 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 axially support force compensating plunger, compensation piston spring, compensation plunger cavity and 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; Be in the circumferential hydraulic fluid port of each speed-sensitive switch high-pressure oil feed valve in oil suction district, all pass pilot valve, be communicated with the high pressure oil-feed runner of oil distribution casing at high-pressure oil feed control step and near the cavity volume between the central side end face; Be in the circumferential hydraulic fluid port of each speed-sensitive switch high-pressure oil feed valve in oil extraction district, all pass pilot valve, be communicated with the fuel-displaced runner of the high pressure of oil distribution casing at high-pressure oil feed control step and near the cavity volume between the central side end face; The circumferential hydraulic fluid port of each speed-sensitive switch oil extraction-Fill valve all passes pilot valve at oil extraction-repairing control step and near the cavity volume between the case side end face, is communicated with the oil return runner of oil distribution casing; 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 each pilot valve was near case side end face and oil extraction-repairing control step, between oil extraction-repairing control step and the high-pressure oil feed control step, high-pressure oil feed was controlled step and near between the central side end face cavity volume is arranged respectively; Each pilot valve is controlled step and is communicated with the oil return runner of oil distribution casing near the cavity volume between the case side end face in oil extraction-repairing, and the cavity volume between high-pressure oil feed control step and oil extraction-repairing control step is communicated with corresponding plunger cavity; Each pilot valve that is in the oil suction district is controlled step and all is communicated with the high pressure oil-feed runner of oil distribution casing near the cavity volume between the central side end face in high-pressure oil feed, and the pilot valve that is in the oil extraction district all is communicated with the fuel-displaced runner of the high pressure of oil distribution casing at high-pressure oil feed control step and near the cavity volume between the central side end face; Two end faces of each pilot valve (near case side end face and close central side end face) all are communicated with the leakage hydraulic fluid port; All pilot valves all are positioned on the same cross section; The end face center of quantitative swash plate is led at the center that compensation plunger cavity one end passes axially support force compensating plunger, and the end face center of oil distribution casing is led at the center that the other end passes the oil distributing valve body;
On housing, opposite side and described oil distributing valve body are positioned at and are provided with the support and relatively rotating of floating between the end face of plunger opposite side with dowel fixes for described oil distribution casing; There are high pressure oil-feed runner, the fuel-displaced runner of high pressure, oil return runner in inside and leak oily runner, all pilot valves that are in the oil suction district are communicated with cavity volume between the close central side end face at high-pressure oil feed control step on one end of its mesohigh oil-feed runner and the described oil distributing valve group, and the other end is communicated with high pressure filler opening on the housing; All pilot valves that are in the oil extraction district are communicated with cavity volume between the close central side end face at high-pressure oil feed control step on one end of the fuel-displaced runner of high pressure and the described oil distributing valve group, and the other end is communicated with high pressure oil outlet on the housing; All pilot valves are communicated with cavity volume between the close case side end face at oil extraction-repairing control step on one end of oil return runner and the described oil distributing valve group, and the other end is communicated with return opening on the housing; Leaking oily runner is communicated with the leakage hydraulic fluid port; The differentiation mode of high pressure oil-feed runner and the fuel-displaced runner of high pressure is, what be positioned at the oil suction district is high pressure oil-feed runner, and what be positioned at the oil extraction district is the fuel-displaced runner of high pressure, and when hydraulic transformer reversed, the fuel-displaced runner of high pressure oil-feed runner and high pressure exchanged;
Described machine solution guide virtual displacement variable driving mechanism is made up of housing, variable driving bearing, quantity governor; The axial end of described housing is fixedlyed connected with described oil distribution casing, and the return opening of its high pressure filler opening, high pressure oil outlet and band back pressure is communicated with high pressure oil-feed runner, the fuel-displaced runner of high pressure, the oil return runner of oil distribution casing respectively; The differentiation mode of high pressure filler opening and high pressure oil outlet is, what be positioned at the oil suction district is the high pressure filler opening, and what be positioned at the oil extraction district is the high pressure oil outlet, and when hydraulic transformer reversed, high pressure filler opening and high pressure oil outlet exchanged.
2, mechanical-hydraulic guiding virtual displacement variable hydraulic transformer according to claim 1, it is characterized in that, the axial centre position of described variable driving bearing is consistent with cross section, described pilot valve place, and inwall contacts near case side with described all pilot valves and provides rotation to support; The inwall center of variable driving bearing 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 bearing 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.
3, mechanical-hydraulic guiding virtual displacement variable hydraulic transformer 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 bearing 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 bearing, and opposite side is communicated with the Variable Control hydraulic fluid port; Spring seat one side contacts with the variable driving bearing, 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 bearing, and opposite side is communicated with the Variable Control hydraulic fluid port; Spring seat one side contacts with the variable driving bearing, 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 bearing, and opposite side all contacts with corresponding Returnning spring; 2 spring chambers all are communicated with the Variable Control hydraulic fluid port.
4, mechanical-hydraulic guiding virtual displacement variable hydraulic transformer according to claim 1, it is characterized in that, described pilot valve is near the end face of central side, its diameter is more smaller than the diameter of pilot valve high-pressure oil feed control step, this area difference provides a pressure radially to pilot valve, makes all pilot valves can both be pressed on the described variable driving bearing.
5, mechanical-hydraulic guiding virtual displacement variable hydraulic transformer 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.
6, mechanical-hydraulic guiding virtual displacement variable hydraulic transformer 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.
7, mechanical-hydraulic guiding virtual displacement variable hydraulic transformer 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.
8, mechanical-hydraulic guiding virtual displacement variable hydraulic transformer 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 bearing 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 bearing 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 |
|---|---|---|---|
| CNU2008201665572U CN201306322Y (en) | 2008-10-30 | 2008-10-30 | Hydraulic transformer for machine liquid pilot virtual displacement variables |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008201665572U CN201306322Y (en) | 2008-10-30 | 2008-10-30 | Hydraulic transformer for machine liquid pilot virtual displacement variables |
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| Publication Number | Publication Date |
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| CN201306322Y true CN201306322Y (en) | 2009-09-09 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNU2008201665572U Expired - Lifetime CN201306322Y (en) | 2008-10-30 | 2008-10-30 | Hydraulic transformer for machine liquid pilot virtual displacement variables |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107044456A (en) * | 2017-04-07 | 2017-08-15 | 江苏师范大学 | A kind of flow waist-shaped hole it is variable enter it is fuel-displaced wait flow four-way hydraulic transformer |
-
2008
- 2008-10-30 CN CNU2008201665572U patent/CN201306322Y/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107044456A (en) * | 2017-04-07 | 2017-08-15 | 江苏师范大学 | A kind of flow waist-shaped hole it is variable enter it is fuel-displaced wait flow four-way hydraulic transformer |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20090909 Effective date of abandoning: 20081030 |