CN101713399A - Hydrostatic separable speed changer - Google Patents
Hydrostatic separable speed changer Download PDFInfo
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- CN101713399A CN101713399A CN200810170115A CN200810170115A CN101713399A CN 101713399 A CN101713399 A CN 101713399A CN 200810170115 A CN200810170115 A CN 200810170115A CN 200810170115 A CN200810170115 A CN 200810170115A CN 101713399 A CN101713399 A CN 101713399A
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Abstract
The invention relates to a separable gear pump or a motor which comprises gear pairs, a casing body, a movable radial sealing block or an axial sliding side plate which are mutually engaged. The gear pump or the motor forms bonded or separated radial sealing or axial sealing. A plurality of the pumps and the motors form a hydrostatic separable speed changer, some of sub-pumps or motors are separated or jointed to change total flow rate so as to achieve the purpose of transiting stepless speed change to multiple gears step speed change softly.
Description
This be about utilize can deciliter gear pump or motor obtain the invention of the step change bending moment of quiet liquid stepless transition, belong to hydraulic transmission technology field.
Existing Hydromechanical transmission transmission efficiency is lower, and its mechanical transmission makes rate of fault higher if will obtain more gear and use existing electricity-liquid on-load automaitc shfit will use complicated structure, and manufacture cost is also higher.Existing quiet liquid stepless speed variator such as the quiet liquid stepless speed variator system of plunger pump/piston motor are then because of using expensive variable piston pump/motor cost high.The patented technology document that has earlier the inventor has been authorized U.S.'s patent of invention 4872536,4932504,5161961 described pump efficiencys are answered clutch, on stepless variable gear pump and the technical foundation to the compound gear pump of bearing liquid pressure complete equilibrium, formerly have on the technical paper inventor's the technical foundation of the Chinese invention patent of mandate 90100918 " balanced type gear pump and motor " (1991 open), and seen the same principle that occurred later in 1992 about papers such as " balanced compound gear pumps ", formerly have on the technical foundation of described braking stored-energy drive speed transmission of technical paper Chinese invention patent ZL02101926.6 and Chinese patent literature 2005100069474 " non-boost automatic clutch employing inclined plane principle ", the inventor continues research, is proposed the present invention.
The objective of the invention is to realize high transmission efficiency, wide slewing range and the multi-speed exchanged gear, that have the such flexible combined function of fluid coupling, the low quiet liquid transmission gear shift device cheap for manufacturing cost of rate of fault simple in structure, can the on-load speed change and can electric control automatic gear shifting.
The objective of the invention is to realize with such basic skills:
1 certain Sealing that makes oil hydraulic pump or motor is answered position and zero pump efficiency to answer between the position at full pump efficiency and can be moved trippingly because of suffered hydraulic coupling is in a basic balance, corresponding oil outlet or the oil inlet hole that opens or closes pump or motor when mobile, make corresponding jointing state or the separated state of being in of pump or motor, its flow can change on continuous stepless ground between two states, makes that the joint of pump or motor is a soft transitions with separating;
2 be connected in parallel rightly several such pump or motors, engage, separate wherein some pump or motor rightly, make the discharge capacity of the pump combine or motor for the algebraic sum of each sub-pump or motor displacement and along with the joint separation of sub-pump or motor changes, make such pump drive such motor, reach the object of the invention of speed change by the discharge capacity that changes pump or motor.
The description of the drawings:
Fig. 1 be about the radial seal piece can be brisk mobile can deciliter gear pump or the principle sectional drawing of motor;
Fig. 2 is the A-A partial sectional view of Fig. 1;
Fig. 3 is the three-dimensional view about the equilibrium block among Fig. 1 and Fig. 2 31;
Fig. 4 is about can deciliter pump and the schematic representation of a kind of quiet liquid speed changer typical structure that is connected into of motor;
Fig. 5 is the partial sectional view about elastic material paster on the axial lateral plate that floats;
Fig. 6 is the schematic representation about the coplanar multiple gearpump;
Fig. 7 is the schematic representation that is also used as the between centers driving gear about coplanar gear pump and gear motor;
Fig. 8 is about schematic representation that can deciliter internal gear pump/motor;
Fig. 9 is the partial view about radial seal piece sealing flute profile oilhole in the presentation graphs 8;
Figure 10 is the two-way schematic representation that can deciliter internal gear pump/motor structure about having that reverse gear is provided with;
Figure 11 is can deciliter gear pump or the schematic representation of motor about what constitute with the side plate that endwisely slips.
Specify below in conjunction with drawings and Examples.
Fig. 1, Fig. 2 and Fig. 3 have shown a kind of theory structure of pump efficiency inductive switch gear pump, pitch wheel 1 and 2 respectively through bearing 12 and 22 be bearing in the axle 11 and 21 on, gear pump shaft to bi-side thickly sealed by side plate 6 liquid; Be full of hydraulic oil within the housing 4, radial seal piece 3 is movable, one section tooth top circular arc that the arc surface liquid that it equals the gear teeth tips circle radius to gear movement to its radius thickly touches each gear symmetrically seals a plurality of tooth tops, promptly constitute the radial seal of gear pump, it is maximum that pump efficiency should reach, and the radial seal piece is in full pump efficiency and answers the position; Can fit on radial seal piece 3 arc surfaces and install the engineering nylon arc surface paster 32 that one deck arc surface radius equals the gear teeth tips circle radius, increase the close property of its liquid, reduce tooth top contact pressure and frictional loss the radial seal of gear, and the radial clearance of compensate for wear generation automatically.When gear pair rotates according to Fig. 1 direction of arrow, hydraulic oil flow into from the oilhole 41 on the housing 4 that L enters H between the zone of high pressure through sealed between cog again between low pressure area, enter the pipeline 34 of hollow in the radial seal piece 3, from equilibrium block 31 inside of hollow pipeline 34 by being solidly installed with the radial seal piece, enter the interval K of back pressure, flow out gear pump through the flute profile oilhole of on side plate 6, offering 53.From stereogram Fig. 3 as can be seen, equilibrium block 31 is cuboids of a T shape, its two sides 312 and the same plane, office, bi-side of radial seal piece 3, therefore can be done axial end face seal in the lump by the side plate 6 of gear pump both sides, 6 pairs of housings 4 of side plate, gear 1 and 2, radial seal piece 3 and equilibrium block 31 and back pressure housing 5 are done thickly axial end sealing of liquid, side plate 6 can all or part ofly be made axial float, after obtaining axial back pressure, gear pump is carried out the floating seal of axial end, this belongs to known technology, does not give unnecessary details here.The hydraulic coupling that radial seal piece 3 is subjected to towards the curved surface of gear comprises the hydraulic coupling and the between cog gradient pressure of H hydraulic oil effect between the zone of high pressure, it make a concerted effort to point to and to make the radial seal piece separate (among Fig. 1 left) with gear, be called separating pressure, radial seal piece 3 both wings backs 30 are acting on synthetic the making a concerted effort of hydraulic coupling of the hydraulic coupling and the sensing gear direction that the interval K hydraulic oil of back pressure acts on equilibrium block 31 of L hydraulic oil between low pressure area, this sensing of making a concerted effort makes the radial seal piece contact (among Fig. 1 to the right) with tooth top, be called activating pressure, the area that equilibrium block 3 is accepted the effect of the interval K hydraulic oil of back pressure is that the size of equilibrium block upper-end surface area S31 among the left side area of equilibrium block among Fig. 1 and Fig. 3 should design to such an extent that make activating pressure be slightly larger than separating pressure, make radial seal piece 3 or engineering nylon arc surface paster 32 be able to automatically the tooth top that pressed toward gear is gently paid, under the end face of the lower protruding edge 313 of equilibrium block both sides convex shoulder 311 and position-limiting action that housing 4 contacts, constitute enough radial seals and energy automatic compensation gap and wearing and tearing, unlikelyly again cause excessive contact pressure and excessive contact wear, the radial seal piece is in full pump efficiency and answers the position.Equilibrium block 31 bear the interval oil pressure of back pressure area S31 around promptly two side planes 312 and two convex shoulder that stretches out 311 liquid thickly are set within the equilibrium block cover 51 of engineering nylon material and can move under equilibrium block overlaps 51 constraint; Equilibrium block 31 can 361 thickly be solidly installed with radial seal piece back of the body end face liquid through the fastening screw trip bolt hole through the fastened screw 36 of resilient pad 33 (centre also has through hole 34) of engineering nylon material, sealing between they and the housing 4 is finished by the intermediate seal ring 42 of engineering nylon material, the intermediate seal ring also uses restraint to the mobile of sealing block radially, the intermediate seal ring 42 of the equilibrium block of engineering nylon material cover 51 and engineering nylon material constitutes the elastic floating support of sealing block 3 and equilibrium block 31 radially, add the elasticity of engineering nylon arc surface paster 32, make the radial seal of 3 pairs of gear pairs of radial seal piece obtain compensation balance automatically, even the radial seal of gear 1 better and the radial seal of gear 2 when relatively poor, the bigger between cog gradient pressure of gear 1 will apply a bias voltage to sealing block radially, this bias voltage forms a tooth top that makes the equilibrium block 31 of elastic floating support state and the adjustment couple that radial seal piece 3 rotates (direction in Fig. 1 is the inhour rotation) make radial seal piece 3 be adjacent to gear 2 more and increases sealing to gear 2 with combining between the pressure in axial section, till the radial seal complete equilibrium of 3 pairs of two gears of radial seal piece, if the radial seal to gear 1 is relatively poor, then above-mentioned adjustment process is opposite.Radial seal piece 3 is collectively referred to as balance radial seal piece with equilibrium block 31, in some occasion, to the elastic floating of equilibrium block and radial seal piece when less demanding, resilient pad 33 can save, the balance radial seal block element that equilibrium block 31 and radial seal piece 3 can be made of one, equilibrium block cover 51 and intermediate seal ring 42 also can be simplified.Position-limiting action between flange 313 and the housing 4 can be with the method adjustment of pad, and obtaining correct radial seal piece, to press to the position, stroke end of tooth top be that full pump efficiency is answered the position; The fastening force of fastening screw trip bolt pressure elasticity pad 33 can be made auxiliary the adjustment to the final position of the balance of the tooth top radial seal of two gears to sealing block radially, simultaneously, the arc surface engineering nylon paster 32 on the radial seal piece is also obtained the enough of two gear teeth tips and don't was produced radial seal galling, balance sealing block radially and plays good effect.Controlling rod 35 liquid thickly pass back pressure housing 5, be installed on the equilibrium block 31 through equalizer bar 351 (representing with the double dot dash line imaginary line among Fig. 2), the axis of bar should be tried one's best near the center of the suffered hydraulic coupling of equilibrium block, can mechanically push away through controlling rod 35, evening up weighing apparatus radial seal piece is affixed to the gear pair tooth top or leaves the gear pair tooth top, the terminal point that balance radial seal piece is pushed the stroke of gear to is that full pump efficiency is answered the position, it is maximum that the delivery pressure of pump and flow reach, from drawing toward the direction of separating (Fig. 1 left) here, then radial seal piece and gear teeth tips gradually away from, tooth top leaks increasing, the rapid reduction of the delivery pressure of pump and flow, simultaneously, the side plane 312 of equilibrium block moves gradually and has sealed flute profile oilhole 53, position among Fig. 1 is that equilibrium block has sealed the only about half of position of flute profile oilhole, balance radial seal piece continues to draw back to detaching direction, then the gap between radial seal piece and gear teeth tips is wide enough so that gear pump loses output flow and pressure fully, a pair of gear pair is equivalent in hydraulic oil and dallies, pump efficiency should be zero, balance radial seal piece reaches zero pump efficiency and answers the position, the also complete liquid of equilibrium block side plane 312 has thickly been sealed flute profile oilhole 53, and the port oil circuit of gear pump is cut off.
Such gear pump also can be used as gear motor work, when high pressure oil is imported from flute profile oilhole 53, balance radial seal piece is in full pump efficiency and answers the position, then hydraulic oil promotes the opposite direction rotation of gear shown in Fig. 1 arrow, on axle 11 and 21, can obtain machine power output, hydraulic oil from the K interval through hollow pipeline 34, the H interval, between cog, oilhole 41 on L interval and the housing 4 flows out, flute profile oilhole 53 becomes the input oilhole at this moment, when balance radial seal piece answers the position when zero pump efficiency answers the position to draw back from full pump efficiency, the power output of gear motor weakens gradually, when balance radial seal piece arrival zero pump efficiency is answered the position, the machine power of gear motor is output as zero, gear pair dallies in oil, and flute profile oilhole 53 is balanced piece side plane 312 complete closed.
When the high pressure oil of gear motor from 41 inputs of housing oilhole and flute profile oilhole 53 during still as output oil hole, turning to of gear pair will be identical with Fig. 1 direction of arrow with the switched in opposite of said gear motor, this moment, the L interval of Fig. 1 was converted between the zone of high pressure and the H interval is converted between low pressure area, and the situation when this operating mode is operated in reverse gear for speed changer needs.At this moment, the interval K of H interval and back pressure is between low pressure area, but the radial seal piece is subjected to the effect of high-pressure and hydraulic oil at the both wings back side 30, after a between cog gradient counteracted by pressure part, the suffered activating pressure of radial seal piece still may be obviously greater than separating pressure, cause to separate and handle difficulty, this requires the area design at the radial seal piece both wings back side 30 to get less on the one hand, make that the suffered hydraulic coupling of radial seal piece is in a basic balance, on the other hand, in order reliably to handle moving of balance radial seal piece, also can on housing 4, offer control oil duct 43 and introduce the control interval J that the control hydraulic oil injection of the controlled valve control of pressure is surrounded by equilibrium block convex shoulder 311 and equilibrium block cover 51 and housing 4, the J interval that has internal pipeline connection both sides on the equilibrium block equates the hydraulic coupling of two control interval J, hydraulic oil forms the control interval oil pressure in the control interval J, act on equilibrium block convex shoulder (the double side acting area is symmetry equivalent) and produce a control force that makes balance radial seal piece to the detaching direction motion, thereby balance radial seal piece is separated reliably with the gear pair tooth top, equally, the oil pressure that reduce to inject control interval J by control valve is during to the degree of needs, weaken detaching motion even turn to the direction of engagement motion with regard to may command balance radial seal piece, like this, use a very little control hydraulic fluid flow rate and the adjustment of pressure, just can handle the joint and the detaching motion of balance radial seal piece reliably.Controlling rod 35 and control oil duct 43---two kinds of control system of control interval J, can only establish a kind of, also can be as required the two all establish organically and use jointly.
Can have overflow hole 52 on the back pressure housing 5, after flute profile oilhole 52 is closed, hydraulic oil may occur in the interval K of back pressure and block overvoltage, high pressure oil can be derived through overflow hole 52 and be entered hydraulic energy storage device or oil sump etc. through control valve this moment, if oil pressure is crossed low or negative pressure occurred and need replenish hydraulic oil (common this situation appears at flute profile oilhole 53 and is closed in the interval K of back pressure, the radial seal piece answer the position near zero pump efficiency and gear pair turn to opposite operating mode shown in Figure 1 under), then the interval K of back pressure is able to suck or obtain replenishing of hydraulic oil through overflow hole 52 and control valve from oil sump or hydraulic energy storage device.Such setting also belongs to known hydraulics, does not give unnecessary details.
Like this, the balance radial seal piece of pump or motor can be answered position and zero pump efficiency to answer between the position at full pump efficiency trippingly and be moved, when being in full pump efficiency and answering the position, pump or motor are in jointing state, balance radial seal piece is in zero pump efficiency when answering the position, the flute profile oilhole is closed, and pump or motor are in separated state.Such pump or motor all can forward and backwards.Such pump or motor are called can deciliter oil hydraulic pump or can deciliter oil hydraulic motor.
Can deciliter oil hydraulic pump and can deciliter oil hydraulic motor can be connected into pump efficiency should deciliter speed changer.Its a kind of typical structure is described below in conjunction with Fig. 4.Can deciliter pump P1 and can a deciliter pump P2 be coaxial, be that the same side gear P2G of the gear P1G of P1 and P2 can be sleeved on axially slidably with key and is transfused to an AP on the input shaft AP and drives in the lump, P13 and P23 are respectively the all-in-one-piece balance radial seal piece of pump P1 and P2, KP1 and KP2 are respectively the back pressure interval of pump P1 and P2, the axial seal in the gear pair of 2 pumps and balance radial seal piece and back pressure interval is that the unsteady axial lateral plate P241 by the unsteady axial lateral plate P141 of the middle side plate of the common housing P40 of centre and pump P1 end and pump P2 end provides together, each unsteady axial lateral plate all is that liquid thickly can be sleeved within the common housing axially slidably, the gap of the appropriate position between P141 and the fixed lateral plate P14 is introduced the high-pressure and hydraulic oil axial lateral plate that will float and is pushed pump P1 gear pair and balance radial seal piece P13 to, and can axially movable gear pair and balance radial seal piece press to the middle side plate of common housing P40, thereby make the gear pair of pump P1 and the floating compensation that balance radial seal piece obtains axial seal, reduced the axial leakage gap that axial leakage and automatic compensate for wear cause, this unsteady axial lateral plate that can do the axial float compensation belongs to known technology, does not give unnecessary details here.Equally, the gap of the appropriate position between axial lateral plate P241 and fixed lateral plate P24 of floating is introduced high pressure oil pump P2 is made the axial float compensation, and fixed lateral plate P14, P24 liquid thickly are installed in common housing P40 two ends and constitute pump P1 and P2 can together.The high pressure oil in the back pressure interval of two pumps is through being entered in the middle of the common housing the shared output oil duct in the side plate by separately balance radial seal piece sealing or the flute profile oilhole of opening and from shared oil outlet tube POUT output, between the low pressure oil that refluxes then enters separately low pressure area from shared oil inlet pipe P1N, as previously mentioned, the balance radial seal piece that moves certain pump can make this pump be in jointing state or separated state, and the output flow of this pump should be maximum mutually or is zero.This be connected in parallel on the same input shaft can a deciliter pump be called coaxial can deciliter pump, P1 among Fig. 4 and P2 be coaxial can deciliter pump.
Same principle, can constitute coaxial can deciliter motor.For example among Fig. 4, the same side gear M1G and the M2G of the gear of can deciliter motor M1 and can deciliter motor M2 can be sleeved on the output shaft AM with key axially slidably, M13, KM1, M141 and M14 be respectively can deciliter motor M1 balance radial seal piece, the back pressure interval, axial lateral plate and fixed lateral plate float, M23, KM2, M241 and M24 be respectively can deciliter motor M2 balance radial seal piece, the back pressure interval, axial lateral plate and fixed lateral plate float, M40 is two coaxial common housings that can deciliter motor, the high pressure oil that enters from oil inlet pipe MIN shared oil duct M53 the side plate in the middle of common housing enters the flute profile oilhole of each motor, if the balance radial seal piece of this motor does not seal its flute profile oilhole and is in full pump efficiency and answers the position, then high pressure oil promotes the gear pair rotation driving output shaft AM rotation of this motor, and hydraulic oil enters the oil outlet tube MOUT of motor again through between the low pressure area of motor.The unsteady axial lateral plate M141 of both sides and M241 to can deciliter motor M1 and the axial float compensating action principle of M2 still as above-mentioned.Can 2 gear shafts be arranged a deciliter motor, its switched in opposite in order to improve the transmission efficiency of direct retaining, should be coaxial output shaft that can deciliter motor to turn to the gear shaft identical with input shaft generally.
Each oil pipe of can deciliter pump and can deciliter motor all is connected on the steering control valve B, when the sealing flap BO of steering control valve forwards horizontal position shown in Fig. 4 to, coaxial oil outlet tube POUT and coaxial oil inlet pipe MIN that can deciliter motor that can deciliter pump connect, and coaxial oil outlet tube MOUT and coaxial oil inlet pipe PIN that can deciliter pump that can deciliter motor connect, the high pressure oil of pump output enters through steering control valve B that MIN enters again from POUT can deciliter motor, from the oil outlet tube MOUT of motor through steering control valve B get back to can deciliter pump oil inlet pipe PIN, finish circulation, this moment, turning to of motor was forward, and promptly output shaft AM is identical with turning to of input shaft AP; Otherwise, if the sealing flap BO of steering control valve B forwards horizontal position shown in dotted lines in Figure 4 to, then the oil outlet tube POUT of pump and motor oil pipe MOUT (oil-feed this moment) connect and motor oil pipe MIN (this moment is fuel-displaced) and pump oil inlet pipe PIN connection, motor is by the hydraulic oil driver inversion, turning to of transmission output shaft AM is opposite with input shaft AP, and speed changer is in reverse gear.Like this, the sealing flap BO that rotates steering control valve B just can change turning to of transmission output shaft, and the decision speed changer is operated in positive shelves or reverse gear.Certainly, the pattern of steering control valve has multiple, does not give unnecessary details here.
The input shaft of speed changer can mechanically directly be connected with output shaft, constitutes high efficiency direct high.For example among Fig. 4, make the input shaft AP and the output shaft AM coaxial line of speed changer, we known it in positive shelves two axles turn to identical, therefore can directly engage two axles with clutch, speed changer is in direct high, velocity ratio is 1, this moment all coaxial can deciliter pump and coaxially can all should be in separated state by deciliter motor, each is very little to dally in the oil power that consumes of gear pair, make speed changer obtain very high direct high transmission efficiency, the operating mode of running at high speed for a long time at vehicle can obtain good oil-saving effect.The joint of two axles with separate the taper non helping hand clutch principle that can use the inventor in Chinese patent literature 2005100069474 " non-boost automatic clutch employing inclined plane principle ", to propose, spiral awl AP1 has on the screw thread APS of identical pitch with the inner screw sheath of the system of getting on the bus of circle in it in the input shaft end, the direction of the spiral direction that to be spiral awl rotate with input shaft is rotated then spiral relative to input shaft on the contrary and is bored AP1 and move axially to the direction of output shaft, like this, under the shift fork induction force that transmits on the fork groove AP11 promotes gently, shift to output shaft when the spiral awl and produce friction with the friction taper sleeve AM1 that is connected on the output shaft with suitable inner conical surface, the direction of this friction torque is to make the relative input shaft of spiral awl AP1 counter-rotational, therefore make the spiral awl further be adjacent to the output shaft friction taper sleeve, produce bigger friction positive pressure and friction torque, make the spiral awl more be adjacent to again to friction taper sleeve, ..., so the self-excitation process of positive feedback will be set up enough friction torque greater than input torque rapidly, make input shaft not rely on any hydraulic booster electromagnetism power-assisted also just can engage with output shaft without friction plate, it is 1 direct high that speed changer enters speed ratio, each pump and motor are in separated state, the gear pair loss power that dallies in oil is minimum, makes that the transmission efficiency of direct high is very high; If input shaft and output shaft are thrown off, can reduce input shaft rotating speed (subtracting throttle slightly) by a small margin and make spiral bore relative input shaft to be inclined to and to relatively rotate in the same way and take place throwing off with the output shaft friction sleeve in a flash away from the moving axially of output shaft as motor.
In order to strengthen the axial float compensate function of the axial lateral plate that floats, can be as the example of Fig. 5, on the axial lateral plate M241 that floats, stick one deck elastic material such as engineering nylon by the one side of elements such as sealed gear M2G and balance radial seal piece M23, as M242, the axial lateral plate that floats like this promotes softer flexiblely being adjacent to by the element of axial seal of elastic material paster M242 from the oil pressure of obtaining with fixed lateral plate M24 gap, can further reduce the axial leakage gap, further reduce frictional loss (being easy to select to the littler engineering nylon of steel friction factor) and wearing and tearing between axial seal and sealed as paster material, better axial float compensation effect can be obtained in compensate for wear and the machining error axial seal gap of causing therefore better.
Can deciliter pump by separating and/or engaging certain, and separate and/or engage certain can deciliter motor, can change the velocity ratio of speed changer.For the speed changer that generally is mainly used in gearing down, should make and to have less gear diameter, tooth depth and the facewidth by deciliter pump, thereby have less revolution discharge capacity, can deciliter motor have bigger gear diameter, tooth depth and the facewidth and have bigger revolution discharge capacity thereby make.
Below in conjunction with embodiment the present invention is made and to further specify.
Embodiment 1: speed changer shown in Figure 4, with revolution discharge capacity that can deciliter gear pump P1 is 1, revolution discharge capacity=1.5 that can deciliter gear pump P2, can deciliter gear motor M1 and the revolution discharge capacity of M2 be respectively 3.25 and 14, then the theoretical velocity ratio of disregarding leakage loss of each grade (=input shaft rotating speed/output shaft rotating speed) can be separated and the combination of joint obtains by each pump and motor following:
The sealing flap BO of steering control valve B is the horizontal position of forward gears at positive shelves,
Advance 1 grade and engage P2 and separate revolution discharge capacity minimum=1 of pump, the revolution discharge capacity maximum=3.25+14 of motor, velocity ratio I1=(3.25+14)/1=17.25 for motor M2 and M1 engage pump P1;
Advance 2 grades for motor M2 engages motor M1 separation, pump P1 engages P2 and separates velocity ratio
I2＝14/1＝14；
Advance 3 grades and separate P2 and engage velocity ratio for motor M1 and M2 engage pump P1
I3＝(3.25+14)/1.5＝11.5；
Advance 4 grades for motor M2 engages the M1 separation, pump P2 engages P1 and separates velocity ratio
I4＝14/1.5＝9.3；
Advance 5 grades for motor M1 and M2 engage, pump P1 and P2 also engage, velocity ratio
I5＝(3.25+14)/(1+1.5)＝6.9；
Advance 6 grades for motor M2 engages the M1 separation, and pump P2 and P1 engage, velocity ratio
I6＝14/(1.5+1)＝5.6；
Advance 7 grades for motor M1 engages the M2 separation, pump is that P1 engages P2 separation, velocity ratio
I7＝3.25/1＝3.25；
Advance 8 grades for motor M1 engages the M2 separation, pump P2 engages P1 and separates velocity ratio
I8＝3.25/1.5＝2.2；
Advancing 9 grades is that motor M1 engages M2 and separates, and two pump P1 and P2 then engage velocity ratio
I9＝3.25/(1+1.5)＝1.3；
Advance 10 grades be direct high, as described above input shaft spiral awl AP1 is directly engaged with output shaft friction taper sleeve AM1, velocity ratio I10=1, each pump P1 of each motor M1 and M2 and P2 are in the line loss of separated state to avoid recycle oil to flow, transmission efficiency is the highest.
B is positioned at backward position when steering control valve, be that its sealing flap BO forwards horizontal position among Fig. 4 to, hydraulic oil oppositely passes through motor, all the time separate between input shaft spiral awl and the output shaft friction taper sleeve, speed changer just is operated in reverse gear, by aforementioned calculation as can be known, speed changer has down 1 grade until falling 9 grades of 9 reverse gears, the forward gears velocity ratio correspondent equal of the absolute value of its velocity ratio and jack per line.
When each pump and each motor all are in separated state, and input axial screw awl also separates with the friction taper sleeve of output shaft, and speed changer promptly is in neutral gear.
Like this, the pump efficiency that 2 motors of this 2 pumps are attacked 4 pairs of gear pairs should have 10 forward gearss, 9 reverse gears and 1 neutral gear by a deciliter speed changer, is suitable for engineering machinery.
Preliminary calculating shows, pump efficiency should deciliter speed changer few and pump and motor all have the full compensation characteristic that axial float compensation and radial floating compensate because of transmission link, therefore transmission efficiency is higher, speed changer simple and compact for structure, volume weight is less, because number of parts wearing and tearing few, hydraulic element are compensated, the joint of balance radial seal piece separates is progressive, greatly reduced to engage to separate and impacted and the pulsating load impact, so pump efficiency answers reliability, shock-resistant ability and the operating life of deciliter speed changer all very high.Operating mode with 180 kilowatts of maximum input torque 1000NM of input power, working hydraulic pressure 20 MPas is an example, 240 millimeters of the gear compound graduation circular diameters of 120 millimeters motors of gear pair standard pitch diameter of pump, the facewidth that the facewidth of pump P1 is about 20 millimeters P2 is about 30 millimeters, the facewidth of motor M1 is about about 143 millimeters of the facewidth of 33 millimeters M2, the about 350-390 kilogram of complete machine weight, total transmission efficiency rough calculation: 1 grade of about 0.68-0.72,4 grades of about 0.72-0.75 of middle bay, direct high about 0.98.The existing Hydromechanical transmission that compares same specification: 3 reverse gears of 4 forward gearss, the transmission efficiency of maximum transmission ratio approaches zero, the highest transmission efficiency about 0.78, middle bay transmission efficiency about 0.68, about 800 kilograms of weight, volume is bigger, and as can be known, pump efficiency of the present invention should have higher performance index and lower manufacture cost by deciliter speed changer.
Each can deciliter pump or the parallel connection of motor also can be coaxial form, but with the form of coplanar multiple gearpump, allow each gear polyphone mesh, not only can reverse gear be set easily and save steering control valve, can also adapt to the engineering machinery engine axle to bigger wheelbase between the driven bridge axle, be also used as the between centers driving gear.A configuration example can be referring to schematic representation Fig. 6 and Fig. 7.The engagement of in same radial plane, contacting of a plurality of gears in the housing 4 of coplanar multiple gearpump P, it in the example of Fig. 6 the engagement of 3 gear polyphones, intermediate gear G3 and input gear G1 engagement and the balance radial seal piece P13 that is made into integration, flute profile oilhole P153 and controlling rod P135 constitute together can deciliter input gear pump, be in jointing state among the figure, input gear G1 is transfused to an AIN and drives, each gear direction of arrow as shown rotates, when moving to left, separates with the tooth top of gear G1 and G3 when having sealed its flute profile oilhole P153 simultaneously balance radial seal piece P13, the input gear pump promptly separates, if this moment, the balance radial seal piece P23 with the center tooth wheel pump was pushed to gear G2 and the radial seal of G3 formation by its controlling rod P235, principle as described above, then the center tooth wheel pump engages, high pressure oil is from its flute profile oilhole output, generally make each polyphone meshed gears have the identical facewidth so that seal with common side plate, oil refluxes from the public oilhole PIN on the housing 4, all be in separated state when importing gear pump and center tooth wheel pump, flute profile oilhole separately is all by the sealing of separately balance radial seal piece, and reverse gear controlling rod R35 pushes over the tooth top formation radial seal that grade balance radial seal piece R3 shifts to gear G3 and G2, then the reverse gear pump engages, by turning to as can be known of Fig. 6 middle gear G2 and G3, the direction of reverse gear pump oil stream is opposite, promptly oil is inhaled into from the flute profile oilhole of reverse gear pump, between the public area between cog is pressed towards housing 4, the radial seal piece P13 of two forward pumps of process separated state this moment and the ample clearance between P23 and the gear teeth tips, high pressure oil is exported from public oilhole PIN, because pump P has exported reverse oil stream at this moment, must make and the oil hydraulic motor switched in opposite make speed changer be operated in reverse gear.The flute profile oilhole that is each sub-pump in the pump all is through pipeline and receives the oil inlet hole MIN of motor M, the public oilhole PIN that the oil outlet MOUT of motor then receives pump (can arrange a plurality of in the interval of each sub-pump, connect together), when importing gear pump joint or center tooth wheel pump joint or engaging together, the forward oil stream that POF is different, flowing into motor from the oil inlet hole MIN of motor flows back to from the oil outlet MOUT of motor, motor will be with corresponding different rotating speed forward rotation, when the input gear pump of pump waits the sub-pump of each forward all to separate with center tooth wheel pump (can be more than) and reverse gear pump when engaging, the reverse oil flow of pump output flows into motor and flows back to pump from motor oil inlet hole MIN from the oil outlet MOUT of motor, the motor counter-rotating, speed changer works in reverse gear.The sub-pump of each forward that is made of the polyphone engaging gear in coplanar gear pump or the motor and the absolute value (the reverse gear pump displacement is a negative value) of the revolution discharge capacity of reverse gear pump delivery for input shaft all equate, the positive reverse gear of the speed changer that this method obtains has not just needed steering control valve B, the oil pipe of pump and motor directly is connected, line loss reduces, and use gear can constitute more pump than peanut, coplanar pump as Fig. 6 has 2 sub-pumps of forward and a reverse gear pump but only to use 3 gears, can save manufacture cost in some occasion.
In the common engineering machinery, engine shaft in the above and the driven bridge axle below, between wheelbase bigger, can allow the double as of speed changer own be the between centers transmission with arrangement illustrated in Figure 7.Allow the middle output shaft of minimum that gear shaft AOUT of pump inner position as pump, the position that can be through the front above-mentioned spiral awl AP1 and the joint principle of friction taper sleeve AM1 directly engage motor M by last and design just walk around to pump in the middle of the identical motor centre input shaft AMIN of output shaft AOUT, when each pump and motor all are in separated state and this two axles and directly engage, pump input shaft AIN is the direct output shaft that through the engagement of motor internal gear power is passed to motor again that engages of output shaft AOUT and motor centre input shaft AMIN in the middle of the engagement of gear G1-G3-G2 and pump mechanically just, the ends A MOUT1 of motor output shaft and AMOUT2 receive the preceding driven bridge input shaft of coaxial line and back driven bridge input shaft respectively, motor has higher transmission efficiency to being that machinery is direct-connected between the bridge at this moment.Fig. 6 has 2 sub-pumps of forward (the revolution discharge capacity of the sub-pump of each forward that the engagement of gear polyphone constitutes is identical) and a reverse gear pump with speed changer shown in Figure 7, there are 2 coaxial sub-motors motor the inside, can constitute the reverse gear of the direct-connected forward gears of the forward gears of 6 hydraulic pressure, 1 machinery and 3 hydraulic pressure and neutral gear (each sub-pump all separates with sub-motor, jack shaft also throw off).Be easy to find out, the right of Fig. 6 middle gear G1 and G3 promptly can also be provided with on the opposite one side of balance radial seal piece P13 the such reverse gear balance radial seal piece of R3 and reverse gear flute profile oilhole constitute another can deciliter reverse gear pump, this moment, the quantity of speed variator reverse gear also just rose to 6, promptly formed the speed changer of 7 positive shelves 6 reverse gears with 7 gears.
Same principle, a balance radial seal piece and a flute profile oilhole can be set on every limit, the both sides of a pair of gear pair,, form a forward pump and a reverse gear pump jointly by side plate axial seal, can save the steering control valve B in Fig. 4 speed changer, principle is as above-mentioned.
As everyone knows, the total efficiency height of internal gear pump/motor, compact structure, flow pulsation is little.Internal gear pump/motor also can be made can deciliter pump/motor, and basic skills is still the Sealing that moves it and causes pump efficiency to disappear or to occur, and one of implementation structure as shown in Figure 8.
Among Fig. 8, the gear 100 that is loaded on the gear shaft 101 keeps engagement with internal gear 200, its axial both ends of the surface are thickly sealed by side plate 400 (still can establish unsteady axial lateral plate as described above) liquid, be installed in the top and the gear 100 of the radial seal piece 300 on the Control Shaft 301, the formation radial seal of thickly fitting of tooth top liquid in each one section circular arc of bottom and internal gear 200, promptly constitute internal gear pump, when gear pair is driven direction of arrow rotation as shown by gear shaft 101, hydraulic oil enters L interval (being between low pressure area at this moment) from the flute profile oilhole of opening on side plate 400 410, be pressed into H interval (being between the zone of high pressure at this moment) through between cog, again from driving the flute profile oilhole 530 output inner gear pumps on side plate 400, radial seal this moment piece 300 is in full pump efficiency and answers the position, pump is in jointing state, when radial seal piece 300 inhour under the driving of Control Shaft 301 is rotated, its top radial sealing surfaces promptly breaks away from the tooth top of gear 100, the radial sealing surfaces of bottom promptly breaks away from the tooth top of internal gear 200, the pump efficiency benefit weakens until disappearance, and the radial seal piece is such with its side plane sealing flute profile oilhole when moving as described above, the top of radial seal piece 300 is with its side plane sealing flute profile oilhole 530, lower side planar surface encloses flute profile oilhole 410, pump promptly is in separated state.Can from partial view Fig. 9, more clearly see this process, in the partial view on Fig. 9 left side, radial seal piece 300 has sealed flute profile oilhole 530 and 410 because of the inhour rotation, be that the radial seal piece is the position that is in separation among Fig. 9, the flute profile oilhole that is closed is expressed as dotted line, the clear radial seal piece 300 of having represented of the C-C part sectioned view on Fig. 9 the right has sealed the flute profile oilhole of opening on side plate (530) with its side plane with side plate 400 applyings, when radial seal piece 300 clockwise rotates then among the right figure of Fig. 9 radial seal piece 300 along moving on the double-head arrow direction around Control Shaft 301, to get out of the way flute profile oilhole 530 and make the oilhole conducting, the sealing side plate of the opposite side of pump is represented in the double dot dash line that is attached to radial seal piece 300 the right, generally on the side plate of shape oilhole one side of not slotting the axial float side plate is set.When turning clockwise just to return again, radial seal piece 300 reopens flute profile oilhole 530 and 410 and make the tooth top of its top radial seal gear 100, the tooth top of bottom radial seal gear 200 under Control Shaft 301 drives.For Control Shaft can be rotated trippingly, to the design of the position of Control Shaft 301 in radial seal piece 300 should make hydraulic oil to the hydraulic coupling of radially sealing block top effect make a concerted effort the moment of torsion of Control Shaft is made a concerted effort the reactive torque size of Control Shaft is equated also substantially slightly greater than the latter with the hydraulic coupling that hydraulic oil acts on radial seal piece bottom, make Control Shaft not only can be rotated easily artificially, can also allow the radial seal piece under the effect that action of hydraulic force make a concerted effort to produce, slightly press to the difference in torque of Control Shaft in the tooth top of external gear, formation is the radial floating compensation of gear pump to the automatic compensation of wearing and tearing of gear pair tooth top and radial clearance, if on radial seal piece and radial sealing surfaces that tooth top contacts, stick the engineering nylon thin layer as described above, allow engineering nylon aspect liquid tooth top of pressed toward gear thickly flexibly under the slight effect of hydraulic coupling difference in torque, the effect of then this automatic radial floating compensation can be better, make the radial seal piece become rotating balance radial seal piece like this, with interior external gear, side plate and flute profile oilhole constitute together can deciliter internal gear pump/motor.
This driving wheel that can deciliter internal gear motor be particularly suitable as the direct powered vehicle of wheel motor, be loaded on direct driving wheel in the hub for vehicle wheel with its inner gear housing, can obtain bigger driving torque greatly because of the internal gear diameter, thereby can save the wheel reductor of establishing in order to amplify torque that common wheel motor output shaft connects.With two driving wheels about coaxial can deciliter internal gear motor advance, oil outlet respectively and connect, two motors are in parallel on oil circuit, be under the identical oil pressure and a definite input flow rate will be diverted to two motors, promptly the flow sum of two motors equals the total discharge of this ransaxle, if this moment is Vehicular turn, then the resisting moment of big its wheel motor of turning medial resistance wheel is bigger, its input flow rate reduces and the motor of opposite side is because of being in that the outside resisting moment of turning is less gets bigger flow automatically automatically under identical input oil pressure effect, makes two motors of oil circuit parallel connection have the function of differential mechanism; When the motor oil circuit of coaxial both sides wheel is contacted, promptly the oil outlet of a side motor connects the oil inlet hole of opposite side motor, total oil inlet and outlet after the series connection is received pump, the flow that flows through of two motors must equate so, the rotating speed of two motors equates, this ransaxle promptly is in the chain state of differential, and this state helps vehicle and climbs out of mire.Promptly by valve allow rightly the both sides motor oil circuit and connect or be connected in series, then this ransaxle is in differential drive condition or the chain drive condition of differential automatically.
The above-mentioned radial floating compensation that can deciliter internal gear pump/motor has the axial float compensation of axial float side plate and turn balance radial seal piece, it is the high efficiency pump of full compensation, usually its total efficiency can reach 0.9, pay with existing helical bevel gear+total efficiency about the 0.91-0.92 of the mechanical transmission bridge of wheel reductor compares, and is only lower slightly or suitable; Can deciliter internal gear pump being the pump of many gears flow, the wheel of receiving each bridge through the very little thick oil pipe of resistance can deciliter internal gear motor, promptly form can deciliter internal gear pump/motor the complete quiet liquid of vehicle drive, the total efficiency of power train is about 0.9 * 0.9=0.81, with the total efficiency of the pure mechanical transmission system of existing vehicle quite or lower slightly, but be higher than the power train total efficiency of existing Hydromechanical transmission+mechanical transmission bridge type formula.
Can deciliter internal gear pump/motor also can make coaxial form, be that the external gear (100) of each pump/motor is loaded on common gear shaft (101) with key and goes up and can endwisely slip along gear shaft, the form of forming speed changer, coaxial with 2 pumps that Fig. 4 describes, the coaxial scheme of 2 motors is comparatively economical, external gear pump/motor among Fig. 4 is changed into corresponding internal gear pump/motor, other content can be constant, also can be provided with between pump shaft and the motor drive shaft spiral awl AP1 and friction taper sleeve AM1 such engage the direct-connected mechanism that separates, constitute 10 forward gearss and comprise a direct high that machinery is direct-connected, 9 reverse gears and 1 neutral gear, the total efficiency of indirect gear can be higher than Hydromechanical transmission up to about 0.81.
Single can deciliter internal gear pump/motor also can be provided with reverse gear, and its principle is still by the mobile of corresponding radial seal piece or rotates sealing when engaging with tooth top or separating, the corresponding flute profile oilhole of unlatching.An one example of structure can be referring to the signal of Figure 10.Among Figure 10, gear shaft 101 actuation gears 100 and the internal gear 200 that is engaged with rotate (by illustrating the direction of arrow for clockwise rotating) together, the present position is the disengaging configuration among radial seal piece 300 figure, when its controlled axle 301 inhour is rotated, one section tooth top liquid of its positive shelves external gear sealing surface 3001 and external gear 100 connects airtight and touches the formation radial seal, one section tooth top liquid of its positive shelves internal gear radial sealing surfaces 3002 and internal gear 200 connects airtight and touches the formation radial seal, open in 4 flute profile oilholes on side plate 400 this moment positive shelves oil inlet hole 410 and a positive shelves oil outlet 530 be opened that (principle still as described in Figure 9, do not give unnecessary details), reverse gear oil inlet hole R410 and reverse gear oil outlet R530 are then sealed by radial seal piece side plane, hydraulic oil flows into through between cog from positive shelves oil inlet hole 410 and is forced out from positive shelves oil outlet 530, the driving oil hydraulic motor is rotated in the forward, and this moment, pump was in positive shelves jointing state; When making its reverse gear external gear sealing surface 3001R contact with 100 1 sections tooth tops of external gear to sealing block 300, Control Shaft 301 counterclockwise rotation radius vectors form radial seal, one section tooth top liquid of its reverse gear internal gear radial sealing surfaces 3002R and internal gear 200 connects airtight and touches the formation radial seal, positive shelves oil inlet hole 410 and positive shelves oil outlet 530 are closed, reverse gear oil inlet hole R410 and reverse gear oil outlet R530 then are opened, hydraulic oil flows into from reverse gear oil inlet hole R410 and is forced out from reverse gear oil outlet R530 through between cog, drive the oil hydraulic motor counterrotating, pump promptly is in the reverse gear jointing state, and Control Shaft forwards radial seal piece 300 to shown in Figure 10 neutral position, 4 flute profile oilholes are opened entirely and the radial seal piece does not contact with any tooth top, the internal gear pair consumption of power that dallies in oil is minimum, pump promptly is in separated state, and corresponding speed changer is in neutral gear.Such pump be called two-way can deciliter internal gear pump/motor.
Embodiment 2: the vehicle of the quiet liquid transmission of a kind of full car, pump by on engine shaft direct 2 coaxial two-way can deciliter internal gear pump pump 1 and pump 2 form, the external gear of two internal gear pumps all is to be loaded on launched arbor driving on the engine shaft with key, the positive shelves oil outlet of two pumps is also received on total oil outlet of pump, the positive shelves oil inlet hole of two pumps is also received on total oil inlet hole of pump, the reverse gear oil outlet of two pumps is also received on total oil inlet hole of pump, the reverse gear oil inlet hole of two pumps is also received on total oil outlet of pump, external gear revolution discharge capacity with pump 1 is 1, the external gear revolution discharge capacity of pump 2 is 1.6, total oil outlet of pump is received on the propons oil inlet hole and back axle oil inlet hole of vehicle through pipeline and distributing valve, total oil inlet hole of pump is received on the propons oil outlet and back axle oil outlet of vehicle through pipeline and distributing valve, on the oil inlet hole of each bridge and two wheel can deciliter internal gear motor oil inlet hole connect, on the oil outlet of each bridge and two wheel can deciliter internal gear motor oil outlet connect, each wheel by install in its wheel hub can deciliter internal gear motor internal gear directly drive and do not have wheel reductor, each wheel can deciliter internal gear motor internal gear revolution discharge capacity be 10.25, the output flow of pump is the algebraic sum of two pump dutys, certain pump be positive shelves when engaging its revolution discharge capacity on the occasion of, its revolution discharge capacity is a negative value when engaging for reverse gear, and each grade is constructed as follows table:
| Gear | Pump 1 operating mode | Pump 2 operating modes | The total displacement of pump | The motor total displacement | Resultant gear ratio |
| Advance 1 | Reverse gear engages | Positive shelves engage | ??1.6-1＝0.6 | ??10.25*4＝41 | ??68.3 |
| Advance 2 | Positive shelves engage | Separate | ??1 | ??41 | ??41 |
| Advance 3 | Separate | Positive shelves engage | ??1.6 | ??41 | ??25.6 |
| Advance 4 | Positive shelves engage | Positive shelves engage | ??1+1.6＝2.6 | ??41 | ??15.8 |
| Advance 5 | Reverse gear engages | Positive shelves engage | ??1.6-1＝0.6 | ??10.25*2＝20.5 | ??34.2 |
| Advance 6 | Positive shelves engage | Separate | ??1 | ??20.5 | ??20.5 |
| Advance 7 | Separate | Positive shelves engage | ??1.6 | ??20.5 | ??12.8 |
| Advance 8 | Positive shelves engage | Positive shelves engage | ??1+1.6＝2.6 | ??20.5 | ??7.9 |
| Neutral gear | Separate | Separate | ??0 | Each motor separates | ??--- |
| Reverse gear 1 | Positive shelves engage | Reverse gear engages | ??1-1.6＝-0.6 | ??41 | ??-68.3 |
| Reverse gear 2 | Reverse gear engages | Separate | ??-1 | ??41 | ??-41 |
| Reverse gear 3 | Separate | Reverse gear engages | ??-1.6 | ??41 | ??-25.6 |
| Reverse gear 4 | Reverse gear engages | Reverse gear engages | ??-2.6 | ??41 | ??-15.8 |
| Gear | Pump 1 | Pump | 2 operating modes | The total displacement of pump | The motor total displacement | Resultant gear |
| Reverse gear | ||||||
| 5 | Positive shelves engage | Reverse gear engages | ??1-1.6＝-0.6 | ??10.25*2＝20.5 | ??-34.2 | |
| Reverse gear 6 | Reverse gear engages | Separate | ??-1 | ??20.5 | ??-20.5 | |
| Reverse gear 7 | Separate | Reverse gear engages | ??-1.6 | ??20.5 | ??-12.8 | |
| Reverse gear 8 | Reverse gear engages | Reverse gear engages | ??-2.6 | ??20.5 | ??-7.9 |
Annotate: positive 5-8 shelves are distributing valve with the shelves of falling 5-8 and the output flow of pump are received (two motors of another bridge separate) on two motors of a bridge, half when so the motor total displacement has only 4 wheel drive, this operating mode is used for engineering machinery travels, and the operating mode that distributing valve is all connected 4 motors of two bridges is used for the full wheel drive of engineering machinery when work needs.
The about 300 millimeters facewidth of the internal gear standard pitch diameter of motor are about 90 millimeters in this example, 26 millimeters of the about 100 millimeters facewidth of the external gear standard pitch diameter of pump 1, about 42 millimeters of the about 100 millimeters facewidth of the external gear standard pitch diameter of pump 2, the nominal operation hydraulic coupling is about 25 MPas, about 65 kilograms of the weight of pump, pump and motor all are full compensation, and efficient is about 0.9, total transmission efficiency is about 0.8, is higher than the total efficiency that existing Hydromechanical transmission adds the mechanical transmission bridge.Efficient is lower greatly but internal gear motor is leaked when the low-speed big operating mode.
Can play differential action automatically by deciliter motor with the both sides of oil circuit in parallel as described above when turning to, the flow that also can flow divider valve changes the both sides wheel motor is realized turning to, then vehicle sharply turns to so that pivot stud when a side motor is just changeing opposite side and makes it to reverse by the reverse gear oil transportation, simply, can also make the wheel motor of turning medial separate and the wheel motor driving in the outside of turning, realize simply turning to by steering wheel control direction wheel.
Present embodiment is applicable to engineering machinery, about 160 kilowatts/2200 rpms of engine power, the about 800 Ns of rice of the maximum input torque of gear pump, about 760 millimeters of tire rolling radius, about 67 kilometers/hour of the highest speed of advancing and counting flow loss 8 grades the time.
Certain gear shaft of said gear pump/motor all can be used as pto, and the gear pump of speed changer all can be used as the working gear pump that engineering machinery drives hydraulic work machinery.
Oil hydraulic motor of the present invention can be also used as break, it is the fuel-displaced oil circuit oil outlet of closed motor for example that motor cuts off motor with valve when being in jointing state in addition, high pressure oil can't be drained and liquid is incompressible, constituted the braking moment to motor drive shaft, what can have braking function can serve as the vehicle braked device by a deciliter motor.
Of the present invention by adding particularly air sac type liquid gas energy storage device of hydraulic energy storage device in the transmission system of can deciliter gear pump and can deciliter gear motor constituting, can deciliter motor when vehicle needs retarding braking engage and the high pressure oil of its oil outlet output is imported accumulator through valve, thereby the kinetic energy of vehicle is converted to the potential energy in the accumulator in the time of will braking, when vehicle need start to walk to quicken, with the high pressure oil in the accumulator through valve derive to inject can deciliter motor oil inlet hole promote the starting of motor running powered vehicle and quicken, oil flowed out through valve from the motor oil outlet and flowed into oil sump this moment, can can be in separated state by deciliter gear pump this moment, motor can be in idling, can engage with motor relay powered vehicle by a deciliter gear pump when vehicle is driven into sufficiently high speed by accumulator again; Equally, accumulator also can disengage injection with high pressure oil through valve when engineering machinery is worked can promote or its work of boosting by deciliter motor, traction and propulsion capability when betterment works machinery is worked under wheel low-speed big operating mode, in order to make accumulator keep the frequent use of energy storage when adapting to engineering machinery work, can deciliter gear pump inject high pressure oil through valve to accumulator by engine-driving increases energy storage.
Can deciliter gear pump and motor can also be used to starting under load oil-electric engine group, adorn on the internal combustion engine shaft one can deciliter gear pump adorn on generator shaft that a revolution discharge capacity equates with pump can deciliter gear motor, be provided with the spiral awl AP1 shown in Figure 4 and the direct coupling device of friction taper sleeve AM1 formation between two axles, when need starting apparatus combustion engine generator set, pump and motor are all placed separated state, the fully loaded electric load internal-combustion engine of generator belt is No Load Start then, engaging gradually then can deciliter pump and motor, make generator load receive internal-combustion engine flexibly, pump and motor engage to be finished generator speed separate pump and motor when normal and directly engages internal combustion engine shaft and generator shaft with spiral awl and friction taper sleeve simultaneously, internal-combustion engine directly drives generator and pump and motor are extremely low because of being in the separated state loss, this use can deciliter pump and the juncture of motor help when having a power failure, requiring the emergency start generator set time light-load starting internal-combustion engine can make its power supply reach the frequency and the voltage of regulation rapidly by the gentle engagement generator again.
The basic skills that realizes purpose of the present invention comprises that certain Sealing that makes oil hydraulic pump or motor can answer position and zero pump efficiency to answer between the position at full pump efficiency because of suffered hydraulic coupling is in a basic balance and move trippingly, corresponding oil outlet or the oil inlet hole that opens or closes pump or motor when mobile, make corresponding jointing state or the separated state of being in of pump or motor, this movable Sealing not only can be served as by the radial seal piece, also can serve as by axial seal, for example make sliding axle serve as movable Sealing to the sealing side plate, its principle can be referring to the signal of Figure 11.
Among Figure 11, external gear 1000 is installed in 2000 engagements of the internal gear in being set in housing 4000 and direction of arrow rotation as shown on the gear shaft 1000, at radial seal piece 3000, stationary axle is formative gear pump or motor under the sealing of sealing side plate 6000 to sealing side plate 6100 and sliding axle, oil enters H between the zone of high pressure from the oil inlet hole (not shown) through between cog and flows out from the high pressure oilhole of opening on slip side plate 6,000 6001, enter interval K of back pressure that liquid thickly surrounds between slip side plate 6000 and the housing 4000 and oil outlet 4001 outflows of offering from housing, the interval hydraulic oil of back pressure provides a back pressure to make its suffered both sides hydraulic coupling pressed toward gear side in a basic balance and slight form unsteady axial seal to the slip side plate 6000 that act as of slip side plate, this belongs to known technology, do not give unnecessary details, have this moment the side plate that endwisely slips can deciliter gear pump or motor be in jointing state, need to prove especially, slip side plate 6000 is that liquid thickly is bearing within the housing 4000 and can slides vertically, because its suffered hydraulic coupling is in a basic balance, so the controlling rod 6003 that can be installed on it draws back trippingly or pushes, when controlling rod will be in the slip side plate of jointing state when drawing back away from the gear direction, the axial clearance that occurs between slip side plate and gear and the radial seal piece strengthening gradually should weaken pump efficiency, with gear pair and radial seal piece enough big axial clearance is arranged during position shown in the dotted line among the slip side plate arrival figure, the gear pair wasted work that dallies in oil is minimum, pump efficiency is answered complete obiteration, slide the cylndrical surface 6002 of side plate simultaneously with housing oil outlet 4001 complete closed, this pump or motor promptly are in separated state.As seen, have the side plate that endwisely slips can deciliter gear pump or the action principle of motor with have movable radial seal piece can deciliter gear pump or motor be corresponding identical.When high pressure oil from housing oilhole 4001 inject high pressure oilhole on the slip side plate enter just form when H between the zone of high pressure promotes gear pair and rotates have a side plate that endwisely slips can deciliter gear motor, process is not given unnecessary details.Have the side plate that endwisely slips can deciliter gear pump or motor also can constitute the form of external gear pump or motor according to same principle, the side plate external gear wheel that endwisely slips this moment is paid with the radial seal piece and the axial seal and the corresponding sealing of separable and joint is provided and opens the housing oilhole, this is that common engineer is understandable, does not also give unnecessary details.A plurality of have the side plate that endwisely slips can deciliter gear pump or motor also as described above principle form coaxial pump or motor or form coplanar pump or motor, make the algebraic sum of its total displacement for the discharge capacity of each sub-pump or motor, thereby further principle is formed hydrostatic separable speed changer as described above, the joint by handling certain a little pump and/or motor and/separate the purpose that the change flow reaches speed change.
By can deciliter gear pump with the forward and reverse joint of each pump of the quiet liquid speed changer that can deciliter gear motor constitutes and motor and steering force that separates the required radial seal piece or the side plate that endwisely slips and above-mentioned direct joint, to separate the required power of stirring of axial screw awl-friction taper sleeve all very little, permission is handled with the electromagnetic push device, thereby whole drive system is easy to realize electrical autocontrol.
If not otherwise specified, the pump delivery of mentioning is the revolution discharge capacity that this pump input shaft is whenever goed around in this specification, and the discharge capacity of the motor of mentioning is the revolution discharge capacity that this motor output shaft is whenever goed around.
Claims (20)
1. separable gear pump or motor, comprise the pitch wheel pair, housing and movable radial seal piece, gear pump or motor drive shaft to bi-side thickly sealed by side plate liquid, it is characterized in that, also comprise at least 1 flute profile oilhole of opening on the axial seal side plate (53), the radial seal piece moves to one section tooth top circular arc that arc surface liquid that its radius equals the gear teeth tips circle radius thickly touches each gear symmetrically to the gear pair direction and seals side plane that a plurality of tooth tops constitute the radial seal radial seal simultaneously piece of gear pumps and open the flute profile oilhole and make the oil circuit of pump or motor open-minded, gear pump or motor are in jointing state, the radial seal piece leaves tooth top and produces enough big gap allow the radial seal effect disappear oil circuit that its side plane sealing flute profile oilhole simultaneously cuts off pump or motor to make the flow of pump or motor be zero to the direction of leaving gear pair its arc surface that equals the gear teeth tips circle radius that moves, and gear pump or motor promptly are in separated state.
2. according to claim 1 can deciliter gear pump or motor, it is external gear pump or motor, it is characterized in that, the pipeline (34) that has hollow in the radial seal piece (3) leads to the interval K of the back pressure that surrounds with back pressure housing (5) and side plate, the interval K hydraulic oil of back pressure act on the pressure of radial seal piece and other point to gear direction make hydraulic coupling that radial seal piece and tooth top contact to make a concerted effort be that activating pressure equals or is separating pressure greater than the radial seal piece towards making of being subjected to of the curved surface of the gear hydraulic coupling that the radial seal piece separates with gear teeth tips slightly, make the radial seal piece be able to automatically that tooth top that pressed toward gear gently pays forms the radial floating compensation and the controlling rod (35) of axis by the center of making a concerted effort that can be installed on it easily spurs or promote, radial seal piece or equilibrium block that be connected on it or one (31) liquid thickly are set within the equilibrium block cover (51) of engineering nylon material and can move under the constraint of equilibrium block cover (51), sealing between itself and the housing (4) is finished by the intermediate seal ring (42) of engineering nylon material, constitute the radial seal piece at the equilibrium block cover (51) of engineering nylon material and the elastic floating support on the intermediate seal ring (42), make the radial seal piece be adjacent to the tooth top of the relatively poor gear of radial seal more if better then its bigger between cog gradient pressure of the radial seal of certain gear will produce an adjustment couple, make between the radial seal of radial seal piece to two gears to average out automatically.
3. according to claim 2 can deciliter gear pump or motor, it is characterized in that, also on housing (4), offer control oil duct (43) and introduce the control interval (J) that the control hydraulic oil injection of the controlled valve control of pressure is surrounded by equilibrium block convex shoulder (311) and equilibrium block cover (51) and housing (4), the control interval (J) that has internal pipeline connection both sides on the equilibrium block equates its oil pressure, the control interval oil pressure acts on the equilibrium block convex shoulder and produces hydraulic control power, thereby the motion of radial seal piece can be handled trippingly.
4. according to claim 1 can deciliter gear pump or motor, it is characterized in that, it is external gear pump or motor, movably a radial seal piece and a flute profile oilhole are set on every limit, the both sides of a pair of gear pair, jointly by side plate axial seal, the flow direction of its flute profile oilhole hydraulic oil was opposite when the flow direction of its flute profile oilhole hydraulic oil engaged with another side radial seal piece when on one side the radial seal piece engaged, and formed a separable forward pump or motor and separable reverse gear pump or motor.
5. according to claim 1 can deciliter gear pump or motor, it is characterized in that, it is internal gear pump or motor, be installed in the top and the external gear of the radial seal piece (300) on the Control Shaft (301) in addition, the formation radial seal of thickly fitting of tooth top liquid in each one section circular arc of bottom and internal gear, hydraulic oil passes in and out internal gear pump or motor from the flute profile oilhole (530) that is positioned at radial seal piece another side of opening the flute profile oilhole (410) that is positioned at radial seal piece one side on side plate (400) and open on side plate, this moment, pump or motor were in jointing state, when rotating under the driving of radial seal piece at Control Shaft, its top radial sealing surfaces promptly breaks away from the tooth top of external gear, the radial sealing surfaces of bottom promptly breaks away from the tooth top of internal gear, the piece of radial seal simultaneously is with its side plane sealing flute profile oilhole, pump or motor promptly are in separated state, promptly by rotating joint that the radial seal piece can control internal gear pump or motor and separating, to the design of the position of Control Shaft (301) in radial seal piece (300) make hydraulic oil to sealing block effect radially make hydraulic coupling that pump or motor engage make a concerted effort the hydraulic coupling that pump or motor are separated that the moment of torsion of Control Shaft and hydraulic oil act on the radial seal piece is made a concerted effort to equate and slightly greater than the latter the size of the reactive torque of Control Shaft is basic, make Control Shaft not only can be rotated easily, can also allow the radial seal piece under the effect of this difference in torque, slightly press in the tooth top of external gear to form automatic compensation to wearing and tearing of gear pair tooth top and radial clearance be that the radial floating of gear pump or motor compensates.
6. according to claim 5 can deciliter gear pump or motor, it is characterized in that, on side plate, also have reverse gear oil inlet hole (R410) and reverse gear oil outlet (R530), when the controlled axle of radial seal piece (300) (301) rotates to a direction, one section tooth top liquid of its positive shelves external gear sealing surfaces (3001) and external gear connects airtight and touches the formation radial seal, one section tooth top liquid of its positive shelves internal gear radial sealing surfaces (3002) and internal gear connects airtight and touches the formation radial seal, be opened reverse gear oil inlet hole (R410) and reverse gear oil outlet (R5300) of positive shelves oil inlet hole (410) and positive grade of oil outlet (530) then sealed by the side plane of radial seal piece, hydraulic oil flows into through between cog from positive shelves oil inlet hole and flows out from positive shelves oil outlet, this moment, pump or motor were in positive shelves jointing state, when contacting one section tooth top of its reverse gear external gear sealing surface (3001R) and external gear, Control Shaft backward rotation radial seal piece forms radial seal, one section tooth top liquid of its reverse gear internal gear radial sealing surfaces (3002R) and internal gear connects airtight and touches the formation radial seal, positive shelves oil inlet hole (410) and positive shelves oil outlets (530) are sealed by the side plane of radial seal piece and reverse gear oil inlet hole (R410) and reverse gear oil outlet (R530) are opened, hydraulic oil flows into from reverse gear oil inlet hole (R410) and flows out from reverse gear oil outlet (R530) through between cog, pump or motor promptly are in the reverse gear jointing state, when Control Shaft forwards the radial seal piece to neutral position, 4 flute profile oilholes are opened entirely and the radial seal piece does not contact with any tooth top, the internal gear pair consumption of power that dallies in oil is minimum, and pump or motor promptly are in separated state.
According to claim 1 or claim 4 or claim 6 can deciliter gear pump or motor, it is characterized in that, have such pump or motor more than 2 or 2, in its gear pair a corresponding gear all install or axially slidably key be contained on the same gear shaft, form coaxial can deciliter gear pump or motor, positive shelves oil outlet and each reverse gear oil inlet hole of its each pump or motor also connects, positive shelves oil inlet hole and each reverse gear oil outlet of its each pump or motor also connects, just handle each pump or motor, reverse gear engage with/separate, make coaxial can deciliter gear pump or the total displacement of motor for the algebraic sum of each pump or motor displacement, reach the variable purpose.
8. according to claim 1 can deciliter gear pump or motor, it is characterized in that, have such pump or motor more than 2 or 2, its each gear all is in polyphone engagement in the same radial plane, wherein import gear (G1) and be transfused to axle (AIN) driving, other gear is driven because of the polyphone engagement, each gear has the equal facewidth can be by same axial seal side plate sealing, movably radial seal piece and the flute profile oilhole that opened and closed by this radial seal piece promptly constitute a separable sub-gear pump or motor to add one between intermeshing 2 gears, the direction that its flute profile oilhole hydraulic oil passed through when each sub-pump or motor turned to decision to engage by its gear pair, what the oil forward passed through is sub-pump of forward or motor, what oil oppositely passed through is sub-pump of reverse gear or motor, the joint by handling sub-pump of each forward or motor and sub-pump of reverse gear or motor with separate just falling of the displacement size that can control entire pump or motor and direction of the traffic.
9. according to claim 1 can deciliter gear pump or motor, comprise at least 1 such pump and at least 1 such motor, constitute hydrostatic separable speed changer, it is characterized in that, the oil outlet of each pump is through control valve or without control valve and receive on the oil inlet hole of each motor, the oil outlet of each motor is through control valve or without control valve and receive on the oil inlet hole of each pump, the algebraic sum of the revolution discharge capacity that total revolution discharge capacity of pump or motor is its each sub-pump or sub-motor, thereby control is some pump and/or the joint of motor and/or the velocity ratio of the speed changer of total revolution discharge capacity change from the pump input shaft to motor output shaft that separation has promptly changed pump and/or motor wherein, engage and/or separate some reverse gear pump and/or motor and change turning to of motor or change turning to of motor and promptly make speed changer be in reverse gear, separate all pumps and motor and then make speed changer be in neutral gear through steering control valve.
10. hydrostatic separable speed changer according to claim 9, it is characterized in that, certain gear shaft of the input shaft of its pump or pump also has the shaft extension of stretching out, be shaped on screw thread (APS) on the shaft extension end, suit has the spiral awl (AP1) of identical internal thread on it, other has the output shaft of motor of coaxial line or certain gear axial pump direction to stretch out to be fixed with friction taper sleeve (AM1) on the shaft extension, the Hand of spiral of spiral awl internal thread be the spiral awl relatively during its backward rotation then the spiral awl move axially to motor, when promoting to shift to down the friction taper sleeve that motor drive shaft has suitable inner conical surface on stretching with it gently in the shift fork induction force that transmits on the fork groove (AP11), spiral awl produces friction, the direction of this friction torque is to make spiral awl it is counter-rotational relatively, therefore make the spiral awl further be adjacent to friction taper sleeve, produce bigger friction positive pressure and friction torque, so the self-excitation process of positive feedback will be set up enough big friction torque rapidly and pump shaft be stretched with the motor shaft extension mechanically directly engages the direct high that constitutes speed changer, when the input shaft rotating speed that reduces pump by a small margin (subtracting throttle slightly as motor) promptly makes relative its of spiral awl relatively rotate in the same way and throwing off with friction taper sleeve in a flash away from friction taper sleeve.
11. according to claim 8 can deciliter gear pump or motor and the described hydrostatic separable speed changer of claim 10, it is characterized in that, make the middle output shaft of minimum that gear shaft (AOUT) of pump inner position as pump, through the position of the spiral of suit on it awl and the motor (M) of coaxial line by last and design the directly joint or separate of the friction taper sleeve that on input shaft (AMIN) in the middle of the motor identical, installs of just walking around with output shaft (AOUT) in the middle of the pump, make pump can mechanically directly engage and separate, constitute the direct high of speed changer with motor.
12. according to claim 5 or 6 can deciliter internal gear motor, it is characterized in that, motor is loaded on direct driving wheel in the hub for vehicle wheel with its inner gear housing, can obtain bigger driving torque greatly because of the internal gear diameter, thereby can save the wheel reductor of establishing in order to amplify torque that common wheel motor output shaft connects, about like this coaxial two driving wheels can deciliter internal gear motor advance, oil outlet respectively and connect, two motors are in parallel on oil circuit, be under the identical oil pressure and its flow sum equals total input flow rate of determining, therefore the flow that the resisting moment of big its wheel motor of turning medial resistance wheel is got more greatly during Vehicular turn reduce the to turn flow of outboard wheels motor is corresponding bigger, thereby the function that has differential mechanism automatically, when the motor oil circuit of coaxial both sides wheel is contacted, promptly the oil outlet of a side motor connects the oil inlet hole of opposite side motor, total oil inlet and outlet after the series connection is received pump, the flow that flows through of two motors must equate so, the rotating speed of two motors equates, this ransaxle promptly is in the chain state of differential, helps vehicle and climbs out of mire.
13. according to claim 1 can deciliter gear pump or motor, it is characterized in that, the unsteady axial lateral plate (M241) that can carry out the axial seal floating compensation also is housed in fixed lateral plate, constitutes the full compensation characteristic of pump or motor with movable radial seal piece.
14. according to claim 1 can deciliter gear pump or motor, it is characterized in that, also on the arc surface of radial seal piece and gear teeth tips contact seal, stick the thin layer of elastic material (as engineering nylon), stick the thin layer of one deck elastic material (as engineering nylon) by the one side of elements such as sealed gear and radial seal piece at side plate, feasible sealing is more flexible, further reduce leakage-gap and because of engineering nylon further reduces frictional loss to the steel friction factor is less, obtain better floating compensation effect.
15. hydrostatic separable speed changer according to claim 9, it is characterized in that, described motor installs to respectively on the driving wheel of ransaxle both sides, the flow that changes the both sides wheel motor turns to realization, then vehicle sharply turns to so that pivot stud when a side motor is just changeing opposite side and makes it to reverse by the reverse gear oil transportation, simply, can also make the wheel motor of turning medial separate and the wheel motor driving in the outside of turning, realize simply turning to by steering wheel control direction wheel.
16. according to claim 1 can deciliter gear pump or motor, it is characterized in that, when engaging this pump or motor, cut off its oil circuit with valve in addition and for example seal its oil outlet,, be also used as break because of the braking moment of the incompressible formation of liquid to the axle of pump or motor.
17. hydrostatic separable speed changer according to claim 9, it is characterized in that, also has particularly air sac type liquid gas energy storage device of hydraulic energy storage device, speed changer is used for system of vehicle transmission, can deciliter motor when vehicle needs retarding braking engage and the high pressure oil of its oil outlet output is imported accumulator through valve, thereby the kinetic energy of vehicle is converted to the potential energy in the accumulator in the time of will braking, when vehicle need start to walk to quicken, with the high pressure oil in the accumulator through valve derive to inject can deciliter motor oil inlet hole promote the starting of motor running powered vehicle and quicken, oil flowed out through valve from the motor oil outlet and flowed into oil sump this moment, can can be in separated state by deciliter gear pump this moment, motor can be in idling, when being driven into sufficiently high speed by accumulator, vehicle can engage with motor relay powered vehicle by a deciliter gear pump again, equally, accumulator also can disengage injection with high pressure oil through valve when engineering machinery is worked can promote or its work of boosting by deciliter motor, traction and propulsion capability when betterment works machinery is worked under wheel low-speed big operating mode, in order to make accumulator keep the frequent use of energy storage when adapting to engineering machinery work, can deciliter gear pump inject high pressure oil through valve to accumulator by engine-driving increases energy storage.
18. hydrostatic separable speed changer according to claim 10, it is characterized in that, also as the starting mechanism of starting under load oil-electric engine group, have only one can be contained on the internal combustion engine shaft by a deciliter gear pump, have only can being contained on the generator shaft by a deciliter gear motor that a revolution discharge capacity equates with pump, be provided with the direct coupling device that described spiral is bored and friction taper sleeve constitutes between two axles, when need starting apparatus combustion engine generator set, pump and motor are all placed separated state, the fully loaded electric load internal-combustion engine of generator belt is No Load Start then, engaging gradually then can deciliter pump and motor, make generator load receive internal-combustion engine flexibly, pump and motor engage to be finished generator speed separate pump and motor when normal and directly engages internal combustion engine shaft and generator shaft with spiral awl and friction taper sleeve simultaneously, internal-combustion engine directly drives generator and pump and motor are extremely low because of being in the separated state loss, helps that the light-load starting internal-combustion engine can make its power supply reach the frequency and the voltage of regulation rapidly by the gentle engagement generator again when power failure requires the emergency start generator set.
19. separable gear pump or motor, comprise the pitch wheel pair, the housing stationary axle is to sealing side plate and radial seal piece, it is characterized in that, also has slidably axial lateral plate (6000), liquid thickly is set in the housing (4000) and can endwisely slips in the manipulation lower edge of controlling rod (6003), when gear pair slides into the axial seal position that is completed into gear pair and radial seal piece, the oilhole (4001) that is opened on the housing is opened, pump efficiency should reach the maximum tooth wheel pump or motor is in jointing state, the back pressure interval (K) that liquid thickly surrounds between slip side plate (6000) and the housing (4000), the high pressure oil that high pressure oilhole (6001) on housing oilhole (4001) and slip side plate feeds enters the back pressure interval provides a back pressure to make the suffered both sides hydraulic coupling of slip side plate pressed toward gear side in a basic balance and slight form unsteady axial seal to the slip side plate, when controlling rod will be in the slip side plate of jointing state when drawing back away from the gear direction, axial clearance increasing pump efficiency should disappear between slip side plate and gear and the radial seal piece, slide the cylndrical surface (6002) of side plate simultaneously with housing oilhole (4001) complete closed, this moment, pump or motor promptly were in separated state.
20. according to above each claim is described can deciliter gear pump or motor, it is characterized in that, also have initially the stirring of axial screw awl of the forward and reverse joint of controlled operate pump of electromagnetic push device and motor and the motion that separates the required radial seal piece or the side plate that endwisely slips and described direct joint, separate pump and motor, make transmission system be easy to realize electrical autocontrol.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200810170115A CN101713399A (en) | 2008-10-04 | 2008-10-04 | Hydrostatic separable speed changer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200810170115A CN101713399A (en) | 2008-10-04 | 2008-10-04 | Hydrostatic separable speed changer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101713399A true CN101713399A (en) | 2010-05-26 |
Family
ID=42417304
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200810170115A Pending CN101713399A (en) | 2008-10-04 | 2008-10-04 | Hydrostatic separable speed changer |
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| Country | Link |
|---|---|
| CN (1) | CN101713399A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112833004A (en) * | 2021-01-19 | 2021-05-25 | 邵立坤 | Internal gear pump |
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|---|---|---|---|---|
| CN85100742A (en) * | 1985-04-01 | 1987-01-17 | 济南液压泵厂 | Radial floating gear pump, gear motor |
| CN87102829A (en) * | 1987-04-18 | 1988-11-02 | 程安强 | Floating shaft type gear pump, gear motor |
| CN1037019A (en) * | 1988-04-11 | 1989-11-08 | 李天宝 | Gear type variable rate pump or motor |
| CN1043366A (en) * | 1986-09-24 | 1990-06-27 | 郑悦 | Rotary positive displacement pumps or motors and their use |
| US5354188A (en) * | 1992-03-19 | 1994-10-11 | J. M. Voith Gmbh | Sickleless internal gear pump with radially movable sealing elements for radial compensation |
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2008
- 2008-10-04 CN CN200810170115A patent/CN101713399A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN85100742A (en) * | 1985-04-01 | 1987-01-17 | 济南液压泵厂 | Radial floating gear pump, gear motor |
| CN1043366A (en) * | 1986-09-24 | 1990-06-27 | 郑悦 | Rotary positive displacement pumps or motors and their use |
| CN87102829A (en) * | 1987-04-18 | 1988-11-02 | 程安强 | Floating shaft type gear pump, gear motor |
| CN1037019A (en) * | 1988-04-11 | 1989-11-08 | 李天宝 | Gear type variable rate pump or motor |
| US5354188A (en) * | 1992-03-19 | 1994-10-11 | J. M. Voith Gmbh | Sickleless internal gear pump with radially movable sealing elements for radial compensation |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112833004A (en) * | 2021-01-19 | 2021-05-25 | 邵立坤 | Internal gear pump |
| CN112833004B (en) * | 2021-01-19 | 2024-01-12 | 南通油顺液压机械有限公司 | Internal gear pump |
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Application publication date: 20100526 |