CN1077254A - Multi-action variable vane pump and motor - Google Patents
Multi-action variable vane pump and motor Download PDFInfo
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- CN1077254A CN1077254A CN 92102268 CN92102268A CN1077254A CN 1077254 A CN1077254 A CN 1077254A CN 92102268 CN92102268 CN 92102268 CN 92102268 A CN92102268 A CN 92102268A CN 1077254 A CN1077254 A CN 1077254A
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Abstract
The invention relates to an oil pump and an oil motor in the field of hydraulic transmission machinery, in particular to a double-acting and multi-acting variable vane pump and a motor. The stator ring is characterized in that a traditional stator ring is disassembled, each circular arc and curve of the inner wall of the stator ring are respectively composed of each block body, the blocks with short radius circular arcs and transition curves are placed in a pump shell inner cavity in a corresponding shape, the block bodies with long radius circular arcs are moved, the volumes of a pump and a motor are changed, and the purpose of variable quantity is achieved. The invention can be applied to wheel oil motors, hydraulic drive axles and hydraulic gearboxes of hydraulic transmission automobiles. The invention can be widely applied to all mechanical fields needing transmission and speed change.
Description
The present invention relates to the oil pump and the oil motor in hydraulic machinery field, is a kind of double-action and multi-function variable vane pump and motor.
Employed double-action or multiaction vane pump and motor in existing hydraulic machinery equipment all are quantitative.Can not limit the application area of this pump and motor and the working efficiency of hydraulic machinery by variable.The present invention has overthrown the wrong judgement that double-action or multiaction vane pump and motor can not variablees, filled up the blank that double-action and multiaction vane pump and motor can only quantitatively use, particularly the application area of double-action sliding-vane motor and multiaction sliding-vane motor is wider to make double-acting vane pump, economic value is bigger, and hydralic drive automobile is become a reality.
The basic principle of double-action and multi-function variable vane pump and motor is to develop from the basis of metering pump to form, its rotor, blade, oil distribution casing are basic identical, different is the stator disintegration fully of variable displacement pump and motor, circular arc on the stator circle inwall and transition curve combine and are positioned in the housing inner chamber of correspondingly-shaped by several blocks respectively, the block that fixedly has short radius circular arc and transition curve, move block with semi major axis circular arc or curve, change the volume of pump and motor, realize the purpose of variable.Variable displacement pump and motor have the folding of the block of semi major axis circular arc or curve and move dependence back pressure chamber, servo valve feedback oil cylinder, balance spring or connecting rod, crank, eccentric wheel and proportion electro-magnet.
Multi-function variable vane pump and motor are to develop to form on the basis of double-function variable vane pump and motor, and its basic structure and working principle are identical, narrate the structure and the working principle of double-function variable vane pump and motor below emphatically.
Fig. 1 double-function variable vane pump and motor schematic diagram
Fig. 2 double-action variable vane motor servo valve schematic diagram
Fig. 3 adds fourth shape blade schematic diagram
Fig. 4 four actuation variable sliding-vane motor schematic diagrams
During the size-constrained system of Fig. 5 warp-wise, double-action variable vane motor schematic diagram (structural drawing)
1, slide blocks 16, back pressure chamber
2, sliding seat 17, low pressure chamber
3, transition plate 18, primary blades
4, servo valve 19, pair blade
5, breach 20, rotor
6, housing 21, anchor shape piece
7, spool 22, pump case
8, valve pocket 23, Luo Shuankong
9, differential pressure cover 24, balance oil duct
10, balance spring 25, valve Xiao
11, month v notch v 26, spool hook for sleeping in
12, advance four oil holes 27, baffle plate
13, equal pressure passageway 28, draining road
14, high pressure oil input channel 29, adjusting oil duct
15, low pressure back oil road 30, oil input channel
4 circular arcs and 4 transition curves of stator inner wall divide other position to be: the circular arc of two segment length's radius Rs respectively by the right and left movably slide blocks (1) constitute, the circular arc of two sections short radius r is respectively by middle the convex formation of two sliding seats (2) up and down.Article 4, transition curve is made of 8 transition plates (3) respectively, except the circular arc of two segment length's radiuses can move do folding with both sides slide blocks (1), just maintains static after remaining circular arc and transition curve assembling finish.Transition plate is sleeved on the sliding seat, can adopt dovetail mount to connect, and sees figure (5), also can adopt Xiao Ding to connect, and sees figure (1), or directly and sliding seat make integral body (the small-power pump is made integral body) and form anchor shape piece, see figure (4).The transition curve of transition plate joins with short radius circular arc r respectively, intersects as figure (1) with the semi major axis circular arc R, and along with the folding of slide blocks is moved, its position of intersecting point also relatively moves, and narrates the structure and the principle of each parts of variable displacement pump below respectively.
One, slide blocks (1)
Two slide blockss (1) that have semi major axis circular arc and curved surface place pump case (6) lining to be positioned at the both sides of rotor, see figure (1), and its upper and lower end is adjacent to airfoil sliding seat (2) respectively, and can move left and right.The front of slide blocks (towards the one side of rotor) is a circular arc or curve, slide blocks last protuberance behind is close on the step of pump case inwall, slide blocks following protuberance behind is close to an end of lower slider seat, up and down protuberance directly with pump case composition back pressure chamber (16), the volume that is changing back pressure chamber is moved in the folding of slide blocks, the corner of protuberance has groove up and down, see figure (2), blade or Stamping Steel Ribbon are housed in the groove, in order to guarantee the sealing of back pressure chamber (16), the dress servo valve is pressed in following protuberance intermediate portion, and is drilled with into oil drain passage.Slide blocks front up and down most advanced and sophisticated position is milled with (5) 4 of the breach of position symmetry, sees figure (1), and the slide blocks on both sides has 8 breach, holds 8 transition plates respectively, in order to improve the performance of pump or motor, certain valve is housed also on the slide blocks, does not draw among the figure.When the warp-wise size was restricted, protuberance can remove under the slide blocks of variable displacement motor, saw figure (5), at this moment, static balance will appear in slide blocks, must reach partial equilibrium by the trench design of slide blocks upper and lower end face, to reduce the static friction and the kinetic friction of end face.
Two, sliding seat (2)
Sliding seat can be an airfoil, sees figure (1), also can be flat shape, and this example adopts wing-shaped structure, and the sliding seat bottom shape is relevant with the pump case volume, and irrelevant with pump performance, the middle upper portion of sliding seat is a convex, and the convex surface is a circular arc concave surface.This circular arc is the short radius circular arc on the conventional variable displacement pump stator, and the radius of circular arc is slightly larger than the radius of rotor, and and the rotor of this pump concentric, its arc length determines the number of blade on this pump rotor, and it is many more that the master of variable displacement pump pays blade, and this arc length is short more, blade is few more, and arc length is long more.Arc length is between the angle of two blades, and is suitable can satisfy being sealed into of high low pressure chamber, sees figure (3).If cooperate with the transition plate that has dovetail mount, sliding seat convex both sides should be milled with dovetail groove, see figure (5), if cooperate with the transition plate that has Xiao hole, sliding seat convex both sides respectively are milled with 2 breach, and Xiao is housed fixedly (at this moment, transition plate should be drilled with Xiao hole), see figure (1) (Xiao does not draw), under the airfoil sliding seat both sides wing of figure (1) the adjustment pad is housed, in order to adjust the gap of sliding seat and slide blocks rubbing surface, be beneficial to the tightness of back pressure chamber.
Three, transition plate (3)
The slip of the epitrochanterian blade of variable displacement pump from the semi major axis circular arc to the short radius circular arc will be through having the transition curve plate of certain curved surface, transition plate is sleeved on the sliding seat with Xiao Zi or dovetail mount, be movable assembling type, the wearing and tearing back is replaceable, short radius on a end on the transition plate curved surface and the adjacent sliding seat convex joins, semi major axis circular arc (or curve) on the other end of curved surface and the adjacent slide blocks intersects, its intersection point changes with moving of slide blocks, transition plate has been arranged, blade just can carry out the transition to the short radius circular arc smoothly from semi major axis circular arc (or curve), the shape of transition plate top-surface camber and length are determining the quality of blade sliding capability, impact when the curved surface of excellent in design can make vanes cross intersection point drops to bottom line, adopt the pressure of flow channel process balance blade root that blade is seamlessly transitted, effectively reduce the wearing and tearing of fillet surface.This point is even more important in four actuation variable motors, in fact in the constant flow paddle pump of routine, the wearing and tearing of its pumping cavity fillet surface are than the serious wear of oil suction chamber fillet surface, this phenomenon is just in time opposite with expert's theory, the cause of this chances are the vane pump pumping cavity is subjected to effect of hydraulic card clamping force, hydraulic card clamping force is pressed on the fillet surface of stator blade, the withdrawal of blade is subjected to serious obstruction, thereby be directed at the wearing and tearing of fillet surface and rotor cell wall, influence the life-span of vane pump, the present invention uses transition plate blade is maked somebody a mere figurehead in transition region, substantially avoided the hydraulic card clamping force of new and old blade, the present invention adopts up-to-date root of blade balance method simultaneously, the method can overcome the high speed centrifugation power of blade, inertial force and hydraulic card clamping force make blade reduce to zero at oil-feed district and laminated oil zone to the frictional force of transition curve.
Four, servo valve (4)
Several different methods has been moved in the folding of control slide blocks, and this specification is only stressed the structure and the principle of servo valve formula controlling method:
Servo valve is contained in slide blocks and descends behind in the circular hole of protuberance, its valve body compresses with sieve cover, spool is withstood by cluster spring, see figure (2), valve body is formed by stacking by a valve pocket (8) and two differential pressure covers (9), use as oil hydraulic motor, valve pocket (8) is a cylindrical body just, use as variable displacement pump, be milled with breach on valve pocket (8) inwall, and the breach on the spool (7) is shorter, the servo valve that is to say variable displacement pump and variable displacement motor can not be general, its difference only is the exchange of oil-feed breach (1) position, what variable displacement motor used in addition is stage clip (can be wall scroll stage clip or the cluster spring more than two), variable displacement pump can be used extension spring, also can use stage clip, if must join a spring overcoat with stage clip, this cover is fixed on the housing (6), and can regulate, spring is contained in the cover, one end of spool lengthening passes from cover and stage clip, and with card and spring abutment pressing spring, this structure is similar with being connected of motor porthole and valve spring, to move be opposite in the folding of slide blocks during the work of variable displacement pump and variable displacement motor, therefore requires the balance spring force direction of servo valve opposite, and it is extension spring that spring overcoat has played the transformation spring just.
The servo valve structural similarity of variable displacement pump and variable displacement motor, principle is opposite.This specification is only narrated the working principle of variable displacement motor servo valve among the figure (2):
High pressure oil is entered in the annular chamber in the differential sleeve through the oil inlet hole on the differential sleeve of the left side by high-pressure oil duct (14), because the annular chamber of the right differential sleeve (9) leads to low pressure chamber (leading to oil outlet), just have an annular pressure difference to act on the left end of spool (7) this moment, spool is moved right, compression balance spring (10), the spool appropriate location that moves right, (11 just communicate with the low pressure circular groove on the right two months v notch vs on the spool, and the fluid of back pressure chamber (16) lining is through all pressures intercommunicating pore (13) the oil inlet and oil return through hole (12) in the spool (7) at this moment, month v notch v (11), right annular chamber, low pressure back oil road (15), low pressure chamber (17) is until return tube.The fluid of back pressure chamber (16) is in case reduce, slide blocks (1) moves (moving right) outside rapidly under the positive pressure effect, slide blocks drive valve pocket (8) moves to right and reaches certain position, two months v notch vs on the spool (7) are covered, at this moment, back pressure chamber (16) is closed, slide blocks rests on the new position, the oil hydraulic motor load is heavy more, the pressure that is reflected in oil input channel (14) lining is high more, left side annular chamber gives the active force of spool (7) and stage clip (10) big more, and the position that slide blocks moves to right is also big more, and the driving torque of motor promptly improves fast with the increase of discharge capacity and pressure, otherwise load alleviates, oil pressure reduces, and spool (7) moves to left under the effect of balance spring, and pressure oil is through left annular chamber, spool moon v notch v (11), oil inlet and oil return road (12), all press oil duct (13) to enter back pressure chamber (16).At this moment, slide blocks (1) moves to left, and motor displacement reduces, and rotating speed improves.The action of variable displacement pump is opposite fully; Pressure raises, the back pressure chamber oil-feed, and slide blocks moves to left, and pump displacement reduces, and pressure reduces, the back pressure chamber oil return, slide blocks moves to right, and pump displacement strengthens.On the housing of pump and motor, all be equipped with and adjust sieve bolt (do not have among the figure and draw),, the folding of the slide blocks of the right and left is moved reach substantially synchronously, and can adjust pump and motor on a fixing characteristic curve in order to adjust the balance spring of servo valve.
Be the running principle of variable displacement motor under other operating mode below.
A, reversing
As oil hydraulic motor, be to need reversing mostly, figure can reverse as motor in (1), but reversing can not variable, and its principle is seen figure (2), during the motor reversing, former return opening becomes filler opening, and low pressure back oil road (15) changes the high pressure oil input channel into, the right annular chamber pressurized of servo valve, spool is moved to the left under hydraulic coupling and balance spring pressure, and the moon v notch v (11) on the spool is linked up with oil duct (14).At this moment, the fluid of back pressure chamber (16) all flows into back oil road under the positive pressure of slide blocks (1), slide blocks (1) is in the maximum position that moves to right, the motor displacement maximum, moment of torsion is also maximum, but rotating speed is the slowest, reversing does not require that the motor of speed change is suitable in many instances, the wheel motor of hydralic drive automobile particularly, hydraulic ransaxle or hydraulic gearbox are the most suitable, in reversing need be come to nothing the crane tool or ship deck machinery of (freewheel state), this type of motor also can be competent at, and requires the four effect oil motors that the machinery of speed change can use figure (4) in reversing.
B, slide
Need slide as the wheel oil hydraulic motor, can save a lot of fuel because slide.Oil motor shown in figure (1), figure (4), the figure (5) all can be accomplished this point, no matter advance to change or reversing, as long as slide blocks front pressurized reduces to a certain degree, being contained in slide blocks return spring (accompanying drawing does not draw) and balance spring behind has enough thrust to push slide blocks to rotor direction, make motor be in minimum displacement position, promptly be in the freewheel state substantially.
C, reversing speed change
The size and the position of appropriate change back pressure chamber (16), see figure (4), just can realize the reversing variable of oil hydraulic motor, but can produce the static pressure imbalance of slide blocks, aggravate the wearing and tearing of each rubbing surface, if on these rubbing surfaces, add needle bearing, certainly will increase the complexity of motor structure, and destroy the sealing of back pressure chamber, therefore except that multiaction low-speed big oil motor, the double-action motor had better not reverse variable, can adopt reversing gear (mechanical commutation) on fixed hydraulic equipment.
D, braking
As long as housing, rotor, blade, the rigidity of live axle, the Intensity Design of sliding-vane motor are reasonable, motor of the present invention can directly be used for braking fully, the method of oil inlet and oil return valve is closed in employing, automobile or machinery are shut down rapidly, no matter advance car or reversing, all close oil input channel or back oil road by the control valve that is contained on the motor during braking, the high pressure that the motor inner chamber forms will reach 2～3 times of maximum normal pressure, and motor can be in displacement automatically during braking.
Five, T-shaped blade (19)
Its epitrochanterian blade of vane pump or sliding-vane motor is many more, flow or moment of torsion are equal more, performance is good more, but blade is many, the intensity of rotor and blade itself has just become problem, as the sliding-vane motor that requires band brake to stop, this problem is especially outstanding, its way can only be bulged blading and reduce the sheet number, and raising material, because of the application of these three ways all is subjected to certain limitation, so the present invention takes to increase the way of paying blade, having increased its primary blades of pair blade in oil hydraulic motor can reduce, can reach like this and both thicken primary blades, do not weaken the purpose of rotor strength again, increased a pair blade, the short radius circular arc on the sliding seat can shorten, for multiaction sliding-vane motor particular importance, it is quite favourable to use flow groove balancing method for root of blade.The T-shaped blade inserts in the epitrochanterian groove, and its cross head is clipped in the groove circular hole, can only make a spot of warp-wise and move, and cross head is not fallen out groove when guaranteeing the blade high speed rotating.
Six, multiaction variable vane motor
Structural principle according to double-function variable vane pump and motor can directly be made multi-function variable vane pump and motor.What its practical value was bigger is the multiaction variable vane motor.Figure (4) is four actuation variable sliding-vane motor structure principle charts, use the main blade structure of paying, primary blades (18) plays sealing and produces torque, paying blade (19) only plays sealing and isolates the high low pressure chamber, transition plate (3) and short radius circular arc are made integral body becomes anchor shape piece (21), anchor shape piece embeds in the groove of housing (22), just maintain static, slide blocks (1) sipes direct and housing is formed back pressure chamber (16), sipes should have the certain depth ratio, otherwise slide blocks is stuck easily.4 servo valves (4) are contained in the inside of 4 slide blockss (1) respectively.Servo valve can be a rotary valve, also can be slide-valve, reaches synchronous adjustment by the connecting rod on the motor end cap, oil cylinder, spring mechanism.
The principle summary
Up to now, any hydraulic pressure books, the expert of any one hydraulic pressure circle, scholar are same conclusions: " double-acting vane pump and motor can not variable ".Announced a kind of patent application that is called " double-function variable vane pump " in the model utility on September 27th, 1989, its structure is to be combined by two single action variable vane pumps, can only be called duplex single action variable vane pump in fact.The present invention is target with the hydralic drive automobile, with the double-action variable vane motor is starting point, at first the stator of traditional quantitative sliding-vane motor of double-action is disintegrated, the inner curve of stator is resolved into several blocks, fix its short radius circular arc and transition curve, move its semi major axis circular arc to reach the purpose of variable, this is one of major character of the present invention.With the block of semi major axis circular arc or curve, must set up back pressure chamber, this is two of a feature.Outer active force or interior active force make the block of two semi major axis circular arcs move do folding, and this is three of a feature.Concrete theory analysis is as follows:
One, the decomposition of stator circle:
4 transition curves of double-action variable pump stator circle inwall can resolve into 4 blocks at least: be respectively 2 of the blocks of semi major axis circular arc, the short radius circular arc comprises 2 of the blocks of transition curve.If the block of transition curve is separated from short radius circular arc block again, then the block sum has increased by 4 again, is total up to 8.If every transition curve is served as by two transition plates respectively, then 4 transition curves are served as by 8 transition plates, the block that this moment, double-acting vane pump stator circle was divided into has 12, figure (1), figure (5) are this kind structures, figure (4) is four actuation variable sliding-vane motor structural drawing, and in this structure, the block of short radius circular arc and 4 transition plates are made integral body, help processing, assembling, and simplified construction.What of block variable displacement pump stator circle resolve into, and are relevant with processing technology, irrelevant with the parameter of pump.
Two, the form of back pressure chamber
A, by the behind excrescence of slide blocks directly and the inner walls of pump form back pressure chamber, this kind method is simple in structure, easy to manufacture, the back pressure chamber hydraulic coupling acts directly on the slide blocks, back pressure chamber can be an open type, also can be enclosed, uses the back pressure chamber of open type, the slide blocks front is basic identical with the mean value of the active force area at the back side, and back pressure chamber has damping hole to be communicated with the positive pressure chamber.This structure back pressure chamber does not require sealing.Use the enclosed back pressure chamber and require high-seal, servo valve or other control valve are only passed through in the turnover of back pressure chamber fluid, and the back pressure area is more a lot of greatly than malleation area.
B, according to the size of variable displacement pump rotor axial and warp-wise dimension scale, use circle or square piston and pump case and form back pressure chamber, the pressure of piston acts on earlier on the holder iron, pass to slide blocks by holder iron again, bear the static pressure imbalance by holder iron and piston, holder iron and piston can be made integral body, also can separate, this structure can be made the double-action oil motor of bidirectional variable, and its shortcoming is that the warp-wise size is bigger, and overall weight and volume are all bigger.
Three, control mode
Double-action and multi-function variable vane pump and motor rely on the folding of slide blocks to move, and reach the purpose of variable, and the active force that the slide blocks folding is moved is from following several forms:
A, armstrong's patent controlling type
In this kind mode, the active force of hand promotes slide blocks by connecting rod, lever, oily arm or eccentric wheel and moves do folding, and the folding of slide blocks is moved has synchronous effect.
B, automatic oil cylinder, mechanically controlled type
This mode is equipped with balance spring by single oil cylinder, and by lever, crank arm or eccentric wheel promotes each slide blocks and moves do folding, the pressure of system averages out by oil cylinder and spring, and the folding of each slide blocks is moved has synchronous effect.
C, pressure spring controlling type
The positive stress surface product moment with the back side of slide blocks is determining pressure difference, the compression degree of this pressure difference and balance spring, determining the folding position of slide blocks, just determining the discharge capacity of pump or motor, the back pressure lifting surface area of slide blocks and malleation lifting surface area are made certain difference, add the adjusting of balance spring can control pump and motor on specific power curve, the method is the simplest, but limited by the strictness of speed range, be applicable to the motor of constant rotational speed supporting, the centrifugal force difference of blade is very big during because of high and low rotating speed, area difference is fixed, and the elastic force of cluster spring is also fixed, and powerful centrifugal force will produce extra thrust to slide blocks, make pump and motor depart from original power curve, cause out of control.
D, servo valve controlling type
The control mode of servo valve has two kinds, first kind is outer active force controlling type, adopt multiple modes such as manual, centrifugal, vacuum, proportion electro-magnet, feedback oil cylinder to control moving of servo valve, moving of each valve of this kind mode reaches synchronously easily, and second kind is interior active force controlling type, adopts the pressure of pump or motor self, the pressure difference that on servo valve, causes, the drive servo valve moves, and can reach the same moved further of slide blocks substantially by the adjustment spring, sees figure (2).Servo valve can be contained on the slide blocks, also can be contained on the housing, and the seal request of using servo valve, back pressure chamber is strict, otherwise can cause interior leakage, reduces volumetric efficiency.Use servo valve, the influence that the powerful centrifugal force that blade is produced when pump and motor high speed rotating moves for the folding of slide blocks is very little; Enough big back pressure will make pump variable free characteristic stable.
Same with the single action variable vane pump, the characteristic curve of double-action and multi-function variable vane pump and motor still can be designed to various control forms such as pressure control, flow control, power control, rotating speed control as requested.Originally the equipment of application single action variable pump and double-action metering pump, machinery, vehicle etc. all can be replaced by double-function variable vane pump.The birth of double-action and multiaction variable vane motor makes hydralic drive automobile become a reality far and away.Because the slewing range and the low speed torque of this motor are all bigger, and it is simple in structure durable, easy to manufacture, therefore, its application area is very extensive, on the hydraulic transmission vehicle, both can be used as the all-wheel powered wheel motor, also but duplex is formed hydraulic ransaxle, or forms hydraulic gearbox with variable displacement pump, can be directly on Light-duty Vehicle or motorcycle and quantitative vane pump, gear pump, plunger pump is supporting, the application of the present invention on automobile can be cancelled original clutch case, gearbox, transmission shaft and ransaxle, and original whole braking system, even traditional steering equipment also can cancel, and makes the structure of vehicle become simple, durable, safe and reliable.The present invention can be widely used in each mechanical field that all need transmission and speed change simultaneously.
Claims (5)
1, a kind of double-action and multi-function variable vane pump and motor, it is characterized in that circular arc and transition curve on pump and the motor stator circle inwall combine and are positioned in the housing inner chamber of correspondingly-shaped by several blocks respectively, the block that fixedly has short radius circular arc and transition curve moves the block with semi major axis circular arc or curve.
2, according to claim (1), it is characterized in that: pump and motor have the folding of the block of semi major axis circular arc or curve and move dependence back pressure chamber, servo valve feedback oil cylinder, balance spring or connecting rod, crank, eccentric wheel and proportion electro-magnet.
3, according to claim (1) and claim (2), it is characterized in that: pump and motor have the block behind of semi major axis circular arc or curve or the behind protuberance is direct and inner walls is formed chamber behind.
4, according to claim (1) and claim (2), it is characterized in that: pump and motor have semi major axis circular arc or curve block back pressure chamber or form by square piston or circular piston and housing.
5, according to claim (1), it is characterized in that: T-shaped is housed on the rotor of pump and motor pays blade.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 92102268 CN1036088C (en) | 1992-04-07 | 1992-04-07 | Multi-action variable vane pump and motor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 92102268 CN1036088C (en) | 1992-04-07 | 1992-04-07 | Multi-action variable vane pump and motor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1077254A true CN1077254A (en) | 1993-10-13 |
| CN1036088C CN1036088C (en) | 1997-10-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 92102268 Expired - Fee Related CN1036088C (en) | 1992-04-07 | 1992-04-07 | Multi-action variable vane pump and motor |
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| Country | Link |
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| CN (1) | CN1036088C (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN1067746C (en) * | 1995-11-21 | 2001-06-27 | 华中理工大学 | Non-round internal engaged gear turning multi-purpose pump |
| WO2010124541A1 (en) * | 2009-04-28 | 2010-11-04 | Wu Zhenfang | High-speed large-torque hydraulic blade motor |
| CN104791246A (en) * | 2015-04-06 | 2015-07-22 | 山东交通学院 | Pinion-and-rack double-acting blade type secondary assembly |
| CN105386970A (en) * | 2015-10-21 | 2016-03-09 | 何家密 | Seal for fit of inlet and outlet in two sides of displacement blade pump, blades and pump interior |
| CN107237748A (en) * | 2016-03-28 | 2017-10-10 | 株式会社捷太格特 | Vane pump |
| CN108361192A (en) * | 2017-01-26 | 2018-08-03 | 大众汽车有限公司 | Vane pump |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| ITTO20040530A1 (en) * | 2004-07-30 | 2004-10-30 | Vhit Spa | DEVICE FOR THE DEACTIVATION OF A APPLIANCE IN THE PERIODS IN WHICH ITS FUNCTION IS NOT NECESSARY |
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1992
- 1992-04-07 CN CN 92102268 patent/CN1036088C/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1067746C (en) * | 1995-11-21 | 2001-06-27 | 华中理工大学 | Non-round internal engaged gear turning multi-purpose pump |
| WO2010124541A1 (en) * | 2009-04-28 | 2010-11-04 | Wu Zhenfang | High-speed large-torque hydraulic blade motor |
| CN104791246A (en) * | 2015-04-06 | 2015-07-22 | 山东交通学院 | Pinion-and-rack double-acting blade type secondary assembly |
| CN105386970A (en) * | 2015-10-21 | 2016-03-09 | 何家密 | Seal for fit of inlet and outlet in two sides of displacement blade pump, blades and pump interior |
| CN107237748A (en) * | 2016-03-28 | 2017-10-10 | 株式会社捷太格特 | Vane pump |
| CN107237748B (en) * | 2016-03-28 | 2020-10-20 | 株式会社捷太格特 | Vane pump |
| CN108361192A (en) * | 2017-01-26 | 2018-08-03 | 大众汽车有限公司 | Vane pump |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1036088C (en) | 1997-10-08 |
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| C15 | Extension of patent right duration from 15 to 20 years for appl. with date before 31.12.1992 and still valid on 11.12.2001 (patent law change 1993) | ||
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| CF01 | Termination of patent right due to non-payment of annual fee |