WO2018014472A1 - 二维锥滚轮活塞泵 - Google Patents

二维锥滚轮活塞泵 Download PDF

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Publication number
WO2018014472A1
WO2018014472A1 PCT/CN2016/105811 CN2016105811W WO2018014472A1 WO 2018014472 A1 WO2018014472 A1 WO 2018014472A1 CN 2016105811 W CN2016105811 W CN 2016105811W WO 2018014472 A1 WO2018014472 A1 WO 2018014472A1
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WIPO (PCT)
Prior art keywords
piston
pump
cylinder
chamber
axial
Prior art date
Application number
PCT/CN2016/105811
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English (en)
French (fr)
Inventor
阮健
金丁灿
申屠胜男
李胜
童成伟
孟彬
Original Assignee
浙江工业大学
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Publication of WO2018014472A1 publication Critical patent/WO2018014472A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18—Lubricating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/08—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion
    • F16H25/12—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion with reciprocation along the axis of rotation, e.g. gearings with helical grooves and automatic reversal or cams

Definitions

  • the invention relates to a two-dimensional cone roller piston pump, belonging to a hydraulic pump and a hydraulic motor in the field of fluid transmission and control.
  • the plunger (piston) pump uses a plunger (piston) and a cylinder block as main working members.
  • the plunger (piston) reciprocates in the plunger (piston) hole of the cylinder block, the volume of the closed working volume chamber composed of the plunger (piston) and the cylinder body changes, and the suction and discharge processes are completed.
  • the plunger (piston) pump is divided into two types, radial and axial.
  • the conventional common axial piston (piston) pump relies on a plunger (piston) to reciprocate in the cylinder to change the volume of the sealing working chamber to achieve suction and pressure oil.
  • a plunger piston
  • the distribution plate and the plunger (piston) The wear of the parts directly affects the service life and durability of the pump.
  • the drive shaft rotates once, each plunger (piston) can only achieve one oil absorption and one oil discharge, and its displacement is limited and needs to be independent.
  • the distribution mechanism is designed to complete the switching of the suction and discharge of the working chamber.
  • the lubrication system of the existing plunger pump is in communication with the infusion system, and the liquid to be delivered is used as a lubricant.
  • This structure is only suitable for conveying oil and is not suitable for use in an aqueous medium environment.
  • Water is the most commonly used liquid substance in human production and life. Therefore, the development of water-related machinery, especially as a water pump for water transfer and energy conversion, has always been the focus of attention and research hotspot.
  • the principle and structure of the pump are mainly divided into blade (centrifugal) type and volumetric type. Compared with the former, the volumetric water pump has the advantages of high efficiency, high power density and easy realization of high pressure. It is an important development direction of the pump technology. Piston pumps that implement pump functions are more practical.
  • the present invention provides a two-dimensional cone roller piston pump.
  • the two-dimensional cone roller piston pump comprises a pump body, the pump body has a liquid suction hole and a liquid discharge hole, the pump body is provided with a pump unit, and the pump unit is connected with the motor.
  • the pump unit comprises a cylinder fixed in the pump body, the piston body is provided with a piston, the central axis of the cylinder body coincides with the central axis of the piston, and both ends of the piston are provided with axial displacement of the driving piston to cause the volume of the working chamber to be degenerated.
  • Triggering device, and the triggering device at both ends of the piston drives the piston to move in the opposite direction;
  • the working chamber includes a left chamber and a right chamber respectively at the two ends of the cylinder, and a shoulder is arranged in the middle of the piston, and the left end surface of the shoulder and the left side rail surround the cylinder chamber into a closed left chamber.
  • the right end face and the right side rail of the shoulder surround the cylinder cavity into a closed right chamber;
  • the shoulder is provided with two axisymmetric left axial grooves and two axisymmetric right axial grooves, and left
  • the axial groove and the right axial groove are alternately arranged on the circumference of the cross section of the piston;
  • the left axial groove communicates with the left chamber, the right axial groove communicates with the right chamber;
  • the cylinder body is provided with two axis symmetry a left window and two axisymmetric right windows, a left window communicating with the drain hole and a right window communicating with the liquid suction hole on the cross section of the cylinder along the circumference of the cylinder Alternate spacing;
  • Axisymmetric means symmetrical with respect to the central axis of the piston; axial means the direction in which the central axis of the piston is located, and radial means the direction in which the diameter of the cross section of the piston is located;
  • the triggering device comprises a guide rail and a roller
  • the guide rail is fixed at an end of the cylinder body
  • the piston penetrates the guide rail
  • the end of the piston is provided with a suspension
  • the suspension is connected with a pair of axisymmetric rollers
  • the guide rail is axially annular
  • the curved surface has an axial undulation, and the projection of the guide rail in the direction of the central axis is annular, and the curved surface has two highest points and two lowest points, and the highest point and the lowest point are respectively located
  • the two perpendiculars of the ring are perpendicular to each other, and the curved surface is symmetric according to the two diameters; the roller rolls on the guide rail to push the piston to move in the axial direction;
  • the undulating waveforms of the guide rails at the ends of the piston are opposite to each other;
  • the waveform of the curved surface of the guide rail has the following correspondence with the positions of the left axial groove and the right axial groove, the left window and the right window: the first stage guide rail and the roller drive piston move to the left, and the left axial groove is aligned to the left window, left
  • the chamber excludes the liquid, while the right axial groove is aligned with the right window, the right chamber draws in liquid; the second stage guide and the roller drive piston move to the right, the left axial groove is aligned with the right window, and the left chamber draws liquid while the right
  • the axial groove is aligned with the left window, and the right chamber discharges the liquid;
  • the inner ring side of the guide rail is higher than the outer ring side;
  • the roller is a tapered roller, and the rolling surface of the tapered roller is matched with the guide rail;
  • a suspension of one of the triggering devices at both ends of the piston is coaxially connected to a motor output shaft penetrating into the pump body;
  • the end cover and the guide rail of the pump body surround the pump body cavity into a closed lubrication cavity, and the lubrication cavity is communicated through a lubrication passage opened on the pump body, and a lubricating oil port is arranged on the lubrication passage.
  • left and right windows are located at different positions on the central axis.
  • a fork is connected to the output shaft of the motor, and a dial is fixed to the end of the suspension, and a force groove is formed on the dial, and the fork is disposed in the force receiving groove; the two sides of the fork are provided with radial
  • the fixing column has a bearing on the fixing sleeve, and the fork pushes the dial through the bearing.
  • the cone roller comprises a conical wheel sleeve
  • the conical wheel sleeve comprises a barrel portion and a cone portion
  • the conical wheel sleeve is sleeved on the pin shaft
  • the pin shaft is radially disposed on the suspension body
  • Ball bearings are arranged between the cone and the pin shaft
  • the ball bearing and the needle bearing are sleeved on the pin and threaded between the needle bearing and the pin
  • the sleeve and the needle bearing are locked in the conical sleeve
  • a first wire retaining ring is arranged between the thread sleeve and the pin shaft
  • a second wire retaining ring is arranged between the thread sleeve and the cone portion.
  • the guide rail is provided with a radial mounting hole, and the left pin penetrates into the pump body, the cylinder body and the radial mounting hole on the left side rail, and the cylinder body and the left side rail are fixed on the pump body, and the right pin penetrates into the cylinder.
  • the radial mounting holes on the body and the right side rails fix the right side rails to the cylinder block; the rails are provided with axial mounting holes that cooperate with the pistons.
  • suspension is sleeved at the end of the piston and is radially fixed to the piston by a cylindrical pin.
  • the two left windows are communicated by a first annular groove on the cylinder, and the two right windows are communicated by a second annular groove on the cylinder.
  • the invention adopts a trigger device matched with a guide roller and a cone roller to push the piston to perform axial movement and circumferential rotation, and the axial movement of the piston drives the volume of the working chamber to be degenerated, and the axial movement and the circumferential rotation of the piston realize the distribution, that is, Dispensing the working chamber to aspirate or drain, eliminating the need for a separate dispensing mechanism.
  • the guide rail and the cone roller are in line contact, which increases the area of rolling contact, reduces the contact stress, effectively avoids slipping, and prolongs the service life of the contact components.
  • the lubrication chamber is sealed from the working chamber to achieve oil-water separation. It can be applied to oil medium and water medium, which expands the scope of use.
  • the suspension is suspended at both ends of the piston and has a degree of freedom of rotation with respect to the pin shaft, and the cone roller on both sides of the pin shaft can be automatically centered and fine-tuned.
  • the plunger (piston) pump can only perform one suction and discharge, and the invention can be miniaturized under the premise of ensuring the same flow rate, and the cost is greatly reduced.
  • the conventional piston pump has a piston-cylinder friction pair and a distribution friction pair.
  • the present invention has only a piston-cylinder friction pair, which improves work efficiency.
  • the two unit pumps can be connected in series to substantially eliminate flow pulsation.
  • the unit pump can be designed to realize unitized insertion and assembly. It can be realized by electronic control after being designed and inserted according to binary flow. Digital pump design.
  • Figure 1 is a schematic view of the structure of the present invention.
  • Figure 2 is a schematic view of the structure of the unit pump.
  • Figure 3 is a schematic view of the structure of the piston.
  • Figure 4 is a cross-sectional view taken along line A-A of Figure 3;
  • Figure 5 is a schematic view of the structure of the cylinder block.
  • Figure 6 is a cross-sectional view taken along line A-A of Figure 5;
  • Figure 7 is a cross-sectional view taken along line B-B of Figure 5;
  • Figure 8 is a schematic view showing the structure of the guide rail on the left side.
  • Figure 9 is a cross-sectional view taken along line A-A of Figure 8.
  • Figure 10 is a schematic view showing the structure of the guide rail on the right side.
  • Figure 11 is a cross-sectional view taken along line A-A of Figure 10;
  • Figure 12 is a schematic view of the assembly of the suspension, the cone roller and the dial on the left side.
  • Figure 13 is a schematic view showing the assembly structure of the suspension and the cone roller on the right side.
  • Figure 14 is a schematic exploded view of the suspension structure of the suspension, the cone roller and the dial on the left side.
  • Figure 15 is a schematic exploded view of the suspension structure of the suspension and cone rollers on the right side.
  • Figure 16 is a schematic exploded view of the motor output shaft and fork assembly structure.
  • Figure 17 is a schematic view showing the structure of the unit pump when the piston is at 0°.
  • Figure 18 is a cross-sectional view taken along line A-A of Figure 17;
  • Figure 19 is a cross-sectional view taken along line B-B of Figure 17;
  • Figure 20 shows the piston rotated counterclockwise to At the time, the unit pump structure is schematic.
  • Figure 21 is a cross-sectional view taken along line A-A of Figure 20;
  • Figure 22 is a cross-sectional view taken along line B-B of Figure 20;
  • Figure 23 shows the piston rotated counterclockwise to At the time, the unit pump structure is schematic.
  • Figure 24 is a cross-sectional view taken along line A-A of Figure 23;
  • Figure 25 is a cross-sectional view taken along line B-B of Figure 23;
  • Figure 26 shows the piston rotated counterclockwise to At the time, the unit pump structure is schematic.
  • Figure 27 is a cross-sectional view taken along line A-A of Figure 26;
  • Figure 28 is a cross-sectional view taken along line B-B of Figure 26;
  • Figure 29 is a schematic view showing the structure of the unit pump when the piston is rotated counterclockwise to ⁇ .
  • Figure 30 is a cross-sectional view taken along line A-A of Figure 29;
  • Figure 31 is a cross-sectional view taken along line B-B of Figure 29;
  • Figure 32 is a graph showing the relationship between the displacement, velocity, acceleration of the roller on the guide rail and the angle of rotation of the piston.
  • a two-dimensional cone roller piston pump includes a pump body 1.
  • the pump body 1 is provided with a liquid suction hole and a liquid discharge hole.
  • the pump body 1 is provided with a pump unit, and the pump unit is connected to the motor.
  • the pump unit comprises a cylinder 2 fixed in the pump body 1.
  • the cylinder 2 is provided with a piston 3, the central axis of the cylinder 2 coincides with the central axis of the piston 3, and both ends of the piston 3 are provided with a driving piston 3 axial direction.
  • a triggering device that moves to cause the volume of the working chamber to degenerate, and the triggering device at both ends of the piston 3 drives the piston 3 to move in the opposite direction;
  • the working chamber includes a left chamber and a right chamber respectively at the two ends of the cylinder, and a shoulder 31 is provided in the middle of the piston 3, the shoulder The left end surface of the 31 and the left side rail 4 enclose the inner cavity of the cylinder 2 into a closed left chamber, and the right end surface of the shoulder 31 and the right side rail 5 enclose the inner cavity of the cylinder 2 into a closed right chamber.
  • a shoulder 31 is provided with two axisymmetric left axial grooves e, h and two axisymmetric right axial grooves f, g, and left axial grooves e, h and right axial grooves f, g Arranged at equal intervals on the circumference of the cross section of the piston 3; the left axial grooves e, h are in communication with the left chamber, the right axial grooves f, g are in communication with the right chamber; and the cylinder 2 is provided with two axis symmetry Left window a, c and two axisymmetric right windows b, d, left windows a, c communicating with the drain holes and right windows b, d communicating with the liquid suction holes in the cylinder
  • the projections on the cross section of 2 are alternately distributed along the circumference of the cylinder 2 at equal intervals;
  • the axisymmetric means that the central axis of the piston 3 is symmetrical; the axial direction refers to the direction in which the central axis of the piston 3 is located, and the radial direction refers to the direction in which the diameter of the cross section of the piston 3 is located;
  • the triggering device comprises guide rails 4, 5 and rollers 9, 7, the rails 4, 5 are fixed at the end of the cylinder block 2, the piston 3 penetrates the guide rails 4, 5, and the ends of the piston 3 are provided with suspensions 8, 6, A pair of axisymmetric rollers 9, 7 are connected to the suspensions 8, 6; the guide rails 4, 5 are axial annular curved surfaces 41, 51, and the curved surfaces 41, 51 have axial undulations, the guide rails 4, 5;
  • the projection in the direction of the central axis has an annular shape, and the curved surface has two highest points and two lowest points, and the highest point and the lowest point are respectively located on two mutually perpendicular diameters of the ring, The curved surfaces are respectively symmetrical according to the two diameters; the rollers 9, 7 roll on the guide rails to push the piston 3 to move in the axial direction;
  • the waveforms of the curved surfaces 41, 51 of the guide rails 4, 5 and the positions of the left axial grooves e, h and the right axial grooves f, g, the left window a, c and the right windows b, d have the following correspondences: the first stage guide 4, 5 and the rollers 9, 7 drive the piston 3 to the left, the left axial slots e, h are aligned with the left windows a, c, the left chamber excludes the liquid, while the right axial slots f, g are aligned with the right window b, d, the right chamber draws in liquid; the second stage guides 4, 5 and the rollers 9, 7 drive the piston 3 to the right, the left axial slots e, h are aligned with the right window b, d, the left chamber draws in liquid, while right The axial grooves f, g are aligned with the left windows a, c, and the right chamber discharges the liquid;
  • the inner ring side of the guide rails 4, 5 is higher than the outer ring side;
  • the rollers 9, 7 are tapered rollers, and the rolling surfaces of the tapered rollers are matched with the guide rails 4, 5;
  • the suspension 8 of one of the triggering devices at both ends of the piston 3 is coaxially connected to the motor output shaft 20 penetrating into the pump body 1; in this embodiment, the suspension 8 on the left side is connected to the motor output shaft 20.
  • the end caps 12, 30 of the pump body 1 and the guide rails 4, 5 surround the inner cavity of the pump body 1 into a closed lubrication chamber, and the lubrication chamber communicates through a lubrication passage opened on the pump body 1, and lubricating oil is provided on the lubrication passage. mouth.
  • the left windows a, c and the right windows b, d are located at different positions of the central axis.
  • the left windows a, c are located on the left side of the cylinder
  • the right windows b, d are located on the right side of the cylinder 2.
  • a shifting fork 18 is connected to the output shaft 20 of the motor, and a dial 81 is fixed to the end of the suspension 8.
  • the force receiving slot 811 is defined on the dial 81.
  • the shifting fork 18 is disposed in the force receiving slot 811; Radial fixing columns are arranged on both sides, and the fixing sleeve on the fixing column is provided with a bearing 82, and the fork 18 pushes the dial 81 through the bearing 82.
  • the cone rollers 9, 7 comprise conical sleeves 91, 71, the conical sleeves 91, 71 comprising a barrel portion and a cone portion, the conical sleeves 91, 71 being sleeved on the pins 16, 17 and the pin 16 17 is radially disposed on the suspensions 8, 6 with thrust bearings 92, 72 between the barrel portion and the pins 16, 17, and a needle bearing 93 is provided between the cone portion and the pins 16, 17.
  • the thrust bearings 92, 72 and the needle bearings 93, 73 are sleeved on the pins 16, 17, and through the threaded sleeve 95 which is inserted between the needle bearings 93, 73 and the pins 16, 17 75 is locked in the conical sleeves 91, 71, between the threaded sleeves 95, 75 and the pins 16, 17 are provided with first wire retaining rings 96, 76, between the threaded sleeves 95, 75 and the cone portion
  • the second wire retaining rings 94, 74 function to define the needle bearing, the thrust bearings 92, 72 bear the axial forces of the tapered wheel sleeves 91, 71, and the needle bearings 93, 73 bear the tapered wheel sleeves 91, 71. Radial force, as shown in Figure 12, Figure 13.
  • the guide rails 4, 5 are provided with radial mounting holes 42, 52, and the left pin 13 penetrates into the radial mounting holes 42 of the pump body 1, the cylinder block 2 and the left side rail 4, and fixes the cylinder block 2 and the left side guide rail 4
  • the right pin 14 penetrates into the radial mounting holes on the cylinder block 2 and the right side rail 5, and the right side rail 5 is fixed to the cylinder block 2; the guide rails 4, 5 are also provided with the piston 3 Fitted axial mounting holes.
  • the suspensions 8, 6 are sleeved at the ends of the piston 3 and are radially fixed to the piston 3 by cylindrical pins 97, 77.
  • the two left windows a, c are communicated by the first annular groove 21 on the cylinder 2, and the two right windows b, d are communicated through the second annular groove 22 on the cylinder 2 to concentrate the oil to facilitate the oil in the pump Convergence in the body.
  • the left end of the pump body 1 is fixedly mounted with an end cover 12 by a bolt 11, and a second grid ring 27 for sealing and a depth for supporting the motor output shaft 20 are mounted between the left end cover 12 and the motor output shaft 20.
  • the ball bearing 28 is mounted, and the motor output shaft 20 is fixed to the left end cover 12 by a snap spring 29.
  • the shift fork 18 is fixed to one end of the motor output shaft through a pin 19, a spring washer 84 and a fourth wire retaining ring 85, and the other end of the motor output shaft 20 is connected to the motor through a coupling.
  • the bearing 82 is sleeved on the fixed posts on both sides of the shift fork 18 and is fixed by the third wire retaining ring 81.
  • the bearing 82 is a deep groove ball bearing and is provided with a bearing sleeve 83.
  • the cylinder block 2 is provided with second mounting holes 43, 53 corresponding to the radial mounting holes 42, 52; the guide rails 4, 5 are provided with grooves for fitting the O-rings 21, 24 with the cylinder block 2.
  • the grooves 44, 54 and the guide rails 4, 5 are also provided with grooves 44, 55 which cooperate with the piston 3 for mounting the first lattice rings 23, 26.
  • the rails 4, 5 are alternately provided with two highest points m and two axis-symmetric lowest points n.
  • the cone rollers 9, 7 are moved from the lowest point n to the adjacent highest point m, the cone rollers 9, 7 are squeezed.
  • the reaction forces of the guide rails 4, 5, the guide rails 4, 5 against the cone rollers 9, 7 synchronously drive the axial movement of the piston 3.
  • the guide rails 4, 5 will squeeze the cone rollers 9, 7, and the reaction forces of the cone rollers 9, 7 against the guide rails 4, 5 will synchronously drive the piston. 3 axial movement.
  • the area between the lowest point n and the highest point m adjacent to the guide rails 4, 5 constitutes a motion section, and the center angle corresponding to each motion section is In each movement interval, the piston 3 achieves one axial movement in one direction, and the direction of movement of the piston 3 in the adjacent movement interval is opposite. And since the shapes of the curved surfaces in each motion section are the same, the waveforms of the curved surfaces of the adjacent motion sections are inverted, so that the piston 3 moves to the left and moves to the right to have the same rate curve.
  • the shape of the guide rails 4, 5 is such that the piston satisfies the deceleration motion law such as equal acceleration, that is, in each movement section, in the first half of the interval, the piston 3 accelerates at the same acceleration, in the latter half of the interval.
  • the piston decelerates at the same deceleration, so that the piston 3 moves to the left and moves to the right with the same acceleration curve, and the sudden change in acceleration is small, so that the impact of the piston on the cylinder is small.
  • the guide rails 4, 5 have a hollow cylindrical shape, and the rolling surfaces of the tapered rollers 9, 7 are in conformity with the curved surfaces 41, 51 of the guide rails 4, 5, ensuring that the extension lines of the tapered contour lines of the two tapered rollers 9, 7 meet at a point. Then, the extension line of the bonding wires of the tapered rollers 9, 7 on the two sides of the suspensions 8, 6 and the guide rails 4, 5 and the central axis of the piston 3 are intersected at one point, so that the cone rollers on both sides of the suspensions 8 and 6 can be made. 9, the difference between the line speeds on the line of contact with the guide rails 4, 5 is the smallest, preventing slipping during rotation.
  • Two axially symmetric left axial grooves e, h and two axisymmetric right axial grooves f, g are alternately arranged on the surface of the shoulder 31, and the left axial grooves e, h are always in communication with the left chamber, right The axial grooves f, g are always in communication with the right chamber.
  • the left chamber becomes smaller, the right chamber becomes larger, and the guide shafts 4, 5 and the rollers 9, 7 drive the piston 3 to rotate circumferentially.
  • the left axial grooves e, h are aligned with the left windows a, c, and the left chamber is drained outward through the through left axial grooves e, h and the left windows a, c;
  • the right axial grooves f, g are Quasi-right window b, d, the left chamber draws in liquid through the right axial grooves f, g and the right windows b, d.
  • the left chamber becomes larger and the right chamber becomes smaller, while the guide rails 4, 5 and the rollers 9, 7 drive the piston 3 to rotate circumferentially.
  • the left axial grooves e, h are aligned with the right windows b, d, the left chamber is sucked inward through the through left axial grooves e, h and the right windows b, d; the right axial grooves f, g are Quasi-left window a, c
  • the left chamber is drained outward through the through right axial grooves f, g and the left windows a, c.
  • the cylinder block 2 and the guide rails 4, 5 are sealed by O-rings 21, 24, and the O-rings 21, 24 are also provided with retaining rings 22, 25 for preventing deformation of the O-rings 21, 24, and the piston 3 and the guide rails 4, 5 are sealed by the first grid rings 23, 26 to ensure the sealing of the left chamber and the right chamber.
  • the output shaft 20 of the motor and the end cover 12 are sealed by a second Glyme ring 27, and the lubrication chamber is separated from the working chamber, and the lubrication chamber can provide independent lubrication to the trigger device.
  • the oil in the lubrication chamber can be completely separated from the water in the working chamber, and does not pollute each other, thereby achieving oil-water separation.
  • the lubrication chamber replenishes the oil through the lubrication port.
  • the two ends of the piston 3 are flattened to form a plug having a flat surface, and a horizontal first radial hole 32 is formed in a plane formed after the flattening, and the left ends of the suspensions 8 and 6 are respectively provided with a plug.
  • the two sides of the sleeve are matched with the plane milled by the end of the piston 3, and there is a gap between the arc surface of the piston 3 not being milled; the suspensions 8 and 6 are opened with the first radial hole 32 through the second radial holes 82, 62, the plugs at the ends of the piston 3 are inserted into the sleeve holes of the suspensions 8, 6, respectively, and the cylindrical pins are inserted into the first radial holes 32 and the second radial holes 82, 62 To fix the suspensions 8, 6 to the piston 3, and because of the gap left between the end portions of the piston and the suspension sleeve holes, the suspensions 8, 6 have a slight swing around the cylindrical pins 97, 77.
  • the cone rollers 9, 7 are disposed on the pins 17, 16, and the axial directions of the pins 17, 16 are perpendicular to the axial directions of the cylindrical pins 97, 77, and the suspensions 8, 6 are swung by the cylindrical pins 97, 77, The centering balance fine adjustment of the cone rollers 9, 7 at both ends of the suspensions 8, 6 is performed so that the tapered rollers 9, 7 at both ends are in close contact with the guide rails 4, 5.
  • the piston rotates 360° for one working cycle.
  • the left and right windows a, b, c, d and the left and right axial slots e, f, g, h are all staggered from each other, and no communication is generated.
  • the cone roller 9 on the suspension 8 is located at the lowest point n on the guide rail 4, and the cone roller 7 on the right suspension 6 is located at the highest point m on the guide rail 5, defining that the cone rollers 9, 7 and the piston 3 are located at this time.
  • 0° as shown in Figures 17-19, the workflow of the present invention in one duty cycle (0 to 2 ⁇ ) is:
  • the left windows a, c and the left axial grooves e, h begin to recombine and penetrate, and at the same time, the right windows b, d and the right axial grooves g, f also begin to rejoin and penetrate; 3 rotate to When the left window a, c and the left axial groove e, h have a maximum penetration area, the through-area of the right window b, d and the right axial groove g, f also reaches a maximum, and the piston 3 reaches a neutral position, as shown in FIG. 21, 22.
  • the cone rollers 9, 7 move from 0° to During the whole process, the piston 3 moves to the left, the left axial grooves e, h and the left windows a, c respectively penetrate and form an ae channel, a ch channel, and the right axial grooves g, f and the right windows b, d respectively penetrate and The bg channel and the df channel are formed; the left chamber is drained to the pump body through the ais channel and the ch channel through the liquid discharge hole on the pump body 1, and the right chamber always passes through the bg channel and the df channel from the liquid suction hole on the pump body 1. Aspirate from the outside of the pump.
  • the invention realizes the first suction and discharge.
  • the right windows b, d and the left axial grooves e, h begin to merge and penetrate, and the left windows a, c and the right axial grooves g, f also begin to recombine.
  • the piston 3 is rotated
  • the through areas of the left window a, c and the right axial groove g, f are also the largest, and the piston 3 reaches the neutral position, as shown in Figs. 28 is shown.
  • the piston 3 moves to the right, and the right windows b, d and the left axial grooves e, h respectively penetrate and constitute the be channel, the dh channel, and the left windows a, c and the right axial grooves g, f respectively
  • the invention forms af channel and cg channel, and the left chamber absorbs liquid from the pump body through the be channel and the dh channel, and the right chamber discharges to the pump body through the af channel and the cg channel.
  • the present invention realizes the second suction and discharge.
  • the combination of the circumferential rotation and the circumferential movement of the piston 3 realizes the switching of the suction and discharge liquid chamber and the continuous suction and discharge liquid, and the independent distribution mechanism is omitted; and the circumferential rotation is performed, and the liquid absorption is realized four times. Drain four times.

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Abstract

二维锥滚轮活塞泵，包括泵体（1），泵体（1）上开有吸液孔和排液孔，泵体（1）内设有泵单元，且泵单元与电机相连，泵单元包括固定在泵体（1）内的缸体（2），缸体（2）内设有活塞（3），缸体（2）的中心轴与活塞（3）的中心轴重合，活塞（3）的两端均设有驱动活塞（3）轴向移动以引起工作腔室容积变化的触发装置，且活塞（3）两端的触发装置驱动活塞（3）运动的方向相反。该活塞泵的导轨（4，5）与锥滚轮（7，9）为线接触，增大了滚动接触的面积，降低了接触应力，有效避免打滑，延长了接触部件的使用寿命；且润滑腔与工作腔室密闭隔开，实现了油水分离，既可适用于油介质，又适用于水介质，扩大了使用范围。

Description

二维锥滚轮活塞泵 技术领域
本发明涉及一种二维锥滚轮活塞泵，属于流体传动及控制领域中的液压泵及液压马达。
背景技术
柱塞(活塞)泵用柱塞(活塞)和油缸体作为主要工作构件。当柱塞(活塞)在缸体的柱塞(活塞)孔中作往复运动时，由柱塞(活塞)与缸体组成的密闭工作容积腔发生容积变化，完成吸、排液过程。根据柱塞(活塞)在缸体中的不同排列形式，柱塞(活塞)泵分为径向式和轴向式两大类。
传统常见的轴向柱塞(活塞)泵依靠柱塞(活塞)在缸体内往复运动，使密封工作容腔容积发生变化来实现吸、压油。内部相对运动的零件多，对材料材质、加工精度要求高，对油液污染敏感，加工、使用、维护的要求和成本较高，价格昂贵；缸体随传动轴一起转动，转动惯量大，导致启动、停止、调速的响应速度慢，不利于通过调速来控制泵的输出流量；缸体内摩擦副较多，高速转动下，缸体温升较快，配流盘、柱塞(活塞)等零件的磨损直接影响泵的使用寿命和耐久性。除此之外，由于柱塞(活塞)泵本身工作原理的限制，传动轴转动一周，每个柱塞(活塞)只能实现一次吸油和一次排油，其排量受到了限制，且需要独立设计配流机构来完成工作容腔吸排油的切换。
现有的柱塞泵的润滑系统与输液系统连通，用所输送的液体作为润滑剂，这种结构只适合输送油，不适合用于水介质环境。
而水是人类生产与生活中最常用的液态物质，因而与水相关的机械，尤其是作为水转输与能量转换的水泵的发展一直是人们关注的焦点和研究的热点。水泵在原理与结构上主要分为叶片(离心)式与容积式，与前者相比，容积式水泵具有效率高、功率密度大和易实现高压的优点，是水泵技术的重要发展方向，因此，能实现水泵功能的活塞泵更加具有实用性。
发明内容
为了克服现有技术的上述缺陷，并实现水泵功能，本发明提供一种二维锥滚轮活塞泵。
本发明采用的技术方案是：
二维锥滚轮活塞泵，包括泵体，泵体上开有吸液孔和排液孔，泵体内设有泵单元，且泵单元与电机相连，
泵单元包括固定在泵体内的缸体，缸体内设有活塞，缸体的中心轴与活塞的中心轴重合，活塞的两端均设有驱动活塞轴向移动以引起工作腔室容积変化的触发装置，且活塞两端的触发装置驱动活塞运动的方向相反；
工作腔室包括分别位于缸体两端的左腔室和右腔室，活塞的中间设有台肩，台肩的左端面和左侧的导轨将缸体内腔围隔成密闭的左腔室，台肩的右端面和右侧导轨将缸体内腔围隔成密闭的右腔室；台肩上设有两条轴对称的左轴向槽和两条轴对称的右轴向槽，且左轴向槽和右轴向槽在活塞的横截面的圆周上等间距交替设置；左轴向槽与左腔室连通，右轴向槽与右腔室连通；缸体上设有两个轴对称的左窗口和两个轴对称的右窗口，与所述的排液孔连通的左窗口和与所述的吸液孔连通的右窗口在缸体的横截面上的投影沿缸体的圆周等间距交替分布；
轴对称是指以活塞的中心轴对称；轴向是指活塞的中心轴所在的方向，径向是指活塞横截面的直径所在的方向；
所述触发装置包括导轨和滚轮，导轨固定在缸体的端部，活塞贯穿导轨，且活塞的端部设有悬架，悬架上连接一对轴对称的滚轮；导轨呈轴向的环状曲面，曲面带有轴向的起伏，所述的导轨在中心轴方向的投影呈圆环状，所述的曲面有2个最高点和2个最低点，所述的最高点和最低点分别位于所述的圆环的相互垂直的两条直径上，所述的曲面分别依照所述的两条直径对称；滚轮在导轨上滚动，推动活塞沿轴向移动；
位于活塞两端的导轨的曲面起伏的波形，相互反相；
导轨的曲面的波形与左轴向槽和右轴向槽、左窗口和右窗口的位置具有如下对应关系：第一阶段导轨和滚轮驱动活塞向左移动，左轴向槽对准左窗口，左腔室排除液体，同时右轴向槽对准右窗口，右腔室吸入液体；第二阶段导轨和滚轮驱动活塞向右移动，左轴向槽对准右窗口，左腔室吸入液体，同时右轴向槽对准左窗口，右腔室排出液体；所述的导轨的内环侧高于外环侧；所述的滚轮是锥滚轮，锥滚轮的滚动面与导轨适配；
活塞两端的触发装置之一的悬架与穿入泵体内的电机输出轴同轴相连；
泵体的端盖与导轨将泵体内腔围隔成密闭的润滑腔，润滑腔通过开设在泵体上的润滑通道连通，且润滑通道上设有润滑油口。
进一步，所述的左窗口和右窗口位于中心轴的不同位置。
进一步，电机的输出轴上连接有拨叉，悬架的端部固定有拨盘，拨盘上开设有受力槽，拨叉设在受力槽内；拨叉的两侧设有径向的固定柱，固定柱上固定套设有轴承，拨叉通过轴承推动拨盘。
进一步，锥滚轮包括锥形轮套，锥形轮套包括筒体部和锥体部，锥形轮套套设在销轴上，销轴径向穿设在悬架上，筒体部与销轴之间设有球轴承，锥体部与销轴之间设有滚针轴承，球轴承和滚针轴承均套设在销轴上，并通过卡设在滚针轴承和销轴之间的螺纹套将球轴承和滚针轴承锁紧在锥形轮套内，螺纹套与销轴之间设有第一钢丝挡圈，螺纹套与锥体部之间设有第二钢丝挡圈。
又进一步，导轨设有径向安装孔，左销钉穿入泵体、缸体和左侧导轨上的径向安装孔，将缸体和左侧的导轨固定在泵体上，右销钉穿入缸体和右侧的导轨上的径向安装孔，将右侧的导轨固定在缸体上；导轨上设有与活塞相配合的轴向安装孔。
再进一步，悬架套设在活塞的端部，并通过圆柱销径向固定在活塞上。
更进一步，两个左窗口通过缸体上的第一环形槽连通，两个右窗口通过缸体上的第二环形槽连通。
本发明采用导轨与锥滚轮相配合的触发装置推动活塞做轴向移动和周向转动，借助活塞的轴向移动驱动工作腔室容积変化，借助活塞的轴向移动和周向转动实现配流，即分配工作腔室吸液或排液，省去了独立的配流机构。
本发明的有益效果体现在：
1、导轨与锥滚轮为线接触，增大了滚动接触的面积，降低了接触应力，有效避免打滑，也延长了接触部件的使用寿命。
2、润滑腔与工作腔室密闭隔开，实现了油水分离，即可适用于油介质，又适用于水介质，扩大了使用范围。
3、悬架悬挂在活塞的两端，具有相对于销轴旋转的自由度，可以对销轴两侧的锥滚轮进行自动对中微调。
4、将现有活塞泵采用的轴与活塞一体化集成，简化了整体结构，利用活塞的周向转动和轴向移动实现配流，省去了传统轴向活塞泵另需配置的配油盘或阀配流结构。
5、可实现连续吸排液功能和配流功能，而且活塞往复运动一次，单个活塞吸排液各进行两次，单个活塞旋转一周可实现两次往复运动，即四次吸、排液，而传统轴向柱塞(活塞)泵只能进行一次吸排液，在保证流量不变的前提下，本发明可以实现微型化，且成本得到大大降低。
6、传统活塞泵具有活塞-缸体摩擦副和配流摩擦副，本发明只有活塞-缸体摩擦副，提高了工作效率。
7、由于单元泵对称的运动特性，将两个单元泵串联即可基本消除流量脉动。
8、采用单元泵的设计可实现单元化插装，在按二进制流量设计插装后可通过电控实现 数字泵的设计。
附图说明
图1为本发明结构示意图。
图2为单元泵结构示意图。
图3为活塞结构示意图。
图4为图3中A-A向剖视图。
图5为缸体结构示意图。
图6为图5中A-A向剖视图。
图7为图5中B-B向剖视图。
图8为左侧的导轨的结构示意图。
图9为图8中A-A向剖视图。
图10为右侧的导轨的结构示意图。
图11为图10中A-A向剖视图。
图12为左侧的悬架、锥滚轮和拨盘装配示意图。
图13为右侧的悬架和锥滚轮装配结构示意图。
图14为左侧的悬架、锥滚轮和拨盘装配结构爆炸示意图。
图15为右侧的悬架和锥滚轮装配结构爆炸示意图。
图16为电机输出轴与拨叉装配结构爆炸示意图。
图17为活塞位于0°时，单元泵结构示意图。
图18为图17中A-A向剖视图。
图19为图17中B-B向剖视图。
图20为活塞逆时针旋转到
Figure PCTCN2016105811-appb-000001
时，单元泵结构示意图。
图21为图20中A-A向剖视图。
图22为图20中B-B向剖视图。
图23为活塞逆时针旋转到
Figure PCTCN2016105811-appb-000002
时，单元泵结构示意图。
图24为图23中A-A向剖视图。
图25为图23中B-B向剖视图。
图26为活塞逆时针旋转到
Figure PCTCN2016105811-appb-000003
时，单元泵结构示意图。
图27为图26中A-A向剖视图。
图28为图26中B-B向剖视图。
图29为活塞逆时针旋转到π时，单元泵结构示意图。
图30为图29中A-A向剖视图。
图31为图29中B-B向剖视图。
图32为滚轮在导轨上的位移、速度、加速度与活塞旋转角度之间的关系图。
具体实施方式
参照附图，二维锥滚轮活塞泵，包括泵体1，泵体1上开有吸液孔和排液孔，泵体1内设有泵单元，且泵单元与电机相连，
泵单元包括固定在泵体1内的缸体2，缸体2内设有活塞3，缸体2的中心轴与活塞3的中心轴重合，活塞3的两端均设有驱动活塞3轴向移动以引起工作腔室容积変化的触发装置，且活塞3两端的触发装置驱动活塞3运动的方向相反；
工作腔室包括分别位于缸体两端的左腔室和右腔室，活塞3的中间设有台肩31，台肩 31的左端面和左侧的导轨4将缸体2内腔围隔成密闭的左腔室，台肩31的右端面和右侧的导轨5将缸体2内腔围隔成密闭的右腔室；台肩31上设有两条轴对称的左轴向槽e、h和两条轴对称的右轴向槽f、g，且左轴向槽e、h和右轴向槽f、g在活塞3的横截面的圆周上等间距交替设置；左轴向槽e、h与左腔室连通，右轴向槽f、g与右腔室连通；缸体2上设有两个轴对称的左窗口a、c和两个轴对称的右窗口b、d，与所述的排液孔连通的左窗口a、c和与所述的吸液孔连通的右窗口b、d在缸体2的横截面上的投影沿缸体2的圆周等间距交替分布；
轴对称是指以活塞3的中心轴对称；轴向是指活塞3的中心轴所在的方向，径向是指活塞3横截面的直径所在的方向；
所述触发装置包括导轨4、5和滚轮9、7，导轨4、5固定在缸体2的端部，活塞3贯穿导轨4、5，且活塞3的端部设有悬架8、6，悬架8、6上连接一对轴对称的滚轮9、7；导轨4、5呈轴向的环状曲面41、51，曲面41、51带有轴向的起伏，所述的导轨4、5在中心轴方向的投影呈圆环状，所述的曲面有2个最高点和2个最低点，所述的最高点和最低点分别位于所述的圆环的相互垂直的两条直径上，所述的曲面分别依照所述的两条直径对称；滚轮9、7在导轨上滚动，推动活塞3沿轴向移动；
位于活塞3两端的导轨4、5的曲面起伏的波形，相互反相；
导轨4、5的曲面41、51的波形与左轴向槽e、h和右轴向槽f、g、左窗口a、c和右窗口b、d的位置具有如下对应关系：第一阶段导轨4、5和滚轮9、7驱动活塞3向左移动，左轴向槽e、h对准左窗口a、c，左腔室排除液体，同时右轴向槽f、g对准右窗口b、d，右腔室吸入液体；第二阶段导轨4、5和滚轮9、7驱动活塞3向右移动，左轴向槽e、h对准右窗口b、d，左腔室吸入液体，同时右轴向槽f、g对准左窗口a、c，右腔室排出液体；
所述的导轨4、5的内环侧高于外环侧；所述的滚轮9、7是锥滚轮，锥滚轮的滚动面与导轨4、5适配；
活塞3两端的触发装置之一的悬架8与穿入泵体1内的电机输出轴20同轴相连；本实施例中左侧的悬架8与电机输出轴20相连。
泵体1的端盖12、30与导轨4、5将泵体1内腔围隔成密闭的润滑腔，润滑腔通过开设在泵体1上的润滑通道连通，且润滑通道上设有润滑油口。
所述的左窗口a、c和右窗口b、d位于中心轴的不同位置，本实施例中左窗口a、c位于缸体的左侧，右窗口b、d位于缸体2的右侧。
电机的输出轴20上连接有拨叉18，悬架8的端部固定有拨盘81，拨盘81上开设有受力槽811，拨叉18设在受力槽811内；拨叉18的两侧设有径向的固定柱，固定柱上固定套设有轴承82，拨叉18通过轴承82推动拨盘81。
锥滚轮9、7包括锥形轮套91、71，锥形轮套91、71包括筒体部和锥体部，锥形轮套91、71套设在销轴16、17上，销轴16、17径向穿设在悬架8、6上，筒体部与销轴16、17之间设有推力轴承92、72，锥体部与销轴16、17之间设有滚针轴承93、73，推力轴承92、72和滚针轴承93、73均套设在销轴16、17上，并通过卡设在滚针轴承93、73和销轴16、17之间的螺纹套95、75锁紧在锥形轮套91、71内，螺纹套95、75与销轴16、17之间设有第一钢丝挡圈96、76，螺纹套95、75与锥体部之间设有第二钢丝挡圈94、74，起限定滚针轴承的作用，推力轴承92、72承担锥形轮套91、71的轴向力，滚针轴承93、73承担锥形轮套91、71的径向力，如图12、图13所示。
导轨4、5设有径向安装孔42、52，左销钉13穿入泵体1、缸体2和左侧导轨4上的径向安装孔42，将缸体2和左侧的导轨4固定在泵体1上，右销钉14穿入缸体2和右侧导轨5上的径向安装孔，将右侧的导轨5固定在缸体2上；导轨4、5上还设有与活塞3相配合的轴向安装孔。
悬架8、6套设在活塞3的端部，并通过圆柱销97、77径向固定在活塞3上。
两个左窗口a、c通过缸体2上的第一环形槽21连通，两个右窗口b、d通过缸体2上的第二环形槽22连通，以汇聚油液，便于油液在泵体中汇合。
泵体1的左端通过螺栓11固定安装有端盖12，左侧的端盖12与电机输出轴20之间安装有起密封作用的第二格来圈27和用于支撑电机输出轴20的深沟球轴承28，且电机输出轴20通过卡簧29固定在左端盖12上。
拨叉18通过销19、弹簧垫片84和第四钢丝挡圈85固定在电机输出轴的一端，电机输出轴20的另一端通过联轴器与电机相连。轴承82套在拨叉18两侧的固定柱上，并由第三钢丝挡圈81固定。轴承82采用深沟球轴承，且套设有轴承套83。
缸体2上设有与径向安装孔42、52一一对应的第二安装孔43、53；导轨4、5上设有与缸体2配合用于安装O形密封圈21、24的沟槽44、54，导轨4、5上还设有与活塞3配合用于安装第格莱圈23、26的沟槽44、55。
电机驱动拨叉18逆时针转动时，拨叉18将扭矩传递到轴承82，轴承82转动，驱动转盘81转动，转盘81带动左侧的悬架8转动，左侧悬架8上的锥滚轮9沿左侧导轨4转动。
导轨4、5上交替设有两个最高点m和两个轴对称的最低点n，当锥滚轮9、7从最低点n向相邻最高点m运动时，锥滚轮9、7会挤压导轨4、5，导轨4、5对锥滚轮9、7的反作用力会同步驱动活塞3轴向运动。而当锥滚轮9、7从最高点m向相邻最低点n运动时，导轨4、5会挤压锥滚轮9、7，锥滚轮9、7对导轨4、5的反作用力会同步驱动活塞3轴向运动。
由于活塞3两端的导轨4、5的曲面起伏的波形相互反相，即当一侧的锥滚轮从最低点n向最高点m运动时，另一侧的锥滚轮正好从最高点m向最低点n运动，促使活塞向同一个方向轴向移动。
导轨4、5上相邻的最低点n与最高点m之间的区域构成一个运动区间，每个运动区间对应的圆心角为
Figure PCTCN2016105811-appb-000004
在每个运动区间内，活塞3实现沿一个方向的一次轴向运动，相邻运动区间内活塞3的运动方向相反。且由于每个运动区间内曲面的形状相同，相邻的运动区间的曲面的波形反相，使得活塞3向左移动和向右移动具有相同的速率曲线。
优选的，可使导轨4、5的形状使活塞满足等加速等减速运动规律，即在每个运动区间内，在该区间的前半段，活塞3以相同的加速度加速，在该区间的后半段，活塞以相同的减速度减速，使得活塞3向左移动和向右移动具有相同的加速度曲线，加速度突变较小，使得活塞对缸体的冲击较小。导轨4、5呈空心圆柱状，锥滚轮9、7的滚动面与导轨4、5的曲面41、51相贴合，保证两个锥滚轮9、7的锥形轮廓线的延长线交汇于一点，再保证悬架8、6两侧的锥滚轮9、7与导轨4、5的贴合线的延长线与活塞3的中心轴线相交于一点，可使得悬架8、6两侧的锥滚轮9、7与导轨4、5接触线上的线速度之间的差值最小，防止转动时打滑。
台肩31的表面上交替开设有两条轴对称的左轴向槽e、h和两条轴对称的右轴向槽f、g，左轴向槽e、h始终与左腔室连通，右轴向槽f、g始终与右腔室连通。
当导轨4、5和滚轮9、7驱动活塞3向左轴向移动时，左腔室变小，右腔室变大，同时在导轨4、5和滚轮9、7驱动活塞3周向转动的过程中，左轴向槽e、h对准左窗口a、c，左腔室经过贯通的左轴向槽e、h和左窗口a、c向外排液；右轴向槽f、g对准右窗口b、d，左腔室经过贯通的右轴向槽f、g和右窗口b、d吸入液体，
当导轨4、5和滚轮9、7驱动活塞3向右轴向移动时，左腔室变大，右腔室变小，同时在导轨4、5和滚轮9、7驱动活塞3周向转动的过程中，左轴向槽e、h对准右窗口b、d，左腔室经过贯通的左轴向槽e、h和右窗口b、d向内吸液；右轴向槽f、g对准左窗口a、c ，左腔室经过贯通的右轴向槽f、g和左窗口a、c向外排液。
缸体2与导轨4、5之间通过O型密封圈21、24密封，且O型密封圈21、24外还套设有防止O型密封圈21、24变形的挡圈22、25，活塞3和导轨4、5之间通过第一格莱圈23、26密封，以保证左腔室、右腔室的密封。
电机的输出轴20与端盖12之间通过第二格莱圈27密封，润滑腔与工作腔室分离，润滑腔可对触发装置提供独立润滑。当本发明用于输送水时，润滑腔内的油与工作腔室内的水能完全隔开，不会互相污染，实现油水分离。
润滑腔通过润滑油口补充润滑油。
活塞3的两端铣平形成侧面为平面的插头，并在铣平后形成的平面上开有水平的第一径向孔32，悬架8、6的左端均开设有与插头相适配的套孔，该套孔的两侧和活塞3端部铣成的平面相贴合，与活塞3未铣平的弧面之间存在间隙；悬架8、6上开有与第一径向孔32贯通的第二径向孔82、62，活塞3两端的插头分别插入悬架8、6的套孔内，再将圆柱销插入第一径向孔32和第二径向孔82、62内，以将悬架8、6固定在活塞3上，且由于活塞端部与悬架套孔的弧面处留有间隙，使得悬架8、6具有一个绕圆柱销97、77略微摆动的自由度，锥滚轮9、7设置在销轴17、16上，销轴17、16的轴向与圆柱销97、77的轴向相互垂直，通过绕圆柱销97、77摆动悬架8、6，可对悬架8、6两端的锥滚轮9、7进行居中平衡微调，以使两端的锥滚轮9、7均紧贴导轨4、5。
以活塞旋转360°为一个工作周期，在初始状态下，左、右窗口a、b、c、d与左、右轴向槽e、f、g、h均相互错开，不产生沟通，左侧的悬架8上的锥滚轮9位于导轨4上的最低点n，右侧悬架6上的锥滚轮7位于导轨5上的最高点m，定义此时锥滚轮9、7和活塞3均位于0°，如图17-图19所示，本发明在一个工作周期(0～2π)内的工作流程为：
1)当锥滚轮9、7沿导轨4、5从0°运动到
Figure PCTCN2016105811-appb-000005
时，左侧悬架8上的锥滚轮9从最低点n向最高点m运动，右侧悬架6上的锥滚轮7从最高点m向最低点n运动，驱动活塞3向左移动，左腔室变小，右腔室变大。
随着活塞3的周向转动，左窗口a、c与左轴向槽e、h开始重合并贯通，同时，右窗口b、d与右轴向槽g、f也开始重合并贯通；当活塞3旋转到
Figure PCTCN2016105811-appb-000006
时，左窗口a、c与左轴向槽e、h的贯通面积达到最大，右窗口b、d与右轴向槽g、f的贯通面积也达到最大，活塞3达到中位，如图20、21、22所示。
当锥滚轮9、7沿导轨4、5继续从
Figure PCTCN2016105811-appb-000007
运动到
Figure PCTCN2016105811-appb-000008
时，左窗口a、c与左轴向槽e、h的贯通面积开始减小，右窗口b、d与右轴向槽g、f的贯通面积也开始减小，活塞3继续往左侧运动。
当锥滚轮9、7旋转到
Figure PCTCN2016105811-appb-000009
时，活塞3达到最左端，左窗口a、c与左轴向槽e、h错开，重合面积归零，右窗口b、d与右轴向槽g、f重合面积也归零，如图23、24、25所示。
在锥滚轮9、7从0°运动到
Figure PCTCN2016105811-appb-000010
的整个过程中，活塞3向左运动，左轴向槽e、h与左窗口a、c分别贯通并构成a-e通道、c-h通道，右轴向槽g、f与右窗口b、d分别贯通并构成b-g通道、d-f通道；左腔室经过a-e通道、c-h通道经泵体1上的排液孔向泵体外排液，右腔室始终经过b-g通道、d-f通道从泵体1上的吸液孔从泵体外吸液。本发明实现第一次吸、排液。
2)当锥滚轮9、7沿导轨4、5从
Figure PCTCN2016105811-appb-000011
运动到π时，左侧悬架8上的锥滚轮9从最高点m 向最低点n运动，右侧悬架6上的锥滚轮7从最低点n向最高点m运动，驱动活塞3沿轴向向右移动，左腔室变大，右腔室变小。
随着活塞3的周向转动，右窗口b、d与左轴向槽e、h开始重合并贯通，同时，左窗口a、c与右轴向槽g、f也开始重合并贯通。当活塞3旋转到
Figure PCTCN2016105811-appb-000012
时，右窗口b、d与左轴向槽e、h贯通面积最大，左窗口a、c与右轴向槽g、f的贯通面积也最大，活塞3达到中位，如图26、27、28所示。
当锥滚轮9、7沿导轨4、5继续从
Figure PCTCN2016105811-appb-000013
运动到π时，右窗口b、d与左轴向槽e、h的贯通面积开始减小，左窗口a、c与右轴向槽g、f的贯通面积也开始减小，活塞3继续往右侧运动。
当锥滚轮9、7转动到π时，活塞3到达最右端，右窗口b、d与左轴向槽e、h错开，贯通面积归零，左窗口a、c与右轴向槽g、f的贯通面积也归零，如图29、30、31所示。
在锥滚轮9、7从从
Figure PCTCN2016105811-appb-000014
运动到π的过程中，活塞3向右运动，右窗口b、d与左轴向槽e、h分别贯通并构成b-e通道、d-h通道，左窗口a、c与右轴向槽g、f分别贯通并构成a-f通道、c-g通道，左腔室经b-e通道、d-h通道从泵体外吸液，右腔室经a-f通道、c-g通道向泵体外排液，本发明实现第二次吸、排液。
3)当锥滚轮沿导轨从π运动到
Figure PCTCN2016105811-appb-000015
时，同锥滚轮沿导轨从0°运动到
Figure PCTCN2016105811-appb-000016
活塞3向左运动，本发明实现第三次吸、排液。
4)当锥滚轮沿导轨从
Figure PCTCN2016105811-appb-000017
运动到2π时，同锥滚轮沿导轨从
Figure PCTCN2016105811-appb-000018
运动到π，活塞3向右运动，本发明实现第四次吸、排液。
本发明由活塞3的周向转动和周向移动的结合实现了吸排液腔室的切换和连续的吸排液，省去了独立的配流机构；且一次周向转动，实现了四次吸液、四次排液。
当导轨4、5的形状使活塞满足等加速等减速运动规律时，活塞在一个工作周期内，活塞的轴向位移、速度、加速度与转动角度对应的关系如图32所示。
本说明书实施例所述的内容仅仅是对发明构思的实现形式的列举，本发明的保护范围不应当被视为仅限于实施例所陈述的具体形式，本发明的保护范围也及于本领域技术人员根据本发明构思所能够想到的等同技术手段。

Claims (7)

  1. 二维锥滚轮活塞泵，包括泵体，泵体上开有吸液孔和排液孔，泵体内设有泵单元，且泵单元与电机相连，其特征在于：
    泵单元包括固定在泵体内的缸体，缸体内设有活塞，缸体的中心轴与活塞的中心轴重合，活塞的两端均设有驱动活塞轴向移动以引起工作腔室容积変化的触发装置，且活塞两端的触发装置驱动活塞运动的方向相反；
    工作腔室包括分别位于缸体两端的左腔室和右腔室，活塞的中间设有台肩，台肩的左端面和左侧的导轨将缸体内腔围隔成密闭的左腔室，台肩的右端面和右侧导轨将缸体内腔围隔成密闭的右腔室；台肩上设有两条轴对称的左轴向槽和两条轴对称的右轴向槽，且左轴向槽和右轴向槽在活塞的横截面的圆周上等间距交替设置；左轴向槽与左腔室连通，右轴向槽与右腔室连通；缸体上设有两个轴对称的左窗口和两个轴对称的右窗口，与所述的排液孔连通的左窗口和与所述的吸液孔连通的右窗口在缸体的横截面上的投影沿缸体的圆周等间距交替分布；
    轴对称是指以活塞的中心轴对称；轴向是指活塞的中心轴所在的方向，径向是指活塞横截面的直径所在的方向；
    所述触发装置包括导轨和滚轮，导轨固定在缸体的端部，活塞贯穿导轨，且活塞的端部设有悬架，悬架上连接一对轴对称的滚轮；导轨呈轴向的环状曲面，曲面带有轴向的起伏，所述的导轨在中心轴方向的投影呈圆环状，所述的曲面有2个最高点和2个最低点，所述的最高点和最低点分别位于所述的圆环的相互垂直的两条直径上，所述的曲面分别依照所述的两条直径对称；滚轮在导轨上滚动，推动活塞沿轴向移动；
    位于活塞两端的导轨的曲面起伏的波形，相互反相；
    导轨的曲面的波形与左轴向槽和右轴向槽、左窗口和右窗口的位置具有如下对应关系：第一阶段导轨和滚轮驱动活塞向左移动，左轴向槽对准左窗口，左腔室排除液体，同时右轴向槽对准右窗口，右腔室吸入液体；第二阶段导轨和滚轮驱动活塞向右移动，左轴向槽对准右窗口，左腔室吸入液体，同时右轴向槽对准左窗口，右腔室排出液体；所述的导轨的内环侧高于外环侧；所述的滚轮是锥滚轮，锥滚轮的滚动面与导轨适配；
    活塞两端的触发装置之一的悬架与穿入泵体内的电机输出轴同轴相连；
    泵体的端盖与导轨将泵体内腔围隔成密闭的润滑腔，润滑腔通过开设在泵体上的润滑通道连通，且润滑通道上设有润滑油口。
  2. 如权利要求1所述的二维锥滚轮活塞泵，其特征在于：所述的左窗口和右窗口位于中心轴的不同位置。
  3. 如权利要求1所述的二维锥滚轮活塞泵，其特征在于：电机的输出轴上连接有拨叉，悬架的端部固定有拨盘，拨盘上开设有受力槽，拨叉设在受力槽内；拨叉的两侧设有径向的固定柱，固定柱上固定套设有轴承，拨叉通过轴承推动拨盘。
  4. 如权利要求3所述的二维锥滚轮活塞泵，其特征在于：锥滚轮包括锥形轮套，锥形轮套包括筒体部和锥体部，锥形轮套套设在销轴上，销轴径向穿设在悬架上，筒体部与销轴之间设有球轴承，锥体部与销轴之间设有滚针轴承，球轴承和滚针轴承均套设在销轴上，并通过卡设在滚针轴承和销轴之间的螺纹套将球轴承和滚针轴承锁紧在锥形轮套内，螺纹套与销轴之间设有第一钢丝挡圈，螺纹套与锥体部之间设有第二钢丝挡圈。
  5. 如权利要求4所述的二维锥滚轮活塞泵，其特征在于：导轨设有径向安装孔，左销钉穿入泵体、缸体和左侧导轨上的径向安装孔，将缸体和左侧的导轨固定在泵体上，右销钉穿入缸体和右侧的导轨上的径向安装孔，将右侧的导轨固定在缸体上；导轨上设有与活塞相配合的轴向安装孔。
  6. 如权利要求5所述的二维锥滚轮活塞泵，其特征在于：悬架套设在活塞的端部，并通过圆柱销径向固定在活塞上。
  7. 如权利要求6所述的二维锥滚轮活塞泵，其特征在于：两个左窗口通过缸体上的第一环形槽连通，两个右窗口通过缸体上的第二环形槽连通。
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