WO2020029899A1 - 柱塞泵及柱塞马达 - Google Patents

柱塞泵及柱塞马达 Download PDF

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Publication number
WO2020029899A1
WO2020029899A1 PCT/CN2019/099161 CN2019099161W WO2020029899A1 WO 2020029899 A1 WO2020029899 A1 WO 2020029899A1 CN 2019099161 W CN2019099161 W CN 2019099161W WO 2020029899 A1 WO2020029899 A1 WO 2020029899A1
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WIPO (PCT)
Prior art keywords
oil
cylinder
plunger
groove
main shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2019/099161
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English (en)
French (fr)
Inventor
朱德伟
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Qingdao Acme Innovation Technology Co Ltd
Original Assignee
Qingdao Acme Innovation Technology Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Qingdao Acme Innovation Technology Co Ltd filed Critical Qingdao Acme Innovation Technology Co Ltd
Priority to JP2021529509A priority Critical patent/JP7076870B2/ja
Priority to EP19847424.9A priority patent/EP3812588B8/en
Priority to US17/263,184 priority patent/US11661928B2/en
Publication of WO2020029899A1 publication Critical patent/WO2020029899A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0409—Cams
    • F03C1/0412—Cams consisting of several cylindrical elements, e.g. rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0435—Particularities relating to the distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/053—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the inner ends of the cylinders
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0413—Cams
    • F04B1/0417—Cams consisting of two or more cylindrical elements, e.g. rollers
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • 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
    • F04B53/006—Crankshafts

Definitions

  • the invention relates to the field of liquid variable capacity machinery, and in particular to a plunger pump and a plunger motor.
  • the plunger pump mainly includes an axial plunger pump (motor) and a radial plunger pump (motor).
  • the cylinder is driven by the main shaft to rotate, and the slide shoe and the plunger ball hinge, the slide shoe is inclined
  • the disc (or stator) slides to drive the plunger to reciprocate in the cylinder bore to complete the suction and discharge process.
  • the distribution plate or the distribution shaft and the cylinder (rotor) The friction pair is not balanced enough, prone to partial wear, and the reliability is not high enough; 3, the friction pair between the sliding shoe and the swash plate or stator of the plunger ball hinge is also relatively easy to wear; 4, the plunger has suffered The large lateral force intensifies the wear between the plunger and the cylinder bore, affecting the product performance; 5.
  • the cylinder (rotor) has a large moment of inertia, which is not conducive to starting; 6.
  • the piston has a certain rotation in the cylinder bore. The phenomenon aggravates the wear of the cylinder bore; 7. The rotation is not well balanced, the rotation is not smooth enough, the vibration is high, and the noise is high; 8.
  • the static pressure balance structure of the sliding shoe is highly sensitive to the cleanliness of the oil.
  • the purpose of the present invention is to provide a plunger pump and a plunger motor to solve the complex structure, low reliability, serious partial wear phenomenon, poor rotation balance, large vibration and high noise of the traditional plunger pump and plunger motor.
  • a plunger pump includes a cylinder body, a plunger, a main shaft, and an end cover.
  • the cylinder body is coaxially connected with the main shaft.
  • the plunger is installed in the cylinder hole of the cylinder body and moves along the cylinder hole.
  • it also includes an oil distribution mechanism, which includes an oil suction mechanism and an oil discharge mechanism;
  • a roller is installed on the plunger, and the roller is rotatably connected to the plunger;
  • the wheel and drive wheel are installed together with the main shaft or integrated with the main shaft.
  • the drive wheel is provided with a drive groove.
  • the raceway surface of the drive groove is curved.
  • the size of the drive groove is adapted to the outer diameter of the roller.
  • the rotation of the main shaft drives the drive wheel to rotate. To drive the plunger to move along the cylinder bore.
  • the oil suction mechanism adopts a valve flow distribution method or an axial flow distribution method
  • the oil discharge mechanism also adopts a valve flow distribution or shaft distribution method
  • valve distribution method of the oil suction mechanism uses an oil absorption check valve in the plunger or other positions
  • valve distribution method of the oil discharge mechanism uses an oil discharge check valve at an oil discharge port or other positions.
  • the inner surface of the cylinder body is further provided with supporting teeth, and the supporting teeth clamp the corresponding plunger, and the plunger moves along the supporting tooth surface.
  • the direction of the cylinder hole is perpendicular to the centerline of the cylinder block, the plunger moves radially along the cylinder block, and the driving wheels are symmetrically installed on both sides of the cylinder block.
  • the driving wheels are divided into left driving wheels and right driving wheels according to the installation position.
  • the driving groove of the driving wheel is divided into an inner raceway surface and an outer raceway surface.
  • the inner raceway surface and the outer raceway surface are continuous surfaces with periodic convex-concave undulation intervals and smoothly connected head and tail along the circumferential direction. The two are equally spaced. They are nested concentrically, and the spacing is adapted to the outer diameter of the rollers.
  • the rollers are symmetrically arranged on the left and right sides of the plunger, and the rollers on both sides fit in the drive grooves of the left and right drive wheels respectively. It is clamped to roll along the drive groove between the inner raceway surface and the outer raceway surface.
  • a casing is also installed outside the cylinder. The casing has an oil outlet. The oil inlet is located on the main shaft or other positions.
  • the bearing is supported on the housing, end cover or cylinder.
  • the direction of the cylinder bore is parallel to the direction of the center line of the cylinder block, and the cylinder blocks are symmetrically arranged left and right.
  • the cylinder holes of the left and right cylinder blocks are in one-to-one correspondence, and the plunger moves in the corresponding communicating cylinder bore.
  • Each plunger can form two left and right working chambers with the corresponding left and right cylinder holes, and simultaneously play the role of oil absorption and oil discharge.
  • the pumping process; the two ends of the housing are sealed with end caps.
  • the oil suction port and the oil discharge port are set on the main shaft and communicate with the cylinder holes respectively.
  • the driving wheel and the main shaft are integrally formed.
  • the position of the driving groove corresponds to the supporting teeth. It is a closed groove around the drive wheel. Its width and depth are compatible with the roller.
  • the roller is located on one side of the plunger, and the roller moves along the drive groove.
  • left and right symmetrical two cylinder bodies may also be set as a single cylinder body, and other components will be adaptively changed accordingly, which will not be described in detail here.
  • a cylinder sleeve is also installed between the left and right symmetrical cylinder bodies, and the supporting teeth are arranged on the cylinder sleeve or the cylinder body.
  • the plunger includes a support beam and a plunger body.
  • the plunger body is perpendicular to the support beam and is T-shaped or cross-shaped.
  • the plunger body is connected with or integrated with the support beam, and the roller is mounted on the support beam.
  • a guide sleeve may be provided on the support beam. When the plunger moves in the cylinder hole, the guide sleeve moves along the support teeth to reduce the wear on the support beam.
  • the upper end of the plunger body can also be provided with a wear ring to facilitate maintenance and replacement.
  • the side of the plunger can provide static pressure support to the plunger to reduce wear by providing a static pressure support groove.
  • the static pressure support groove can be The pressure hole communicates with the cylinder hole.
  • the axial flow distribution method of the oil suction mechanism is to set an oil suction groove on the outer circular surface of the left driving wheel, the oil suction groove is communicated with the indoor cavity of the plunger pump, and a cylinder oil suction channel is provided corresponding to each cylinder hole in the cylinder body.
  • a casing oil passage is opened, and the cylinder oil suction passage communicates with the cylinder hole through the casing oil passage; the cylinder oil suction passage and the cylinder hole can also pass through the cylinder body.
  • the axial flow distribution method of the oil discharge mechanism is to arrange oil discharge grooves on the outer circular surface of the right driving wheel, and the outer circular surface of the driving wheel is matched with the inner circular surface of the cylinder body, and the cylinder body corresponds to each cylinder hole.
  • Cylinder block oil discharge channel I and cylinder block oil discharge channel II are evenly distributed; the driving wheel controls the communication or cutoff between the cylinder block oil discharge channel I and the cylinder block oil discharge channel II through its outer circular surface and the oil drain groove.
  • the main shaft is provided with an oil suction groove and an oil discharge groove.
  • the oil suction groove communicates with the pump oil inlet through the internal oil suction oil passage of the main shaft
  • the oil discharge groove communicates with the pump oil outlet through the internal oil discharge oil passage of the main shaft
  • the cylinder oil passage is arranged at the end.
  • the cylinder oil passage communicates with the corresponding cylinder hole
  • the main shaft rotates
  • the oil suction groove communicates with the corresponding cylinder hole through the corresponding cylinder oil passage
  • the oil discharge groove communicates with the corresponding cylinder hole through the corresponding cylinder oil passage and cooperates with each other. Complete the suction and discharge process.
  • a plunger motor The drive mechanism of the plunger motor has the structural characteristics of any of the plunger pumps described above.
  • the pump oil discharge port of the plunger pump is a high-pressure oil that is used as the oil inlet of the plunger motor.
  • the axial flow mode of the plunger pump controls the high-pressure oil to enter the cylinder holes in a timely manner and drives the plunger to move in the cylinder holes, thereby driving the spindle to rotate and output power; the pump oil inlet of the original plunger pump is the return of the plunger motor.
  • the oil port can use the axial flow distribution method or valve flow distribution method of the plunger pump to cooperate with the movement of the plunger to control the return of hydraulic oil in the cylinder bore to realize the function of the motor.
  • the technical solution involved in the invention abandons the traditional mode of sliding shoe driving, the new structure is simple and reliable, reduces the sensitivity to oil cleanliness, and has high rotational balance of components and stable rotation.
  • the cylinder and plunger no longer rotate, reducing the moment of inertia, easy to start, and the setting of the supporting teeth reduces the column.
  • the lateral force between the sliding surface of the plug and the cylinder bore eliminates the autobiography problem of the plunger, reduces the wear of the cylinder bore, and improves product reliability.
  • Embodiment 1 is a schematic structural diagram of Embodiment 1;
  • FIG. 2 (1) is an A-A view of FIG. 1, and FIG. 2 (2) is a B-B view of FIG. 1;
  • Fig. 3 is a C-C view of Fig. 1;
  • Embodiment 4 is a three-dimensional schematic diagram of a driving wheel structure in Embodiment 1;
  • FIG. 5 is a three-dimensional schematic view of a cylinder structure in Embodiment 1;
  • FIG. 6 (1) is a three-dimensional schematic view of the plunger structure of Embodiment 1;
  • FIG. 6 (2) is a cross-sectional view of the plunger structure of Embodiment 1;
  • FIG. 7 (1) is a schematic diagram of the installation of a driving wheel and a plunger in Embodiment 1;
  • FIG. 7 (2) is a schematic diagram of the installation of a driving wheel and a cylinder in Embodiment 1;
  • FIG. 8 (1)-FIG. 8 (6) are schematic examples of the shape of a driving groove of a driving wheel
  • Embodiment 9 is a schematic structural diagram of Embodiment 2.
  • Fig. 10 (1) is a schematic cross-sectional view taken along the line D-D in Fig. 9;
  • Fig. 10 (2) is a schematic cross-sectional view taken along the line F-F in Fig. 9;
  • Embodiment 11 is a schematic structural diagram of Embodiment 3.
  • FIG. 12 is a schematic structural diagram of an oil suction groove and an oil discharge groove in Embodiment 2 and Embodiment 3;
  • FIG. 13 (1) is a sectional view taken along the line H-H in FIG. 11;
  • FIG. 13 (2) is a sectional view taken along the line I-I in FIG. 11;
  • Fig. 13 (3) is a sectional view taken along the line G-G in Fig. 11;
  • Fig. 13 (4) is a sectional view taken along the line J-J in Fig. 11;
  • Fig. 14 (5) is a sectional view of R-R in Fig. 14 (4);
  • Fig. 14 (6) is a three-dimensional schematic diagram of Fig. 14 (4);
  • 15 is a schematic assembly diagram of a split plunger structure
  • FIG. 16 is a schematic structural diagram of a parallel plunger according to Embodiment 5.
  • Figure 17 (1) is a front view of the assembly of a parallel plunger;
  • Figure 17 (2) is a Z1-Z1 sectional view of Figure 17 (1);
  • Figure 19 (1) is a schematic diagram of the assembly of a double-acting plunger;
  • Figure 19 (2) is a Z2-Z2 sectional view of Figure 19 (1);
  • Embodiment 7 is a schematic structural diagram of Embodiment 7.
  • Fig. 21 is a Q-Q view in Fig. 20;
  • FIG. 22 (1) is a sectional view taken along X1-X1 in FIG. 20;
  • FIG. 22 (2) is a sectional view taken along X2-X2 in FIG. 20;
  • FIG. 22 (3) is a sectional view taken along X3-X3 in FIG. 20;
  • FIG. 22 (4) is a sectional view taken along X4-X4 in FIG. 20;
  • FIG. 22 (5) is a cross-sectional view taken along X5-X5 in FIG. 20;
  • FIG. 22 (6) is a cross-sectional view taken along X6-X6 in FIG. 20;
  • FIG. 23 is a sectional view taken along X7-X7 in FIG. 20;
  • Embodiment 24 is a partially exploded view of Embodiment 7.
  • FIG. 25 is a schematic diagram of a driving groove formation principle in FIG. 20;
  • Figure 27 (1) is a schematic diagram of the installation of the guide sleeve in the integral plunger
  • Figure 27 (2) is a schematic diagram of the installation of the guide sleeve in the split plunger
  • FIG. 28 is a schematic structural diagram of Embodiment 10.
  • 29 is a sectional view taken along the line X8-X8 in FIG. 28;
  • the plunger pump includes a main shaft 1, a housing 5, a cylinder block 2, a driving wheel 4, a plunger 3, an end cover 6, an oil check valve 7, and ⁇ ⁇ Check valve 8.
  • the main shaft is provided with an oil inlet channel 11, and the main shaft is supported on the housing and the end cover through a bearing 12.
  • the pump chamber cavity is formed between the housing and the end cover.
  • the outer circular surface of the cylinder is matched with the inner circular surface of the housing and is The casing and the end cover are clamped and fixed in the casing; the cylinder body is provided with a plurality of radial cylinder holes 21 uniformly distributed on the circumference. This embodiment uses eight cylinder holes as an example.
  • each cylinder hole A plunger is correspondingly installed inside, and the sliding mating surfaces 34 of each plunger are respectively matched to form a working unit in the corresponding cylinder hole, and the two driving wheels are symmetrically mounted on both sides of the cylinder hole, and are splined. 42 is connected to the main shaft.
  • a driving groove 41 is provided on the driving wheel, and the driving groove has an inner raceway surface 411 and an outer raceway surface 412.
  • the inner and outer raceway surfaces are periodically convex and concave undulating and spaced smoothly from one end to the other along the circumferential direction. Continuous surface, the two are nested concentrically at equal intervals, and the distance is adapted to the outer diameter of the roller.
  • Two left and right rollers 32 on the plunger are respectively fitted to the drive grooves of the left and right drive wheels respectively. Inside, the roller is clamped between the inner and outer raceway surfaces of the nesting arrangement and can roll along the inner and outer raceway surfaces and is constrained by the inner and outer raceway surfaces.
  • the cylinder body is further provided with supporting teeth 22 corresponding to the cylinder holes.
  • the plunger is provided with a guiding surface 31 corresponding to the supporting teeth, and the plunger is held by the guiding surface. Between two adjacent support teeth, the plunger guide surface can slide along the surface of the support teeth.
  • the support teeth provide support and movement guidance for the plunger, can withstand the lateral force of the plunger, and limit the freedom of rotation of the plunger about the axis of the cylinder bore, so that the sliding mating surface of the plunger that cooperates with the cylinder bore can only be in the cylinder.
  • the inside of the hole slides in the direction of the cylinder bore axis and cannot be rotated.
  • the roller rolls in the driving groove and keeps the roller axis parallel to the main shaft axis.
  • the distance between the roller axis and the main shaft axis changes correspondingly with the periodic fluctuations of the inner and outer raceway surfaces. Therefore, the plunger is driven to generate a corresponding periodic reciprocating motion in the radial cylinder bore, and the oil suction and discharge process is completed in cooperation with the oil distribution mechanism.
  • the oil distribution method of this embodiment is valve distribution.
  • the oil distribution mechanism includes an oil suction check valve and an oil discharge check valve.
  • Each cylinder hole and the corresponding plunger constitute a working unit, and correspondingly, An oil suction check valve and an oil discharge check valve are arranged.
  • the oil suction check valve is arranged in the corresponding plunger hole 33, and the oil discharge check valve is arranged on the casing oil passage 51 corresponding to the cylinder hole.
  • the directional valve is in communication with the corresponding oil outlet.
  • Figure 1 respectively shows the process of the work unit S1 sucking oil from the pump suction port O and the process of the work unit S2 draining oil through the pump drain port P.
  • the arrows indicate the flow of hydraulic oil, which will not be described in detail here.
  • the driving principle of the driving wheel is as follows:
  • the main shaft drives the driving wheel to rotate clockwise, forcing the plunger roller to roll in the driving groove, and at the same time, the roller is forced to follow the inner and outer raceways under the pressure of the inner and outer raceway surfaces.
  • the periodic convexoconcavities of the surface fluctuate accordingly and make adaptive changes in position accordingly, so as to drive the plunger gradually away from or close to the center of the spindle, and then cause the plunger sliding mating surface to generate periodic reciprocating motion in the cylinder bore.
  • BB in Figure 2 (2) shows a schematic diagram of the momentary position of each plunger roller rolling in the drive groove.
  • the black dots indicate the convex and concave high and low points of the raceway surface in the drive groove;
  • the AA view shows the corresponding position of each plunger in the corresponding cylinder hole at the corresponding moment.
  • the roller of the plunger S3 is exactly at the convex high point T1 of the inner raceway surface, and the plunger at this position is away from the main axis.
  • the farthest point in the center the plunger has reached the top dead center position T0 of its stroke;
  • the roller of plunger S4 is just at the lowest point L2 of the recess of the inner raceway surface, and the plunger at this position is correspondingly at Shortest from the center of the spindle, the plunger reached the bottom dead center position L0 of the stroke.
  • the plunger roller always follows the periodic fluctuations of the raceway surface and continuously changes between the high and low points of the raceway surface, thereby driving the corresponding plunger at its top and bottom dead center. Corresponding periodic reciprocating movements are continuously performed between them, so as to realize the periodic suction and discharge of oil by the pump.
  • the plunger runs from the top dead center to the bottom dead center as an oil absorption process, and then moves from the bottom dead center to the top dead center as an oil drain process.
  • a continuous suction and oil discharge constitutes a working cycle. For example, as shown in the BB view of FIG.
  • T1 To L1 is the oil absorption process
  • L1 to T2 is the oil drainage process.
  • the number of working cycles of the plunger for one rotation of the driving wheel depends on the number of high and low points on the raceway surface. This embodiment exemplifies the case where the number of high and low points on the raceway surface is five. Therefore, the driving wheel can be driven every one revolution. Each plunger completes 5 working cycles.
  • FIGS. 8 (1) to 8 (6) there can be various installation forms of the inner and outer raceway surfaces of the drive groove.
  • FIGS. 8 (1) to 8 (6) Several installation schemes are preferred in FIGS. 8 (1) to 8 (6).
  • the example given in FIG. 8 (1) is the inner and outer raceway
  • the cross-sectional profile of the surface is a concentric circle with a certain eccentric distance.
  • One rotation of the driving wheel can drive the plunger to complete one working cycle;
  • the inner and outer raceway surfaces of Figure 8 (2) are oval surfaces, and one rotation of the driving wheel can drive the plunger.
  • Figures 8 (3), 8 (4), and 8 (5) are examples of continuous curved surfaces formed by the smooth end-to-end connection of several segments of r1 / r2 arc surfaces on the raceway surface, driving wheels One rotation can drive the plunger to complete 3, 4, and 5 working cycles respectively.
  • the example shown in Figure 8 (6) is the cross-sectional profile of the raceway surface formed by 4 r1 arcs smoothly connected by 4 straight lines Y. One rotation of the driving wheel can drive the plunger to complete 4 working cycles.
  • arc surfaces r1, r2 can also be transformed into other different shapes, different numbers of curved surfaces or planes, and connected together by a smooth transition to form different drive groove raceway surfaces, which will not be described in detail here. .
  • the rollers can be reasonably set according to the needs, and can be rolling structures such as bearings, bushes, and bushes.
  • the displacement of the pump can be adjusted by changing the size of the cylinder bore, increasing or decreasing the number of cylinder bore settings, changing the contour shape of the drive wheel raceway surface, etc., so that different specifications and models can be derived, and several pumps can be used in series.
  • each plunger and the corresponding cylinder hole can be used as an independent unit pump, or it can be combined with other working units to connect the corresponding pump oil outlets and combine with external oil supply to form different usage plans. It will not be described in detail here.
  • FIG. 9 is a front view of Embodiment 2.
  • the oil distribution mechanism of Embodiment 1 adopts a valve distribution method for the oil absorption and discharge distribution
  • the oil distribution mechanism of Embodiment 2 Adopts axial flow distribution + valve flow distribution.
  • the specific changes are as follows: in Example 2, the oil absorption distribution in Embodiment 1 was changed from the valve distribution to the shaft distribution, and the oil absorption check valve in the plunger was removed.
  • the structure of the driving wheels on the two sides of the cylinder is also different.
  • An oil suction groove 431 is evenly arranged on the outer circular surface of the wheel 43 to communicate with the cavity in the pump chamber.
  • the outer circular surface of the driving wheel is matched with the circular surface in the cylinder body, and the cylinders are arranged on the circular surface of the cylinder body corresponding to each cylinder hole.
  • the body oil suction channel 23 communicates with the corresponding cylinder bore through the housing oil channel 51.
  • the driving wheel suction groove and the outer surface timely control the opening and closing of the corresponding cylinder oil suction channel to match the oil absorption of the plunger.
  • oil discharge through coordination and cooperation to achieve the suction and discharge process of the plunger.
  • Figure 9 shows the process of the work unit S1 sucking oil from the pump suction port O and the process of the work unit S2 draining oil through the pump drain port P with arrows.
  • 10 (2) shows the matching state of the oil suction groove and the outer surface of the driving wheel with the oil suction channel of each cylinder at a certain moment
  • the DD of 10 (1) is the moment when each plunger is in the corresponding cylinder hole.
  • the oil suction channel of the cylinder body communicates with the oil suction groove of the driving wheel; while in the oil discharging state, the oil suction channel of the cylinder body is closed by the outer surface of the driving wheel.
  • the body oil suction channel and the driving wheel oil suction groove are cut off.
  • Other working principles are similar to those in Embodiment 1, and will not be described in detail here.
  • FIG. 11 is a front view of Embodiment 3. Compared with Embodiment 2, the main differences are as follows: The valve oil distribution method is used for the oil discharge distribution in Example 2, and the valve oil is used for the oil discharge distribution in Embodiment 2 in Example 3. It is changed to the axial flow distribution type. The specific change is: the oil drain check valve in the housing is removed. Correspondingly, as shown in FIG. 12, oil drain grooves 441 are uniformly arranged on the outer circular surface of the right drive wheel 44 and the right drive The outer circular surface of the wheel is matched with the inner surface of the cylinder body. At the same time, the cylinder oil discharge channel I24 and the cylinder oil discharge channel II25 are arranged on the circular surface of the cylinder body corresponding to each cylinder hole.
  • the cylinder oil discharge channel I passes The corresponding casing oil passage communicates with the corresponding cylinder bore, and the cylinder oil discharge passage II communicates with the corresponding pump oil discharge port.
  • the oil drain groove and the outer surface of the right drive wheel timely control the oil discharge channel I and oil discharge channel II of the cylinder. Opening and closing, through the coordination and cooperation to achieve the suction and discharge process of the plunger.
  • Fig. 11 shows the process of the work unit S1 sucking oil from the pump suction port O and the process of the work unit S2 draining oil through the pump drain port P with arrows.
  • the hydraulic oil enters the pump from the pump suction port O Indoor cavity, then enter the corresponding cylinder block oil suction channel through the oil suction groove of the left driving wheel, and then enter the corresponding cylinder hole through the corresponding housing oil channel; meanwhile, the outer circular surface of the right driving wheel closes the corresponding cylinder accordingly.
  • the cylinder block oil drain channel I and the cylinder block oil drain channel II cut off the oil drain passage corresponding to the cylinder bore, and cooperate to complete the oil suction process of the work unit S1.
  • the working unit S2 discharges oil
  • the corresponding oil suction channel of the cylinder block is closed by the outer surface of the left drive wheel, thereby cutting off the passage between the corresponding cylinder hole and the pump chamber cavity.
  • the cylinder block oil drain channel I and the cylinder block oil drain channel II of the unit S2 communicate with each other, and the compressed hydraulic oil is discharged from the pump drain port P through the casing oil channel, the cylinder oil drain channel I, and the cylinder oil drain channel II. .
  • Figure 13 (1) Figure 13 (4) show the cylinder bore, cylinder oil suction channel, cylinder oil discharge channel I, cylinder oil discharge channel II, the suction groove of the left driving wheel and the row of the right driving wheel.
  • Figure 11 shows the cooperation state of the oil tank at the moment of operation, in which the HH view of Figure 13 (1) shows the cooperation state of the oil suction tank and the outer circular surface of the left drive wheel with the oil suction channels of each cylinder block.
  • GG view and JJ view of FIG. 13 (4) show the mating state of the oil drain groove and the outer circular surface of the right drive wheel with the cylinder oil drain channel I and the cylinder oil drain channel II of each cylinder block, FIG.
  • FIG. 13 The II view of this figure shows the position of each plunger in the corresponding cylinder bore in this state.
  • the oil suction channel of the working unit in the oil suction state communicates with the oil suction groove of the left drive wheel.
  • the corresponding cylinder The body oil drain channel I and the cylinder oil drain channel II are closed by the outer surface of the right drive wheel, thereby cutting off the oil drain channel of the working unit; while the oil draining working unit has a cylinder oil drain channel I
  • the oil drain channel II of the cylinder block is communicated with the oil drain groove of the right drive wheel, and the oil drain channel is opened. Accordingly, the oil suction path of the cylinder block is driven by the outer of the left drive wheel. Closed surface, suction passage is closed.
  • FIG. 12 shows the assembly position of the main shaft with the left driving wheel and the right driving wheel in a three-dimensional view
  • FIG. 11 shows the oil suction fluid flow path of the work unit S1 and the oil discharge fluid flow path of the work unit S2 with arrows.
  • Other working principles Similar to the embodiment 2, detailed description is omitted here.
  • the plunger pump can also be used as a motor.
  • the plunger pump can be used as a plunger motor.
  • the plunger is The driving wheel can be driven to rotate by the reciprocating movement of the plunger in the cylinder hole under the action of high pressure oil, and then the main shaft is rotated to output power. The action process is opposite to that of the pump, which will not be described in detail here.
  • FIG. 14 is a cross-sectional view of the assembly of a split-type plunger with a cylinder block and a driving wheel.
  • Fig. 14 (5) is an RR cross-sectional view of Fig. 14 (4)
  • Fig. 14 (6) is a three-dimensional schematic diagram of Fig. 14 (4).
  • the static pressure support groove is opened in the lateral force of the plunger to bear pressure.
  • the area, its area size, shape, and specific setting position can be reasonably designed and arranged according to the actual pressure of the plunger.
  • the static pressure support groove communicates with the hydraulic oil of the cylinder bore through the static pressure hole 391, thereby lubricating the plunger lateral pressure bearing portion, and during the compression stroke stage of the pump, the compressed high pressure oil is guided to the static pressure support through the static pressure hole. Grooves, so as to produce a hydrostatic bearing on the surface of the plunger and reduce the wear of the cylinder bore caused by the lateral force of the plunger.
  • FIG. 17 (2) is a front view matching the cylinder block
  • FIG. 17 (2) is a Z1-Z1 sectional view of FIG. 17 (1).
  • FIG. 18 illustrates a double-acting structure of a plunger of a radial plunger pump.
  • Two sliding mating surfaces 34 are respectively arranged on two sides of a support beam.
  • cylinder bores on a cylinder block are radially arranged on two sides of corresponding support teeth. It is matched with the two sliding mating surfaces of the plunger respectively.
  • the support beam of the plunger penetrates the groove of the support tooth, the guide sleeve is sleeved on the support beam and fits in the groove of the support tooth and can roll along the length of the groove.
  • Fig. 19 (1) is a front view of the double-acting structure plunger and cylinder block
  • Fig. 19 (2) is Z2-Z2 of Fig. 19 (1) Sectional view, when the driving wheel drives the plunger to reciprocate in the cylinder hole through the roller and the support beam, the plunger can perform work twice in one working cycle, which will not be described in detail here.
  • FIG. 20 is a front view of Embodiment 7.
  • the plunger of Embodiment 4 is an axial arrangement form, and two cylinder bodies are arranged symmetrically with a total of 8 cylinder holes as an example. This arrangement form It can form 8 working units.
  • the plunger is a double-acting structure. As shown in the plunger structure in Figure 24, two sliding mating surfaces with left and right symmetry are respectively matched with the left and right cylinder bores.
  • the guide surface of the plunger is at The key groove formed by the supporting teeth slides in the groove to guide and support the plunger movement, as shown in Figure 22 (3) and Figure 22 (4).
  • the driving wheel driving groove is integrated on the main shaft.
  • the driving groove is a closed groove formed on the surface of the main shaft and surrounding the main shaft.
  • the plunger roller can roll in the drive groove; the drive groove has two extreme positions of Y1 and Y2 in the axial direction, as shown in FIG. 20, the two plungers shown in the figure have just moved to the extreme positions. ; Figure 21 shows the state of the other two plungers at the midpoint of the stroke.
  • the drive groove can drive the roller to complete a reciprocating cycle between Y1 and Y2, thereby driving the plunger to complete a reciprocating movement in the cylinder hole, and the corresponding left and right working units each complete an oil suction and discharge process.
  • the distance W between Y1 and Y2 is the stroke of the plunger pump.
  • the oil distribution mechanism of this embodiment adopts a shaft flow distribution, as shown in FIG. 24.
  • An oil suction groove 431 and an oil discharge groove 441 are provided on the main shaft, and communicate with the pump oil suction port and the pump oil discharge port through the internal oil passage of the main shaft, as shown in FIGS. 21 and 23.
  • Shown; and the cylinder oil passage 26 is correspondingly provided on the end cover and communicates with the corresponding cylinder hole, as shown in FIG. 20, FIG. 21, and FIG. 24.
  • the oil suction groove and the oil discharge groove communicate with the corresponding cylinder hole through the corresponding oil passage of the cylinder body in time, and cooperate with the corresponding work unit to complete the oil suction and discharge process.
  • FIG. 22 (2), Fig. 22 (5), and Fig. 22 (6) show the on-off state of the oil suction tank and oil drain tank in Fig. 20 at the moment of operation and the cylinder oil passage of each corresponding working unit.
  • the rotation direction of the main shaft is clockwise, and the principle of sucking and draining oil is similar to that in Embodiment 3, and details are not described herein again.
  • the driving grooves can be formed in various ways, and FIG. 25 illustrates the formation principles of the two driving grooves.
  • the drive groove is formed by using a keyway milling cutter.
  • the keyway milling cutter uses the origin as the starting point and cuts radially from the main shaft.
  • the tool also includes a uniform rotation around the main shaft (the X axis represents the angle of rotation) and The uniform speed movement along the axis of the spindle (Y axis represents the axial movement distance), the result of the XY compound movement forms a curve in the figure, which represents the trajectory of the tool around the surface of the spindle, thereby forming the corresponding drive groove.
  • Y1 and Y2 represent the two extreme positions of the drive groove in the axial direction
  • W is the axial distance, which determines the drive stroke of the drive groove.
  • the number of cycle cycles of the curve determines the number of cycles of oil suction and discharge that can be completed by the work unit in one revolution of the spindle.
  • the cycle numbers of the single-cycle drive groove and the double-cycle drive groove illustrated in the figure are 1 and 2, respectively, so that the work unit can complete one and two oil suction and discharge work cycles, respectively, when the spindle rotates once.
  • the number of circulation cycles of the drive groove can be reasonably set according to the needs.
  • the same number of oil circulation grooves and oil discharge grooves are configured to adapt to it.
  • the setting principle is similar to that of Embodiment 3 (the drive groove of Embodiment 3 is 5 cycle cycles). Number), which will not be described in detail here.
  • the number of cylinder bores can be increased or decreased as required, or two sets of left and right symmetry may not be required. Only one set may be provided, and multiple sets may be arranged in series to form a multiple pump.
  • This embodiment changes the oil supply method.
  • oil port P is used as the oil inlet and oil port O is used as the oil return port
  • this plunger pump can also be used as a motor. Its principle of action is exactly the opposite of the above pump. Here No more details.
  • FIG. 26 is a schematic diagram of this embodiment. Compared with Embodiment 7, the main difference is that the oil suction and discharge mechanism of this embodiment adopts a valve distribution method, that is, two check valves with opposite directions are provided corresponding to each working unit. The oil suction and discharge of each cylinder hole is automatically controlled, and its working principle is similar to that of Embodiment 1, which will not be described in detail here.
  • the oil distribution mechanism of Example 7 can also be set to adopt valve distribution for oil absorption and distribution, and shaft distribution for oil distribution and distribution, or shaft distribution for oil distribution and distribution, and
  • the structure of the valve distribution structure is similar to that described above, and will not be described in detail here.
  • a cylinder block sleeve 27 is provided to connect the left and right cylinder blocks together, and the supporting teeth are arranged on the cylinder block sleeve, thereby simplifying the manufacturing process of the cylinder block.
  • FIGs 27 (1) and 27 (2) illustrate two types of split plunger structures, which transfer the original integral plunger guide surface to the split
  • the guide sleeve is sleeved on the support beam of the plunger.
  • the guide surface of the guide sleeve can roll on the support surface of the supporting tooth, and at the same time, the rotation of the plunger relative to the axis of the cylinder hole is restricted , As shown in Figure 28, Figure 29.

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Abstract

一种柱塞泵以及柱塞马达。柱塞泵包括缸体（2）、柱塞（3）、主轴（1）、端盖（6）以及配油机构，配油机构包括吸油机构和排油机构；柱塞（3）上安装有滚子（32），滚子（32）与柱塞（3）可转动连接；主轴（1）上还带有驱动轮（4），驱动轮（4）与主轴（1）配合安装或者与主轴（1）一体成型，驱动轮（4）上开有驱动槽（41），驱动槽（41）的滚道面为曲面，驱动槽（41）尺寸与滚子（32）外圆尺寸相适应。该柱塞泵中缸体和柱塞不再旋转，降低了转动惯量，易于启动，且支撑齿的设置降低了柱塞滑动配合面与缸孔之间的侧向力，同时消除了柱塞的自转问题，提高了产品可靠性。

Description

柱塞泵及柱塞马达 技术领域
本发明涉及液体变容式机械领域，具体而言，涉及一种柱塞泵及柱塞马达。
背景技术
柱塞泵(马达)主要有轴向柱塞泵(马达)和径向柱塞泵(马达)，现有技术是通过主轴驱动缸体转动，通过滑靴与柱塞球铰，滑靴在斜盘(或定子)上滑动从而驱动柱塞在缸孔内往复运动，完成吸排油过程，尚存在以下不足：1、结构复杂，制造成本高；2、配流盘或配流轴与缸体(转子)摩擦副受力不够均衡，易于出现偏磨现象，可靠性不够高；3、与柱塞球铰的滑靴与斜盘或定子之间的摩擦副也比较容易磨损；4、柱塞承受了较大的侧向力，加剧了柱塞与缸孔之间的磨损，影响产品性能；5、缸体(转子)转动惯量较大，不利于启动；6、柱塞在缸孔内存在一定的自转现象，加剧了缸孔的磨损；7、转动的平衡性不好，转动不够平稳，振动大，噪音高；8、滑靴的静压平衡结构对油液清洁度的敏感度高。
发明内容
本发明的目的在于提供一种柱塞泵及柱塞马达，以解决传统柱塞泵和柱塞马达结构复杂、可靠性低，偏磨现象严重，转动平衡性差、振动大，噪音高；滑靴的静压平衡结构对油液清洁度的敏感度高的问题。
为了实现上述目的，本发明采用以下的技术方案：
一种柱塞泵，包括缸体、柱塞、主轴以及端盖，缸体与主轴同轴连接，柱塞安装在缸体的缸孔内，沿着缸孔运动，缸体的两端用端盖密封，除此之外，还包括配油机构，配油机构包括吸油机构和排油机构；所述柱塞上安装有滚子，滚子与柱塞可转动连接；主轴上还带有驱动轮，驱动轮与主轴配合安装或者与主轴一体成型，驱动轮上开有驱动槽，驱动槽的滚道面为曲面，驱动槽尺寸与滚子外圆尺寸相适应；主轴旋转，带动驱动轮转动，从而带动柱塞沿着缸孔运动。
进一步的，吸油机构采用阀配流方式或者轴配流方式，排油机构也采用阀配流或者轴配流方式；
进一步的，吸油机构的阀配流方式采用的是在柱塞中或其它位置设置吸油单向阀，排油机构的阀配流方式采用的是在排油口或其它位置设置排油单向阀。
进一步的，缸体内表面还设置有支撑齿，支撑齿夹持对应的柱塞，柱塞沿着支撑齿表面运动。
进一步的，缸孔方向垂直于缸体的中心线方向，柱塞沿着缸体径向运动，驱动轮对称安 装在缸体两侧，驱动轮按照安装位置分为左驱动轮和右驱动轮，驱动轮的驱动槽分为内滚道面和外滚道面，内滚道面和外滚道面为周期性凸凹起伏间隔且沿周向均布的首尾圆滑相接的连续面，二者等间距地同心嵌套在一起，其间距大小与滚子的外径相适应，滚子对称设置在柱塞左右两侧，两侧的滚子分别对应配合在左右两个驱动轮的驱动槽内，滚子被夹持在内滚道面、外滚道面之间沿驱动槽滚动；缸体外还安装有壳体，壳体上带有出油口，进油口位于主轴或者其他位置上，主轴通过轴承支撑在壳体、端盖或缸体上。
进一步的，缸孔方向平行于缸体的中心线方向，缸体左右对称布置，左右对称布置的情况下左右缸体的缸孔一一对应相连通，柱塞在对应连通的缸孔内运动，每一柱塞可与对应的左右缸孔形成左右两个工作室，同时起到吸油和排油的作用，当一侧工作室吸油时，对应另一侧的工作室排油，交替做功，完成泵油过程；壳体的两端用端盖密封，吸油口和排油口均设置在主轴上，分别与缸孔连通，驱动轮与主轴一体成型，驱动槽的位置与支撑齿对应，驱动槽是环绕驱动轮一周的封闭槽，其宽度和深度与滚子相适应，滚子位于柱塞的一侧，滚子沿着驱动槽运动。
根据实际需要，上述左右对称的两个缸体也可仅设置为单个缸体，其它零部件相应地做出适应性变化，在此不再详述。
进一步的，左右对称的缸体之间还安装有缸体套，支撑齿设置在缸体套或者缸体上。
进一步的，柱塞包括支撑梁和柱塞本体，柱塞本体与支撑梁垂直，呈T字形或者十字形，柱塞本体与支撑梁装配连接或者一体成型，滚子安装在支撑梁上。
进一步的，支撑梁上还可以设置导向套，当柱塞在缸孔内运动的时候，导向套沿着支撑齿上运动，减少对支撑梁的磨损。
进一步的，柱塞本体的上端还可以设置耐磨环以方便维修更换，柱塞的侧面可通过设置静压支撑槽的方式对柱塞提供静压支撑以减少磨损，静压支撑槽可通过静压孔与缸孔连通。
进一步的，吸油机构的轴配流方式为在左驱动轮的外圆面设置吸油槽，吸油槽与柱塞泵的室内腔相连通，缸体内对应各缸孔设置有缸体吸油道，壳体内开有壳体油道，缸体吸油道通过壳体油道与缸孔连通；缸体吸油道与缸孔亦可在缸体内贯通。
进一步的，排油机构的轴配流方式为在右驱动轮的外圆面上对应均布设置排油槽，驱动轮的外圆面与缸体的内圆面配合，缸体上对应于各缸孔均布设置缸体排油道Ⅰ和缸体排油道Ⅱ；驱动轮通过其外圆面及排油槽控制缸体排油道Ⅰ和缸体排油道Ⅱ之间的连通或切断，当驱动轮外圆面上的排油槽运转至与缸体排油道Ⅰ和缸体排油道Ⅱ相对的位置时，缸体排油道Ⅰ和缸体排油道Ⅱ即通过排油槽连通，实现泵的排油；反之，缸体排油道Ⅰ和缸体排油道Ⅱ的油口则被驱动轮外圆面封闭，从而切断了二者之间的连通，泵排油口进入关闭状态，配合 泵的吸油过程。
进一步的，主轴上设置有吸油槽和排油槽，吸油槽通过主轴内部吸油油道与泵吸油口相通，排油槽通过主轴内部排油油道与泵排油口相通，缸体油道设置在端盖上，缸体油道与对应缸孔相通，主轴旋转，吸油槽通过对应的缸体油道与对应的缸孔连通，排油槽通过对应的缸体油道与对应的缸孔连通，相互配合完成吸排油过程。
一种柱塞马达，该柱塞马达的驱动机构具有以上任一所述柱塞泵的结构特征，柱塞泵的泵排油口为本柱塞马达的进油口通入高压油，并采用柱塞泵的轴配流方式控制高压油适时的进入各缸孔并驱动柱塞在缸孔内运动，进而带动主轴旋转输出动力；而原柱塞泵的泵吸油口则为本柱塞马达的回油口，可采用柱塞泵的轴配流方式或阀配流方式配合柱塞的运动控制缸孔内液压油的回油，实现马达的功能。
本发明具有以下有益效果：
该发明所涉及的技术方案，摒弃了滑靴驱动的传统模式，新结构简单可靠，降低了对油液清洁度的敏感度，且部件回转平衡性高，转动平稳，解决了现有技术转动的平衡性不好、转动不够平稳、配流摩擦副和滑靴摩擦副可靠性不高的问题，同时缸体和柱塞不再旋转，降低了转动惯量，易于启动，且支撑齿的设置降低了柱塞滑动配合面与缸孔之间的侧向力，同时消除了柱塞的自传问题，减少了缸孔的磨损，提高了产品可靠性。
附图说明
图1是实施例1结构示意图；
图2(1)是图1的A-A视图，图2(2)是图1的B-B视图；
图3是图1的C-C视图；
图4是实施例1中驱动轮结构三维示意图；
图5是实施例1中缸体结构三维示意图；
图6(1)是实施例1柱塞结构三维示意图；图6(2)是实施例1柱塞结构剖视图；
图7(1)是实施例1中驱动轮与柱塞安装示意图；图7(2)是实施例1中驱动轮与缸体安装示意图；
图8(1)—图8(6)是驱动轮的驱动槽形状示意图例；
图9是实施例2结构示意图；
图10(1)是图9中的D-D剖视示意图；图10(2)是图9中的F-F剖视示意图；
图11是实施例3结构示意图；
图12是实施例2、实施例3中的吸油槽、排油槽结构示意图；
图13(1)是图11中的H-H剖视图；图13(2)是图11中的I-I剖视图；
图13(3)是图11中的G-G剖视图；图13(4)是图11中的J-J剖视图；
图14(1)—14图(4)是实施例4中所述的分体式柱塞结构示意图；
图14(5)是图14(4)中R-R剖视图；图14(6)是图14(4)的三维示意图；
图15是分体式柱塞结构装配示意图；
图16是实施例5所述的并联式柱塞结构示意图；
图17(1)是并联式柱塞装配主视图；图17(2)是图17(1)的Z1-Z1剖视图；
图18是实施例6所述的双作用柱塞结构示意图；
图19(1)是双作用柱塞装配示意图；图19(2)是图19(1)的Z2-Z2剖视图；
图20是实施例7结构示意图；
图21是图20中的Q-Q视图；
图22(1)是图20中的X1-X1剖视图；图22(2)是图20中的X2-X2剖视图；
图22(3)是图20中的X3-X3剖视图；图22(4)是图20中的X4-X4剖视图；
图22(5)是图20中的X5-X5剖视图；图22(6)是图20中的X6-X6剖视图；
图23是图20中的X7-X7剖视图；
图24是实施例7的部分爆炸视图；
图25是图20中驱动槽形成原理示意图；
图26是实施例8结构示意图；
图27(1)是整体式柱塞中导向套安装示意图；图27(2)是分体式柱塞中导向套安装示意图；
图28是实施例10结构示意图；
图29是图28中X8-X8剖视图；
其中，上述附图包括以下附图标记：1、主轴；11、进油通道；12、轴承；13、吸油油道；14、排油油道；2、缸体；21、缸孔；22、支撑齿；23、缸体吸油道；24、缸体排油道Ⅰ；25、缸体排油道Ⅱ；26、缸体油道；27、缸体套；3、柱塞；31、导向面；32、滚子；33、柱塞孔；34、滑动配合面；35、柱塞本体；36、支撑梁；37、导向套；38、耐磨环；39、静压支撑槽；391、静压孔；4、驱动轮；41、驱动槽；411、内滚道面；412、外滚道面；42、花键；43、左驱动轮；431、吸油槽；44、右驱动轮；441、排油槽；5、壳体；51、壳体油道；6、端盖；7、吸油单向阀；8、排油单向阀。
具体实施方式
下面结合附图对本发明作进一步说明。
实施例1
如图1-图8(6)所示，本发明所述的柱塞泵包括主轴1、壳体5、缸体2、驱动轮4、柱塞3、端盖6、吸油单向阀7以及排油单向阀8。主轴上带有进油通道11，主轴通过轴承12支撑在壳体和端盖上，壳体和端盖之间形成泵室内腔，缸体的外圆面与壳体的内圆面配合并被壳体和端盖夹持固定在壳体内；缸体上设置有若干个呈圆周均布的径向缸孔21，本次实施例以8个缸孔为例说明，相应地，每个缸孔内对应安装有1个柱塞，每个柱塞的滑动配合面34分别对应配合在相应的缸孔内形成一个工作单元，两个驱动轮则左右对称地装配在缸孔两边，并通过花键42与主轴连接。
如图4所示，驱动轮上设置有驱动槽41，驱动槽具有内滚道面411和外滚道面412，内外滚道面为周期性凸凹起伏间隔且沿周向均布的首尾圆滑相接的连续面，二者等间距地同心嵌套在一起，其间距大小与滚子的外径相适应，柱塞上左右对称设置的两个滚子32分别对应配合在左右两个驱动轮的驱动槽内，滚子被夹持在嵌套布置的内外滚道面之间并可沿内外滚道面滚动并受内外滚道面约束。
如图5所示，缸体上对应于缸孔还设置有支撑齿22，如图6(1)所示，柱塞上对应于支撑齿设置有导向面31，柱塞通过导向面被夹持在两个相邻支撑齿之间，柱塞导向面可沿支撑齿的表面滑动。支撑齿对柱塞提供支撑和运动导向，可承受柱塞所受的侧向力，同时限制柱塞绕缸孔轴线的转动自由度，使与缸孔配合的柱塞滑动配合面只能在缸孔内沿缸孔轴线方向滑动而无法转动。当主轴带动驱动轮旋转时，滚子在驱动槽内滚动且保持滚子轴线与主轴轴线平行，同时随内外滚道面的周期性起伏变化而相应地改变滚子轴线与主轴轴线之间的距离，从而带动柱塞在径向缸孔内产生相应的周期性往复运动，并在配油机构配合下完成吸排油过程。
本实施例的配油方式为阀配流，如图1所示，配油机构包括吸油单向阀和排油单向阀，每个缸孔与对应的柱塞构成为一个工作单元，并相应地配置一个吸油单向阀和排油单向阀，吸油单向阀设置在相应的柱塞孔33内，排油单向阀则设置在与缸孔对应的壳体油道51上，排油单向阀与对应的出油口相通。当工作单元处于吸油阶段时，液压油从泵吸油口吸入泵室内腔，然后推开相应工作单元的吸油单向阀，通过对应的柱塞进油孔进入相应缸孔，完成该工作单元的吸油，与此同时，在吸油过程中，该工作单元的对应排油单向阀则相应地处于关闭状态；当工作单元处于排油阶段时，液压油在对应柱塞的压缩迫使下从相应缸孔进入对应壳体油道，然后推开相应的排油单向阀，通过泵排油口对外供油，从而完成该工作单元的排油；与此同时，在排油过程中，该工作单元的对应吸油单向阀则相应地处于关闭状态。图1用箭头分别展示了工作单元S1从泵吸油口O吸油的过程和工作单元S2通过泵排油口P排油的过程，图中用箭头表示液压油流向，在此不再详述。
驱动轮的驱动原理如下：
如图2(1)、图2(2)所示，主轴带动驱动轮顺时针旋转，迫使柱塞滚子在驱动槽内滚动，同时滚子在内外滚道面的迫使下随着内外滚道面的周期性凸凹高低起伏而相应地做出位置上的适应性变化，从而带动柱塞逐渐远离或靠近主轴中心，进而使柱塞滑动配合面在缸孔内产生周期性往复运动。图2(2)的B-B展示了各柱塞滚子在驱动槽内滚动的某瞬间位置示意图，图中用黑点标识出了驱动槽内滚道面的凸凹高低点；图2(1)的A-A视图则展示了相应瞬间各柱塞在对应缸孔内的对应位置，其中，柱塞S3的滚子恰好处在了内滚道面的凸起高点T1，此位置的柱塞处于距离主轴中心的最远处，柱塞运行到了其行程的上止点位置T0；而柱塞S4的滚子则恰好处在了内滚道面的凹处最低点L2，此位置的柱塞则相应处于距离主轴中心的最近处，柱塞运行到了行程的下止点位置L0。在驱动轮不断旋转的过程中，柱塞滚子总是顺应滚道面的周期性起伏变化不断地在滚道面的高低点之间滚动变换，从而驱动对应柱塞在其行程的上下止点之间不断地进行相应的周期性往复运动，从而实现泵的周期性吸排油。柱塞从上止点运行到下止点为吸油过程，进而，再由下止点运行到上止点为排油过程，一次连续的吸油和排油构成一个工作循环。例如，如图2(2)的B-B视图所示，当图中的T1、L1、T2三点随着驱动轮的转动依次通过柱塞滚子时，则对应柱塞即完成一个工作循环，T1到L1为吸油过程，L1到T2为排油过程。驱动轮旋转一周柱塞的工作循环次数取决于滚道面凸凹高低点的数量，本实施例示范的是滚道面凸凹高低点的数量各为5个的情况，因此驱动轮每旋转一周可驱动每个柱塞完成5个工作循环。
显而易见，驱动槽内外滚道面的设置形式可以有多种，图8(1)～图8(6)优选了几种设置方案，图中，图8(1)给出的示例为内外滚道面的截面轮廓形状为偏心一定距离的同心圆，驱动轮旋转一周可驱动柱塞完成1个工作循环；图8(2)的内外滚道面为椭圆形面，驱动轮旋转一周可驱动柱塞完成2个工作循环；图8(3)、图8(4)以及图8(5)给出的示例为滚道面为几段r1/r2圆弧面首尾圆滑连接形成的连续曲面，驱动轮旋转一周可分别驱动柱塞完成3、4、5个工作循环；图8(6)给出的示例为滚道面的截面轮廓形状为4个r1圆弧用4段直线Y平滑连接形成的，驱动轮旋转一周可驱动柱塞完成4个工作循环。显然，根据实际需要，上述圆弧面r1、r2还可变换为其它不同形状、不同数量的曲面或平面通过圆滑过渡的方式连接在一起形成不同的驱动槽滚道面，在此不再详述。
滚子可根据需要合理设置，可为轴承、轴瓦、轴套等滚动结构。
泵的排量可通过改变缸孔大小、增加或减少缸孔的设置数量、改变驱动轮滚道面轮廓形状等方式加以调整，从而衍生出不同的规格型号，亦可几个泵串联使用。
上述每个柱塞与对应缸孔形成的工作单元即可以作为一个独立的单元泵使用，亦可以与 其它工作单元组合将相应泵排油口连在一起合并对外供油，形成不同的使用方案，在此不再详述。
实施例2
图9为实施例2的主视图，与实施例1相比，主要区别为：实施例1的配油机构中吸油配流和排油配流均采用阀配流方式，而实施例2的配油机构则采用轴配流+阀配流的混合式配流。具体变动为：实施例2将实施例1中的吸油配流由阀配流式改为了轴配流式，去掉了柱塞中的吸油单向阀，缸体两侧的驱动轮结构也有所区别，左驱动轮43的外圆面上均布设置吸油槽431与泵室内腔相通，驱动轮的外圆面与缸体内圆面配合，同时在缸体内圆面上对应于各缸孔均布设置缸体吸油道23与对应缸孔通过壳体油道51相通，在驱动轮旋转的过程中，驱动轮吸油槽和外圆面适时地控制对应的缸体吸油道的开闭以配合柱塞的吸油和排油，通过协调配合来实现柱塞的吸排油过程。图9用箭头分别示出了工作单元S1从泵吸油口O吸油的过程和工作单元S2通过泵排油口P排油的过程，在工作单元S1吸油时，液压油从泵吸油口O进入泵室内腔，然后通过驱动轮的吸油槽进入缸体吸油道，进而通过壳体油道进入对应的缸孔。在工作单元S2排油时，与其对应的缸体吸油道被驱动轮的外圆面封闭，从而切断了缸孔与泵室内腔的通道，而被压缩的液压油则打开对应的排油单向阀从泵排油口P排油。图10(2)的F-F视图展示了驱动轮的吸油槽和外圆面与各缸体吸油道在某瞬间的配合状态，而10(1)的D-D为该瞬间各柱塞在对应缸孔中的位置，图中，处于吸油状态的工作单元，其缸体吸油道与驱动轮吸油槽相通；而处于排油状态的工作单元，其缸体吸油道则被驱动轮的外圆面封闭，缸体吸油道与驱动轮吸油槽处于切断状态。其它工作原理与实施例1类似，在此不再详述。
实施例3
图11为实施例3的主视图，与实施例2相比，主要区别为：实施例2的排油配流采用阀配流方式，而实施例3则将实施例2中的排油配流由阀配流改为了轴配流式，具体变动为：去掉了壳体中的排油单向阀，相应地，如图12所示在右驱动轮44的外圆面上对应均布设置排油槽441，右驱动轮的外圆面与缸体内圆面配合，同时在缸体内圆面上对应于各缸孔均布设置缸体排油道Ⅰ24和缸体排油道Ⅱ25，缸体排油道Ⅰ通过对应的壳体油道与对应的缸孔相通，而缸体排油道Ⅱ则与对应的泵排油口相通。在右驱动轮旋转的过程中，配合柱塞的吸油和排油过程，右驱动轮的排油槽和外圆面适时地控制对应缸体的缸体排油道Ⅰ和缸体排油道Ⅱ的开闭，通过协调配合来实现柱塞的吸排油过程。图11用箭头分别示出了工作单元S1从泵吸油口O吸油的过程和工作单元S2通过泵排油口P排油的过程，在工作单元S1吸油时，液压油从泵吸油口O进入泵室内腔，然后通过左驱动轮的吸油槽进入对应的缸体吸油道，进 而通过对应的壳体油道进入对应的缸孔；与此同时，右驱动轮的外圆面则相应地封闭对应缸孔的缸体排油道Ⅰ和缸体排油道Ⅱ，从而切断了对应缸孔的排油通道，配合完成工作单元S1的吸油过程。在工作单元S2排油时，与其对应的缸体吸油道被左驱动轮的外圆面封闭，从而切断了对应缸孔与泵室内腔的通道，与此同时，右驱动轮的排油槽将工作单元S2的缸体排油道Ⅰ和缸体排油道Ⅱ连通，被压缩的液压油通过壳体油道、缸体排油道Ⅰ和缸体排油道Ⅱ从泵排油口P排油。
图13(1)—图13(4)展示了缸体的缸孔、缸体吸油道、缸体排油道Ⅰ、缸体排油道Ⅱ和左驱动轮的吸油槽及右驱动轮的排油槽在图11所示工作瞬间的相互配合状态图，其中图13(1)的H-H视图展示了左驱动轮的吸油槽和外圆面与各缸体吸油道的配合状态，而图13(3)的G-G视图和图13(4)的J-J视图展示了右驱动轮的排油槽和外圆面与各缸体的缸体排油道Ⅰ和缸体排油道Ⅱ的配合状态，图13(2)的I-I视图为该状态下各柱塞在对应缸孔中的位置，图中，处于吸油状态的工作单元，其缸体吸油道与左驱动轮的吸油槽相通，相应地，对应的缸体排油道Ⅰ和缸体排油道Ⅱ则被右驱动轮的外圆面封闭，从而切断了该工作单元的排油通道；而处于排油状态的工作单元，其缸体排油道Ⅰ和缸体排油道Ⅱ则被右驱动轮的排油槽连通，排油通道开启，相应地，其缸体吸油道则被左驱动轮的外圆面封闭，吸油通道关闭。图12用三维图展示了主轴与左驱动轮和右驱动轮的装配位置图，图11用箭头示出了工作单元S1的吸油液流路线及工作单元S2的排油液流路线，其它工作原理与实施例2类似，在此不再详述。
改变供油方法，本柱塞泵还可以变为马达使用。当我们把泵排油口做为马达进油口通入高压油，同时将原来的泵吸油口作为马达的回油口使用，则该柱塞泵即可变为柱塞马达使用，柱塞即可在高压油作用下通过柱塞在缸孔内的往复运动带动驱动轮转动，进而带动主轴旋转输出动力，其作用过程与泵相反，在此不再详述。
实施例4：
如图14(1)-图14(4)所示，分别示例了4种径向柱塞泵的分体式柱塞结构，柱塞本体35与支撑梁36通过分体制造装配在一起，同时分体设置导向套37，导向套套在柱塞的支撑梁上，当柱塞在缸孔内滑动时，导向套可在支撑齿的支撑面上滚动同时限制柱塞相对于缸孔轴线的转动。图15为分体式柱塞与缸体、驱动轮装配在一起的剖视图，吸油单向阀和排油单向阀设置在了缸孔的上部。图14(3)所示的柱塞上与缸孔配合的部位还设置了至少一道耐磨环38与缸孔配合；图14(4)—图14(6)则示例了带静压支撑槽39的柱塞结构，图14(5)为图14(4)的R-R剖视图，图14(6)为图14(4)的三维示意图，静压支撑槽开在柱塞的侧向力承压部位，其面积大小、形状、及具体设置位置可根据柱塞的实际承压情况 合理设计并布置。静压支撑槽通过静压孔391与缸孔的液压油连通，从而对柱塞侧向承压部位进行润滑，并在泵的压缩行程阶段，通过静压孔将压缩高压油引到静压支撑槽，从而对柱塞表面产生静压支承的作用，减小柱塞因承受侧向力而导致的缸孔磨损。通过以上柱塞结构的各种变化并配合前述多种配油机构，可以得到不同的柱塞泵(马达)的技术方案，在此不再详述。
实施例5：
如图16(1)、图16(2)所示，分别示例了至少2个柱塞并联在一起成组使用的并联结构(图中以2个柱塞并联为例)，几个柱塞通过支撑梁连接在一起，对应地，缸体上设置对应数量的缸孔分别与对应并联柱塞配合，如图17(1)、图17(2)所示，图17(1)为并联柱塞与缸体配合的主视图，图17(2)为图17(1)的Z1-Z1剖视图。通过以上柱塞结构的变化并配合前述多种配油机构，可以得到不同的柱塞泵(马达)的技术方案，在此不再详述。
实施例6：
图18示例了径向柱塞泵的柱塞的双作用结构，两个滑动配合面34分别布置在支撑梁的两边，对应地，缸体上的缸孔沿径向布置在对应支撑齿的两边并分别与柱塞的两个滑动配合面配合，柱塞的支撑梁贯穿在支撑齿的沟槽内，导向套套在支撑梁上并配合在支撑齿的沟槽内且可沿沟槽长度方向滚动，如图19(1)和图19(2)所示，图19(1)为双作用结构柱塞与缸体配合的主视图，图19(2)为图19(1)的Z2—Z2剖视图，当驱动轮通过滚子和支撑梁驱动柱塞在缸孔内往复滑动时，一个工作循环柱塞可做功两次，在此不再详述。
实施例7：
图20为实施例7的主视图，与前述柱塞泵相比，实施例4的柱塞为轴向布置形式，以左右对称布置两个缸体共8个缸孔为例，此种布置形式可组成8个工作单元；柱塞为双作用结构，如图24中的柱塞结构所示，具有左右对称的两个滑动配合面分别与左右对称的缸孔配合，柱塞的导向面则在支撑齿形成的键槽内滑动，对柱塞运动进行导向和支撑，如图22(3)和图22(4)所示。本实施例将驱动轮驱动槽集成在了主轴上，如图24中的主轴结构示意图所示，驱动槽为在主轴表面上开出的环绕主轴一周的封闭槽，其宽度和深度与柱塞滚子相适应，柱塞滚子可在驱动槽内滚动；驱动槽在轴向具有Y1和Y2两个极限位置，如图20所示，图中所示的两个柱塞正好运动到了极限位置上；图21则展示了另外两个柱塞在行程中点位置的状态。当主轴旋转一周，驱动槽可驱动滚子在Y1和Y2之间完成一个往复循环，从而带动柱塞在缸孔内完成一次往复运动，对应的左右两个工作单元则各完成一次吸排油过程，Y1和Y2之间的距离W则为柱塞泵的行程。
本实施例的配油机构采用轴配流，如图24，吸油槽431和排油槽441设置在主轴上，并 通过主轴内部油道与泵吸油口和泵排油口相通，如图21、图23所示；而缸体油道26则相应设在端盖上且与对应缸孔相通，如图20、图21、图24所示。当主轴旋转时，吸油槽和排油槽通过对应的缸体油道与对应的缸孔适时连通，配合相应工作单元完成吸排油过程。图22(1)、图22(2)、图22(5)、图22(6)展示了图20的工作瞬间吸油槽和排油槽与各对应工作单元的缸体油道的通断状态，主轴旋转方向为顺时针旋转，其吸排油原理与实施例3类似，在此不再详述。
驱动槽可由多种形成方式，图25示例了2种驱动槽的形成原理。假设驱动槽是用键槽铣刀加工形成，键槽铣刀以原点为起始点，从主轴径向切入，刀具除自身的旋转外，还包括绕主轴的匀速转动(X轴表示转过的角度)和沿主轴轴向的匀速移动(Y轴表示轴向移动距离)，XY复合运动的结果即形成图中的曲线，代表了刀具环绕主轴表面走过的轨迹，从而形成相应的驱动槽。Y1和Y2代表了驱动槽在轴向的两个极限位置，W为轴向距离，决定了驱动槽的驱动行程大小，曲线的循环周期数决定了主轴转动一周工作单元可完成的循环吸排油次数。图中示例的单循环驱动槽和双循环驱动槽的循环周期数分别为1和2，从而主轴旋转一周工作单元可分别完成1个和2个吸排油工作循环。驱动槽的循环周期数可根据需要合理设置，相应地，配置相同循环周期数量的吸油槽和排油槽与之适应，其设置原理与实施例3类似(实施例3的驱动槽为5个循环周期数)，在此不再详述。
缸孔设置数量可根据需要增减，亦可不必左右对称设置两组，仅设置一组亦可，亦可多组串联设置形成多联泵。
本实施例改变供油方法，例如：以油口P作为进油口，油口O作为回油口，则本柱塞泵亦可以变为马达使用，其作用原理与上述泵正好相反，在此不再详述。
实施例8：
图26为本实施例的示意图，与实施例7相比，主要区别为：本实施例的吸排油机构均采用阀配流方式，即：对应于每个工作单元设置两个方向相反的单向阀自动控制每个缸孔的吸排油，其工作原理与实施例1类似，在此不再详述。
实施例9：
结合实施例7和8，实例7配油机构还可设置为吸油配油方式为阀配流，而排油配油方式为轴配流，或者吸油配油方式为轴配流，而排油配油方式为阀配流的结构形式，其工作原理与前述类似，在此不再详述。
实施例10：
如图27—图29所示，本实施例通过设置缸体套27将左右两个缸体连接在一起，支撑齿设置在缸体套上，从而简化了缸体的制造工艺。
柱塞结构亦可根据需要做出种种变化，图27(1)和图27(2)优选示例了两种分体式的柱塞结构，将原来整体式柱塞的导向面转移到了分体设置的导向套上，导向套套在柱塞的支撑梁上，当柱塞在缸孔内滑动时，导向套的导向面可在支撑齿的支撑面上滚动，同时限制柱塞相对于缸孔轴线的转动，如图28、图29所示。
需要指出的是，以上仅为本发明较佳的具体实施方式，但本发明的保护范围并不局限于此。显而易见，根据实际需要，还可以抽取或参照上述各实施例所展示的技术特征、技术方法及技术构思进行优化排列组合，做出其它的方案，在此不再穷举。任何熟悉本领域的技术人员在本发明揭露的技术范围内，根据本发明的实施方案及其发明构思加以等同替换或改变，例如：改变缸孔数量或布置方向，改变驱动轮形状，改变驱动槽形态，改变油道位置或数量、形态，改变油路连接方法，改变单向阀形式、数量及布置方法等，都应涵盖在本发明的保护范围之内。
在本发明的描述中，需要说明的是，术语“前端”、“后端”、“左右”“上”、“下”、“水平”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。
在本发明的描述中，还需要说明的是，除非另有明确的规定和限定，术语“设置”、“安装”、“相连”、“连接”、“连通”应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或一体地连接；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本发明中的具体含义。
当然，上述内容仅为本发明的较佳实施例，不能被认为用于限定对本发明的实施例范围。本发明也并不仅限于上述举例，本技术领域的普通技术人员在本发明的实质范围内所做出的均等变化与改进等，均应归属于本发明的专利涵盖范围内。

Claims (14)

  1. 一种柱塞泵，包括缸体(2)、柱塞(3)、主轴(1)以及端盖(6)，缸体(2)与主轴(1)同轴连接，柱塞(3)安装在缸体(2)的缸孔(21)内，沿着缸孔(21)运动，缸体(2)的两端用端盖(6)密封，其特征在于，还包括配油机构，配油机构包括吸油机构和排油机构；所述柱塞(3)上安装有滚子(32)，滚子(32)与柱塞(3)可转动连接；主轴(1)上还设置有驱动轮(4)，驱动轮(4)与主轴(1)配合安装或者与主轴(1)一体成型，驱动轮(4)上开有驱动槽(41)，驱动槽(41)的滚道面为曲面，驱动槽(41)尺寸与滚子(32)外圆尺寸相匹配；主轴(1)旋转，带动驱动轮(4)转动，从而带动柱塞(3)沿着缸孔(21)运动。
  2. 根据权利要求1所述的柱塞泵，其特征在于，吸油机构采用阀配流方式或者轴配流方式，排油机构也采用阀配流或者轴配流方式。
  3. 根据权利要求2所述的柱塞泵，其特征在于，吸油机构的阀配流方式采用的是在柱塞(3)中安装吸油单向阀(7)，排油机构的阀配流方式采用的是在排油口安装排油单向阀(8)。
  4. 根据权利要求1-3任一所述的柱塞泵，其特征在于，缸体(2)内表面还设置有支撑齿(22)，支撑齿(22)夹持对应的柱塞(3)，柱塞(3)沿着支撑齿(22)表面运动。
  5. 根据权利要求4所述的柱塞泵，其特征在于，缸孔(21)方向垂直于缸体(2)的中心线方向，柱塞(3)沿着缸体(2)径向运动，驱动轮(4)对称安装在缸体(2)两侧，驱动轮(4)按照安装位置分为左驱动轮(43)和右驱动轮(44)，驱动轮(4)的驱动槽(41)分为内滚道面(411)和外滚道面(412)，内滚道面(411)和外滚道面(412)为周期性凸凹起伏间隔且沿周向均布的首尾圆滑相接的连续面，二者等间距地同心嵌套在一起，其间距大小与滚子(32)的外径相适应，滚子(32)对称设置在柱塞(3)左右两侧，两侧的滚子(32)分别对应配合在左右两个驱动轮(4)的驱动槽(41)内，滚子(32)被夹持在内滚道面(411)、外滚道面(412)之间沿驱动槽(41)滚动；缸体(2)外还安装有壳体(5)，壳体(5)上带有出油口，主轴(1)通过轴承(12)支撑在壳体(5)、端盖(6)或缸体(2)上。
  6. 根据权利要求4所述的柱塞泵，其特征在于，缸孔(21)方向平行于缸体(2)的中心线方向，缸体(2)左右对称布置，左右缸体(2)的缸孔(21)一一对应相连通，柱塞(3)在对应连通的缸孔(21)内运动，每一柱塞(3)可与对应的左右缸孔(21)形成左右两个工作室，同时起到吸油和排油的作用，当一侧工作室吸油时，对应另一侧的工作室排油，交替做功，完成吸排油过程；壳体(5)的两端用端盖(6)密封，吸油口和排油口均设置在主轴(1)上，分别与缸孔(21)连通，驱动轮(4)与主轴(1)一体成型，驱动槽(41)的位置与支撑齿(22)对应，驱动槽(41)是环绕驱动轮(4)一周的封闭槽，其宽度和深度与滚子(32)相适应，滚子(32)位于柱塞(3)的一侧，滚子(32)沿着驱动槽(41)运动。
  7. 根据权利要求6所述的柱塞泵，其特征在于，左右对称的缸体(2)之间还安装有缸 体套(27)，支撑齿(22)设置在缸体套(27)上或者缸体(2)上。
  8. 根据权利要求1-3任一所述的柱塞泵，其特征在于，柱塞(3)包括支撑梁(36)和柱塞本体(35)，柱塞本体(35)与支撑梁(36)垂直，呈T字形或者十字形，柱塞本体(35)与支撑梁(36)装配连接或者一体成型，滚子(32)安装在支撑梁(36)上。
  9. 根据权利要求8所述的柱塞泵，其特征在于，支撑梁(36)上还设置有导向套(37)，当柱塞(3)在缸孔(21)内运动的时候，导向套(37)沿着支撑齿(22)上运动，减少对支撑梁(36)的磨损。
  10. 根据权利要求8所述的柱塞泵，其特征在于，柱塞本体(35)的上端设置有耐磨环(38)，柱塞(3)的侧面还开有静压支撑槽(39)，静压支撑槽(39)通过静压孔(391)与缸孔(21)连通。
  11. 根据权利要求2所述的柱塞泵，其特征在于，吸油机构的轴配流方式为在左驱动轮(43)的外圆面设置吸油槽(431)，吸油槽(431)与柱塞泵的室内腔相连通，缸体(2)内圆面对应各缸孔(21)设置有缸体吸油道(23)，壳体(5)内开有壳体油道(51)，缸体吸油道(23)通过壳体油道(51)与缸孔(21)连通。
  12. 根据权利要求2所述的柱塞泵，其特征在于，排油机构的轴配流方式为在右驱动轮(44)的外圆面上对应均布设置排油槽(441)，驱动轮(4)的外圆面与缸体(2)的内圆面配合，缸体(2)上对应于各缸孔(21)均布设置缸体排油道Ⅰ(24)和缸体排油道Ⅱ(25)，驱动轮(4)通过其外圆面及排油槽(441)控制缸体排油道Ⅰ(24)和缸体排油道Ⅱ(25)之间的连通或切断，当驱动轮(4)外圆面上的排油槽(441)运转至与缸体排油道Ⅰ(24)和缸体排油道Ⅱ(25)相对的位置时，缸体排油道Ⅰ(24)和缸体排油道Ⅱ(25)即通过排油槽(441)连通，实现泵的排油；反之，缸体排油道Ⅰ(24)和缸体排油道Ⅱ(25)的油口则被驱动轮(4)外圆面封闭，从而切断了二者之间的连通，泵排油口进入关闭状态，配合泵的吸油过程。
  13. 根据权利要求1-3任一所述的柱塞泵，其特征在于，主轴(1)上设置有吸油槽(431)和排油槽(441)，吸油槽(431)通过主轴(1)内部吸油油道(13)与泵吸油口相通，排油槽(441)通过主轴(1)内部排油油道(14)与泵排油口相通，缸体油道(26)设置在端盖(6)上，缸体油道(26)与对应缸孔(21)相通，主轴(1)旋转，吸油槽(431)通过对应的缸体油道(26)与对应的缸孔(21)连通，排油槽(441)通过对应的缸体油道(26)与对应的缸孔(21)连通，相互配合完成吸排油过程。
  14. 一种柱塞马达，其特征在于，该柱塞马达的驱动机构具有权利要求1、2、3、5、6、7、9、10、11或12任一项所述柱塞泵的驱动机构的结构特征，柱塞泵的泵排油口为本柱塞 马达的进油口通入高压油，并采用柱塞泵的轴配流方式控制高压油进入各缸孔(21)并驱动柱塞(3)在缸孔(21)内运动，进而带动主轴(1)旋转输出动力；原柱塞泵的泵吸油口则为本柱塞马达的回油口，采用柱塞泵的轴配流方式或阀配流方式配合柱塞的运动控制缸孔(21)内液压油的回油，实现马达的功能。
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