WO2020182205A1 - Duplex axial plunger motor - Google Patents
Duplex axial plunger motor Download PDFInfo
- Publication number
- WO2020182205A1 WO2020182205A1 PCT/CN2020/079226 CN2020079226W WO2020182205A1 WO 2020182205 A1 WO2020182205 A1 WO 2020182205A1 CN 2020079226 W CN2020079226 W CN 2020079226W WO 2020182205 A1 WO2020182205 A1 WO 2020182205A1
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- WO
- WIPO (PCT)
- Prior art keywords
- plunger
- oil
- sliding plate
- swash plate
- plate
- Prior art date
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Classifications
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- 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
- F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
- F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F03C1/0639—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
-
- 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
- F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
- F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F03C1/0644—Component parts
-
- 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
- F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
- F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F03C1/0644—Component parts
- F03C1/0668—Swash or actuated plate
-
- 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
- F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
- F03C1/0678—Control
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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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
-
- 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
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2078—Swash plates
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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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
-
- 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
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/30—Control of machines or pumps with rotary cylinder blocks
-
- 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
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
Definitions
- the embodiment of the present disclosure relates to an axial plunger motor, and more particularly to a double-connected non-through shaft plunger motor.
- the axial piston motor is one of the most widely used hydraulic components in modern hydraulic transmission.
- the hingeless inclined axis motor and the sliding shoe swash plate axial piston motor are the two most widely used and most important types of shafts. To the plunger motor. These two motors are still in competition, and each is constantly improving and developing.
- At least one embodiment of the present disclosure provides a dual axial plunger motor, including two sliding plate non-through shaft plunger motors and a terminal sandwiched between the two sliding plate non-through shaft plunger motors
- Each sliding plate type non-through shaft plunger motor includes a main shaft, a swash plate, a sliding plate, a plunger and a cylinder.
- the sliding plate is an integral structure and is supported on the swash plate to form a flow distribution sliding plate sub-assembly.
- the end surface of the sliding plate opposite to the swash plate is provided with a static pressure support surface
- the end surface of the sliding plate opposite to the cylinder is provided with a plurality of plunger ball sockets
- the sliding plate is provided with a connecting plunger ball socket and
- the oil through hole of the hydrostatic bearing surface one end of the plunger is placed in the plunger ball socket, the other end is inserted into the cylinder, one end of the plunger center hole inside the plunger is connected to the oil through hole, and the other end is connected to the
- the plunger hole in the cylinder communicates with the swash plate.
- the swash plate of the two sliding plate type non-through shaft plunger motors is supported on a common end seat.
- the flow distribution oil groove and the end The oil inlet and outlet ports set on the seat are connected, and the high-pressure oil flows through the distribution oil groove, the oil through hole, the plunger center hole and the plunger hole on the swash plate to drive the cylinder body and the main shaft to rotate synchronously.
- a plurality of oil chambers are provided on the hydrostatic bearing surface of the sliding plate, and the oil chambers are spaced apart from the axis of the sliding plate.
- an oil through hole is provided between the bottom of each oil chamber and the corresponding plunger ball socket. The oil through hole serves as the main channel for sucking and discharging oil and introduces the oil into the static pressure support.
- a sealing portion for sealing oil is provided on the boss surface, and the sealing portion includes a radially inner and outer side of the oil chamber.
- the inner sealing part and the outer sealing part, and the interval sealing part arranged between adjacent oil chambers.
- a plurality of oil chambers are provided on the static pressure supporting surface, and the end surface of the swash plate opposite to the sliding plate is provided with The low-pressure distribution window and the high-pressure distribution window are intermittently communicated with the oil chamber.
- the supporting surface on the swash plate opposite to the end seat has a cylindrical supporting surface formed into a cylindrical shape.
- the cylindrical supporting surface is provided with a groove-shaped low-pressure port and a groove-shaped high-pressure port that are configured in a groove shape, and the groove-shaped low-pressure port and the groove-shaped high-pressure port are respectively communicated with the low-pressure distribution window and the high-pressure distribution window.
- the oil through hole on the sliding plate and the plunger center hole on the plunger are both large-diameter main oil holes for sucking and discharging oil. structure.
- the axial plunger motor is configured as a centralized variable structure, and the end seat is provided with a variable mechanism including a spool valve, two The shaft pins of the two opposite swash plates are connected to a common slide valve. Under the action of the hydraulic pressure and spring force of the variable mechanism, the slide valve drives the two swash plates to rotate synchronously to realize synchronous variable.
- the axial plunger motor is configured as a separate variable structure, and the housing of the axial plunger motor is connected with two Variable mechanism, the variable mechanism is respectively connected with the corresponding swash plate, and realizes independent variable under the action of hydraulic pressure and spring force of the respective variable mechanism.
- the sliding plate type non-through shaft plunger motors distributed on both sides of the end seat are combined in a variable manner of swash plate, and the specific combination method is two sides Slip-disk type non-thru-shaft plunger motors are of variable type structure; or both sides-slip-disk type non-thru-shaft plunger motors are of quantitative structure; or slide-plate type non-thru-shaft plunger motors on both sides are of quantitative structure , The other is a variable structure.
- one end of the main shaft of the two sliding disc type non-through shaft plunger motors extends out of the housing and is supported on the first bearing, and the other One end cantilever supports the cylinder body and rotates synchronously with the cylinder body.
- the plunger hole of the cylinder body is a structure with one end closed and one end open. The closed end of the cylinder body is not provided with a distribution pair. The main shaft and When the cylinder is rotating, the hydraulic axial force is transmitted to the housing through the cylinder through the first bearing.
- the first bearing supporting the main shaft includes at least one centripetal thrust bearing or thrust bearing, and hydraulic axial force acts on the plunger during operation.
- the hole closes the end surface of the cylinder at one end and is transmitted to the casing of the plunger pump or the motor through the first bearing.
- a third bearing is interposed between the swash plate and the sliding plate, and the sliding plate is in a state of being restricted in its radial direction. Supported on the third bearing.
- the middle part of the swash plate has a supporting shaft or a supporting shaft pin extending outward
- the sliding plate is provided with a central through hole
- the first The three bearings are sandwiched between the inner wall of the central through hole of the sliding plate and the supporting shaft or the supporting shaft pin, and the sliding plate is supported on the third bearing in a state of being restrained in the radial direction.
- the outer periphery of the swash plate is provided with a raised support stop, and the third bearing is sandwiched between the outer side of the swash plate and the support stop. Between the inner sides, the sliding plate is supported on the third bearing in a state of being restrained in its radial direction.
- the plunger includes a connecting rod plunger with a tapered structure or a connecting rod plunger with a ball head or a belt on both ends.
- a type of spherical plunger with a hinge one end of the plunger can be inserted into the plunger hole of the cylinder in a reciprocating manner relative to the cylinder, and the other end is fixed on the sliding plate in a state where the distance from the end surface of the sliding plate is restricted and can be tilted.
- the plunger is provided with a large-aperture plunger center hole communicating the plunger ball socket and the plunger hole.
- a valve plate is sandwiched between the sliding plate and the swash plate, and the sliding plate is supported on the valve plate and kept sliding with the valve plate
- the valve plate is provided with high and low pressure valve ports, and the high pressure oil flows through the valve oil groove on the swash plate, the valve port of the valve plate, the oil chamber of the sliding plate, the oil through hole, the center hole of the plunger and the cylinder block.
- the plunger hole drives the cylinder body and the spindle to rotate synchronously.
- Figure 1 is a schematic diagram of a swash plate type non-through shaft plunger motor
- Fig. 2 is an embodiment of the double-joint concentrated variable axial piston motor in the present disclosure
- Figure 3 is a cross-sectional view of the axial plunger motor A-A of Figure 2 in this disclosure
- Figure 4 is a plan view of one end of the sliding plate in this disclosure.
- Fig. 5 is a B-B sectional view of the sliding plate in Fig. 4 in this disclosure.
- Figure 6 is a plan view of the other end of the sliding plate in this disclosure.
- FIG. 7 is a plan view of the supporting surface of one end of the swash plate opposite to the sliding plate in the present disclosure
- Figure 8 is another plan view of the supporting surface of one end of the swash plate opposite to the sliding plate in the present disclosure
- Figure 9 is a plan view of the swash plate opposite to the end seat in this disclosure.
- Figure 10 is a D-D cross-sectional view of the swash plate of Figure 9 in this disclosure.
- FIG. 11 is an embodiment of a double-connected concentrated variable axial piston motor adopting a sliding disk internal support method in this disclosure
- Fig. 12 is an E-E sectional view of the axial piston motor in Fig. 11 in this disclosure
- FIG. 13 is an embodiment of a dual concentrated variable axial plunger motor adopting a sliding disk external support method in this disclosure
- Fig. 14 is an embodiment of the double-coupled split variable axial piston motor in this disclosure.
- 15 is a cross-sectional view of a sliding plate type non-through shaft plunger motor including a valve plate in this disclosure.
- FIG. 16 is a schematic diagram of the structure of the quantitative sliding disc type axial piston motor in this disclosure.
- 10 is the spindle
- 10C is the spindle axis
- 12 is the spindle shoulder
- 21 is the first bearing
- 21a is the radial ball bearing
- 21b is the radial thrust bearing or thrust bearing
- 22 is the second bearing
- 31 is the front shell
- 32 is the shell body
- 33 is the end seat
- 33a is the oil inlet
- 33b is the oil outlet
- 33c is the spool valve
- 33d is the flow channel
- 33e is the sliding surface
- 34 is
- the first cavity, 35 is the second cavity
- 38 is the variable connection part
- 40 is the swash plate
- 41 is the support surface of the swash plate
- 41a is the support block
- 42 is the distribution oil groove
- 43 is the low pressure distribution window
- 44 is the high pressure distribution window
- 45 is a cylindrical support surface
- 46 is a groove-shaped low-pressure port
- 47 is a groove-shaped high-pressure port
- 48
- FIG. 1 it is a typical structure of a non-through shaft swash plate type axial piston motor, which includes a swash plate 40, a sliding shoe 120, a plunger 70, a cylinder 80, a valve plate 90, a main shaft 10, and a center Spring 100, return plate 130 and other components.
- a swash plate 40 a sliding shoe 120
- a plunger 70 a plunger 70
- a cylinder 80 a valve plate 90
- main shaft 10 a center Spring 100, return plate 130 and other components.
- One end of the main shaft 10 is supported on a bearing at one end, and the other end penetrates the valve plate 90 and is connected to the cylinder block 80 by a key.
- the central spring 100 connects the sliding shoe 120 through the sleeve 102 and the steel ball 101.
- the central spring 100 compresses the cylinder block and the valve plate through the outer sleeve 103, a cylinder liner 84 is provided on the outer peripheral surface of the cylinder block 80, and a second bearing 22 is interposed between the cylinder liner 84 and the motor housing 32.
- the purpose of the present disclosure is to provide a dual axial piston motor in view of the problems of non-thru-shaft axial piston motors that cannot be connected in series, are low in reliability, and are too large in size. Demand for hydraulic motors with high power, high pressure and large flow, compact structure and high reliability.
- the embodiments of the present disclosure are shown in a typical orientation, the orientation is such that when the central axis of the spindle of the axial plunger motor stands horizontally, “longitudinal”, “lateral”, “up”, and “up” are used in the description.
- the terms “down”, “front”, “rear”, “left”, “right”, “horizontal”, “bottom”, “inner”, “outer” and other terms are all used with reference to this position, just for ease of description
- the present disclosure and simplified description do not indicate or imply that the device or element referred to must have a specific orientation, and a specific orientation structure and operation. It should be understood that the present disclosure can be manufactured and stored in an orientation different from the stated position. , Delivery, use and sale.
- the double-connected axial piston motor includes two sliding plates.
- the flow distribution sliding plate sub-assembly includes a swash plate 40 and a sliding plate 50 supported on the swash plate 40, the sliding plate 50 is an integral structure.
- the opposite end of the sliding plate 50 and the swash plate 40 is provided with a static pressure support surface 51, and the sliding plate 50 is provided with a plurality of plunger ball sockets 58 distributed on one end surface.
- One end of the plunger 70 is placed in the plunger ball socket 58, and the other end Inserted into the cylinder 80, one end of the plunger center hole 72 inside the plunger 70 communicates with the oil through hole 53, and the other end communicates with the plunger hole 81 in the cylinder 80.
- the swash plate 40 is provided with Portion oil groove 42.
- the swashplates 40 of the two sliding plate type non-through shaft plunger motors are supported on a common end seat 33.
- the port flow groove 42 and the oil inlet 33a and the oil outlet provided on the end seat 33 33b is connected, the high-pressure oil flows through the distribution oil groove 42 on the swash plate 40, the oil chamber 53a of the sliding plate 50 and the oil through hole 53, the large-diameter plunger center hole 72, and the cylinder plunger hole 81 to drive the cylinder 80 and The main shaft 10 rotates.
- the large pore diameters in the large-diameter oil through hole 53 and the large-diameter plunger center hole 72 are relative to the pore diameter of the corresponding part in another structure, and the pore diameter in this structure is slender. Hole diameter, only a small part of the high-pressure oil in the plunger hole passes through this hole, and the oil pressure is reduced under the action of the slender pore diameter. Therefore, the pore diameter in the structure with the slender pore diameter is mainly used for throttling and For decompression, the large-aperture oil through hole 53 and the large-aperture plunger center hole 72 in the present disclosure are used as the main oil hole structure.
- the pore diameter of the oil through hole 53 is increased to be similar to or consistent with the widthwise dimension of the waist-shaped oil chamber 53a compared with the pore diameter of the corresponding part in the above-mentioned slender pore structure.
- the end seat 33 is arranged in the middle, and each of the left and right sides has a sliding plate type non-through shaft plunger motor.
- the sliding plate on the left and right sides The non-through shaft plunger motor is a symmetrical structure.
- the sliding disc type non-through shaft plunger motors on the left and right sides share one end seat 33, which is used to close one end opening of the motor housing on both sides, and the sliding disc type non-through shaft plunger motors on the left and right sides and the end seat 33 is connected by bolts. Since the sliding plate type non-through shaft plunger motors on both sides of the end seat are similar in structure, for simple description, the sliding plate type non-through shaft plunger motor on one side is taken as an example.
- the shells of the sliding disc type non-thru-shaft plunger motors on the left and right sides can be set in a double-piece structure or an integral structure.
- the shell includes a front shell 31 and a shell body 32.
- the front shell 31 has a first cavity 34 for accommodating the first bearing 21, and the housing body 32 has a second cavity 35 for accommodating the cylinder and the valve sliding plate pair.
- the housing of the axial piston motor can also be configured as an integral structure, that is, the motor front shell 31 and the shell body 32 can be made into an integral structure, as shown in FIGS. 11 to 14.
- the end seat 33 is used to close the opening at one end of the shell body 32.
- the end seat 33 is provided with the oil inlet 33a and the oil outlet 33b of the motor, the flow passage 33d communicating with the swash plate distribution oil groove 42 and the supporting swash plate 40 sliding arc surface 33e;
- a variable mechanism for variable swing is provided on the end seat 33, and the variable mechanism includes a slide valve 33c, the Axle pin holes are respectively provided on both sides of the spool valve 33c, and the axle pins 49 on the two opposed swash plates 40 are connected to the same spool valve 33c, and the axle pins 49 can rotate in the axle pin holes.
- the slide valve 33c moves and drives the swash plate 40 together with the slide plate 50 to rotate in the second cavity 35 to realize the synchronous variable of the motors at both ends of the end seat.
- the main shaft 10 is cylindrical and penetrates the first cavity 34 of the motor front housing 31.
- a first bearing 21 is interposed between the main shaft and the motor front housing 31.
- One end of the main shaft 10 extends out of the front housing 31 for external load. , And supported on the motor front housing 31 via a first bearing 21.
- the main shaft axis 10C of the main shaft 10 coincides with the cylinder center axis 80C of the cylinder block 80.
- One end of the main shaft 10 is supported on the first bearing 21, The other end is connected with the cylinder 80 by a key.
- the main shaft 10 cantilever supports the cylinder 80 and rotates synchronously with the cylinder 80.
- the main shaft 10 can rotate freely around its own axis via a first bearing 21.
- the first bearing 21 includes at least A centripetal thrust bearing or thrust bearing 21b is provided with a spindle shoulder 12 on the spindle close to the end of the cylinder 80.
- the spindle shoulder 12 is used to stop the cylinder and act on the axial hydraulic pressure on the cylinder. The force is transmitted to the centripetal thrust bearing or thrust bearing 21b.
- the cylinder 80 has a cylindrical configuration with a circular cross-section in the radial direction, and is accommodated in the second cavity 35 of the housing 32 of the motor.
- the cylinder 80 has a uniform circumferential direction about the central axis 80C of the cylinder.
- a plurality of distributed plunger holes 81 and a spindle assembly hole 82 at the center for accommodating the spindle, the plunger hole 81 of the cylinder 80 is a blind hole structure with one end closed and one end open.
- the number of the plunger holes is generally set to 7 or 9
- the spindle 10 passes through the spindle assembly hole 82 of the cylinder body 80 and is connected to the cylinder body 80 by a key connection on the outer circumference of the shaft body, so The cylinder 80 is supported on the main shaft 10 in a manner that it moves synchronously with the main shaft 10.
- the end of the cylinder 80 abuts on the main shaft shoulder 12 and rotates synchronously with the main shaft.
- the axial hydraulic pressure and central spring force are transmitted to the radial thrust ball bearing or tapered roller bearing through the main shaft shoulder 12 Or the thrust bearing 21b, and then to the motor housing.
- the plunger 70 includes a plunger ball 71 with one end supported on the plunger ball socket 58 of the sliding plate 50 and fixed on the end surface of the sliding plate via a pressure plate 60, and a post for communicating the plunger hole 81 and the plunger ball socket 58
- the central hole 72 of the plug, the conical rod portion 73 with a conical outer peripheral surface, and the plunger portion 74 that is clearance fit with the cylinder plunger hole wall and can reciprocate therebetween.
- the plunger ball head 71 is spherical and slidably supported on the plunger ball socket 58 of the sliding plate 50.
- the plunger center hole 72 has a large-diameter through-hole structure, which serves as a channel for sucking and discharging oil.
- the plunger portion 74 is often provided with at least one sealing ring for sealing the liquid.
- the tapered rod portion 73 has a tapered shape that gradually increases from the ball end of the plunger to the plunger portion 74.
- the plunger 70 moves to a certain position At this time, the tapered rod portion 74 is in contact with the inner circumferential surface of the cylinder plunger hole 81 and plays a role of force transmission.
- the plunger 70 is not limited to the conical plunger type, and may also include a connecting rod-plunger with ball heads at both ends or a spherical plunger with a universal hinge.
- the end face of the sliding plate 50 opposite to the swash plate is provided with a static pressure support surface 51, the sliding plate axis 50C and the spindle axis 10C are at a certain angle, and the static pressure support
- the surface 51 is supported on the swash plate 40 and always maintains a sliding fit with the swash plate 40.
- the static pressure support surface 51 is provided with a plurality of lumbar-shaped oil chambers 53a.
- the oil chambers 53a are smooth
- the disc axis 50C is uniformly distributed on the hydrostatic support surface 51 as the center, and the sliding disc 50 is provided with a large-diameter oil through hole 53 that communicates the plunger ball socket 58 and the oil chamber 53a.
- the opposite end surface of the sliding plate 50 and the swash plate 40 is provided with a raised boss surface 52 extending along the axis 50C of the sliding plate to the side of the swash plate 40, and the boss surface 52 is formed by the inner diameter R1 and the outer diameter R1.
- the area enclosed by the diameter R2 is configured so that the boss surface 52 of the sliding plate and the supporting surface of the swash plate 40 abut against each other in a slidable manner.
- a plurality of oil chambers 53a are provided on the boss surface 52 corresponding to the position of the plunger ball socket 58.
- the oil chambers 53a are distributed evenly on a common circumference centered on the sliding disc axis 50C.
- the boss surface 52 is on.
- an effective hydrostatic oil film support is formed between the boss surface 52 and the support surface of the swash plate 40, and the boss surface 52 is provided with a sealing portion for sealing oil, and the sealing portion surrounds the oil chamber
- the state of 53a is set on the inner and outer circumferences of the oil chamber 53a, and the sealing portion includes an inner sealing portion 55 and an outer sealing portion 54 distributed radially inward and outward of the oil chamber 53a, and an interval sealing portion distributed between adjacent oil chambers 53a 56.
- the inner seal portion 55 is an area enclosed by the inner edge of the oil chamber 53a and the inner diameter R1 of the boss surface 52
- the outer seal portion 54 is enclosed by the outer edge of the oil chamber 53a and the outer diameter R2 of the boss surface 52.
- the interval sealing portion 56 is a boss surface area formed by the interval between adjacent oil chambers 53a. A reasonable gap is always maintained between the sealing portion of the boss surface 52 and the supporting surface of the swash plate 40 so that the oil film leakage is at a reasonable level.
- a plurality of plunger ball sockets 58 are provided on the end surface of the sliding plate 50 facing the cylinder block opposite to the plunger 70, and the plunger ball sockets 58 form openings on the end surface of the sliding plate 50.
- a substantially hemispherical recess, the plunger ball sockets 58 support the plunger ball 71 in a state evenly distributed on the common circumference of the spool axis 50C.
- the method for fixing the plunger 70 on the end surface of the sliding plate 50 is not limited to the way of using a pressing plate.
- a form-locking pressing device (not shown) may also be provided on the sliding plate 50, The pressing device can fix the plunger ball head 71 through a covering greater than 180 degrees.
- FIGS. 7-10 show an embodiment of the swash plate.
- the swash plate has a swash plate support surface 41 that matches the static pressure support surface of the swash plate.
- a waist-shaped low pressure distribution window is provided on the swash plate support surface 41.
- 43 and a waist-shaped high-pressure distribution window 44 are divided into two sides by a CC plane passing through the central axis of the swash plate.
- the low-pressure distribution window 43 and the high-pressure distribution window 44 are arranged relative to the central plane CC
- the flow distribution window can be configured as a single or multiple windows having a waist shape.
- the low-pressure distribution window 43 and the high-pressure distribution window 44 can be rotated to a certain angle along the central axis of the swash plate; alternatively, the low-pressure distribution window can also be used.
- the end of the window 43 is provided with a throttle groove or hole that transitions from the low-pressure distribution window 43 to the high-pressure distribution window 44, and at the end of the high-pressure distribution window 44 is provided a throttle groove or hole that transitions from the high-pressure distribution window 44 to the low-pressure distribution window 43.
- High pressure to low pressure or low pressure to high pressure play the role of pre-pressure reduction and pre-boost.
- the supporting surface of the swash plate 40 opposite to the end seat 33 is configured to have a cylindrical supporting surface 45 shaped as a cylinder, and the end seat 33 has a sliding arc surface 33e with the same radius as the cylindrical supporting surface 45 of the swash plate, so that The cylindrical support surface 45 of the swash plate always maintains a close contact state when sliding on the sliding arc surface 33e of the end seat.
- the cylindrical support surface 45 of the swash plate has a groove-shaped low-pressure port 46 and a groove-shaped high-pressure port 47 that are configured in a groove shape.
- the groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the cylindrical support surface 45 are respectively connected to The low pressure distribution window 43 and the high pressure distribution window 44 on the supporting surface 41 on the opposite side of the cylindrical surface of the swash plate are correspondingly communicated.
- the groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the cylindrical support surface 45 are arranged in a symmetrical structure; the groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the cylindrical support surface 45 have a seal
- the sealing band of the notch makes the cylindrical support surface 45 of the swash plate seal oil when sliding on the sliding arc surface 33e of the end seat.
- the end seat 33 is provided with an oil inlet 33a and an oil outlet 33b of the axial piston motor.
- the oil outlet 33b is in communication with the groove-shaped low pressure port 46 on the cylindrical support surface 45.
- the oil inlet 33a Connected with the groove-shaped high-pressure port 47 on the cylindrical support surface 45, the number of the oil inlet 33a and the oil outlet 33b provided on the end seat 33 can be one or two.
- the end seat 33 has only One oil inlet 33a and one oil outlet 33b are provided, so that the motors on the left and right sides share one oil inlet and one oil outlet.
- valve plate 90 is sandwiched between the sliding plate 50 and the swash plate 40 in the valve plate sub-assembly, and the static pressure support surface 51 is supported on the valve plate 90 And maintain a sliding fit with the valve plate 90, the valve plate is fixed on the swash plate by means of pins or the like, the valve plate 90 is provided with a high pressure valve port 93 and a low pressure valve port 92, the high pressure valve port 93 and the low pressure valve plate The ports 92 respectively communicate with the low pressure distribution window 43 and the high pressure distribution window 44 on the swash plate.
- the low-pressure distribution port and the high-pressure distribution port can be arranged in a symmetrical structure relative to the central plane; further, in order to make the distribution plate have a certain pre-boosting and pre-decreasing effect, the low-pressure distribution port and the high-pressure distribution port can be arranged along the distribution plate
- the central axis rotates at a certain angle; alternatively, the direction of transition from the low-pressure port to the high-pressure port and the direction of the transition from the high-pressure port to the low-pressure port can be set on the end of the high-pressure port.
- the throttling groove or hole plays the role of pre-pressure reduction and pre-boosting from high pressure to low pressure or low pressure to high pressure.
- the advantage of sandwiching the valve plate 90 between the sliding plate 50 and the swash plate 40 is that it is easier and cheaper to replace the valve plate later than replacing the swash plate.
- a third bearing 23 is sandwiched between the sliding plate 50 and the swash plate 40 in the flow distribution sliding plate sub-assembly, so that the sliding plate 50 follows its diameter. It is supported on the third bearing 23 in a constrained state, and the valve sliding plate pair of the third bearing 23 is arranged, and its structure is more favorable for stress.
- FIG. 11 and 12 there is shown an embodiment of a series variable axial piston motor supported in the sliding disk.
- a supporting shaft or supporting shaft pin 49 extending outward is provided in the middle of the swash plate 40, and a third bearing 23 is interposed between the swash plate supporting shaft or supporting shaft pin 49 and the inner side of the sliding plate 50, The sliding plate 50 is supported on the third bearing 23 in a state of being constrained in its radial direction.
- the third bearing 23 may be configured to include, but is not limited to, a radial thrust ball bearing, a needle roller bearing, and a cylindrical roller. One of bearings, tapered roller bearings, and radial ball bearings.
- FIG. 13 and 14 there is shown an embodiment of a sliding disc externally supported series variable shaft axial piston motor.
- a third bearing 23 is interposed between the outer circumference of the sliding plate 50 and the inner side of the supporting block 41a, so The sliding plate 50 is supported by the third bearing 23 in a state of being restrained in its radial direction.
- the plunger 70 in the high-pressure zone is acted on by the high-pressure oil pressure from the plunger hole 81 of the cylinder block, and a nearly horizontal hydraulic pressure is exerted on the sliding plate 50 through the plunger ball 71.
- the force pushes the sliding plate 50 toward the swash plate 40 and makes close contact with the end surface of the swash plate 40.
- the end of the swash plate 40 exerts a reaction force on the sliding plate 50.
- the reaction force of the swash plate 40 can be decomposed into a horizontal component force along the spindle axis 10C and
- the lateral component force along the direction perpendicular to the spindle axis 10C has a tendency to move the sliding plate sideways.
- the sliding plate is also subjected to the return force at the central axis, the inertial force (to cancel each other), and the frictional force (not shown), etc.
- the above-mentioned forces constitute the force balance of the sliding plate. It should be noted that the horizontal component force of each force along the axis of the main shaft is balanced with the hydraulic pressure of the plunger 70 acting on the sliding plate 50.
- the lateral component force acting on the sliding plate 50 in the direction perpendicular to the spindle axis 10C can be offset in the sliding plate 50 without being further transmitted to the cylinder 80 via the plunger 70.
- This structure adopting the bearing to support the sliding plate has the following characteristics: the third bearing 23 restricts the movement or movement trend of the sliding plate 50 in the radial direction, and balances the lateral component of the sliding plate 50, so that the sliding plate 50 passes through The lateral force of the plunger 70 on the cylinder 80 is eliminated or greatly reduced, which improves the working reliability, working pressure and working life of the axial piston pump or motor.
- the return structure includes a restraining device provided on the side of the valve sliding plate pair, and the restraining device restricts the slide plate 50 in the return stroke. Keep away from the end face of the swash plate 40 under the action of force.
- the restraining device includes a stop protruding inward on the side of the sliding plate 50 close to the hydrostatic support surface 51
- the portion 57 and the engagement device 140 provided outside the swash plate support shaft or the support shaft pin 49.
- the stop portion 57 is used to stop the movement of the third bearing 23, and the engagement device 140 includes an engagement circumferential groove provided on the outer side of the swash plate support shaft or the support shaft pin 49 and an engagement circumferential groove A circlip (not shown) is provided, and the circlip restricts the sliding plate from moving away from the end surface of the swash plate 40 in a manner of restraining the third bearing 23 from moving outward along the supporting shaft 41.
- the restraining device 140 can also be configured as a combination of a stop portion and a pre-tightening nut (not shown), that is, a thread is provided on the outside of the supporting shaft or the supporting shaft pin 49, and the nut is tightened to restrain the third bearing and sliding The disk is away from the end face of the swash plate.
- the restraining device includes a stop protruding outward on the side of the sliding plate 50 close to the hydrostatic bearing surface 51 Portion 57 and an engagement device 140 provided on the supporting stop portion 41a.
- the stop portion 57 is used to restrict the movement of the third bearing 23, and the engagement device includes an engagement circumferential groove provided on the support stop portion 41a and adjacent to the third bearing 23 and in the engagement
- a retaining spring (not shown) is provided on the circumferential groove, and the retaining spring restricts the sliding plate from moving away from the end surface of the swash plate 40 in a manner of restricting the third bearing 23 to move outward.
- an elastic washer (not shown) can also be appropriately provided between the stop portion 57 and the third bearing 23 or between the circlip and the third bearing 23, so that the restraint assembly can not only restrict the sliding plate from moving away from the swash plate, Outside the end face, there is also a certain initial preload to maintain the preload state of the sliding plate and the swash plate.
- the restraining method of the restraining device 140 can also be realized by the interference fit of the third bearing 23, and the engaging circumferential groove is provided adjacent to the third bearing 23 and the circlip that cooperates with the engaging circumferential groove is further restrained. effect.
- the constraining device 140 is provided on the auxiliary to meet the requirements of the plunger's return stroke. There is no need to add additional pre-tensioning or return components such as a central spring, so that the constraining device greatly simplifies the structure and avoids fatigue damage to the central spring. Phenomena such as fracture.
- the cylinder 80 moves along the main shaft 10 in the direction of the sliding plate, on the main shaft 10, adjacent to the end surface of the cylinder.
- a cylinder circlip 141 is provided to restrict the string movement of the cylinder 80.
- the variable mode of the dual axial piston motor adopts a separate variable.
- the double variable axial plunger motor is provided with two independent variable mechanisms, the variable mechanisms are respectively connected to the housing 32 on both sides of the end seat, the end of the swash plate is provided with a variable connecting portion 38, so The variable connection portions 38 of the swash plate on both sides are respectively connected to the variable mechanism.
- the variable mechanism respectively controls the respective swash plate movement to realize synchronous or asynchronous variable.
- the motors distributed on the left and right sides of the end seat 33 in the dual axial piston motor can have different combinations, including one of the following combinations: 1) The motors on the left and right sides of the end seat 33 are both It is a variable type axial piston motor, as shown in Figures 2 and 3, both ends of the end seat are provided with cylindrical sliding arc surfaces 33e and tightly abutted with the cylindrical support surface 45 of the variable swash plate; 2) the left and right sides of the end seat 33 The motors on the side are all quantitative axial piston motors. As shown in Fig.
- the swash plates 40 on the left and right sides have a fixed inclination angle and are supported on a common end seat 33; 3) the left and right sides of the end seat 33
- One of the motors is a quantitative axial piston motor, and the other is a variable axial piston motor.
- One end of the end seat is provided with a cylindrical sliding arc surface 33e and is in close contact with the cylindrical support surface 45 of the variable swash plate, and the other end is provided
- the plane supporting surface is connected with the swash plate 40 with a fixed angle.
- the beneficial effects of the embodiments of the present disclosure include at least:
- At least one embodiment of the present disclosure connects two sliding plate type non-through shaft plunger motors in series, and the motor power is increased by two times, which can meet the requirements of large displacement, high pressure and high power, and solves the problem of non-through shaft plunger. Motors cannot be connected in series or difficult to connect in series.
- the swash plate is arranged oppositely, and the swash plate is supported on a common end seat, and the swash plate is provided with an oil suction and discharge channel and is connected with
- the connection between the inlet and outlet ports provided on the end seat can greatly simplify the structure, make the size smaller, the structure more compact, and the weight of the motor is smaller, thus increasing its power density per unit mass.
- the dual axial piston motor As the optimized structure of the cylinder is closer to the bearing, the bending moment acting on the cantilever main shaft is reduced, which is more beneficial to the main shaft, the bearing life is longer, and the mechanical noise during operation is smaller.
- At least one embodiment of the present disclosure integrates the functions of flow distribution, variable tilt, and hydrostatic support into the sliding plate pair.
- the main friction pairs are the sliding plate pair and the plunger pair.
- One is that one valve pair is reduced, thereby reducing The leakage of oil improves its efficiency; secondly, the lateral force of the plunger is greatly reduced, which eliminates or reduces the overturning phenomenon of the cylinder. Since there is no valve pair at the end of the cylinder, there are no problems such as wear and leakage at the end of the cylinder. Even if there is a side force that overturns the cylinder, it will not cause problems such as partial wear and failure. At the same time, this structure Makes the life of the cylinder longer, less maintenance later, and reduces the cost of use.
- variable mode of the dual axial plunger motor provided by at least one embodiment of the present disclosure can be set to a centralized and separate variable mode, which can be adapted to different working conditions and each has its own characteristics, of which the centralized variable mode ,
- Two opposite swash plates can be connected to a common slide valve. When the slide valve moves, it can drive the two swash plates to move synchronously.
- This structure only has one variable mechanism, so the structure is simple and the variables are convenient , It is especially advantageous for the situation that requires the simultaneous movement of the two shaft ends of the dual axial piston motor.
- At least one embodiment of the present disclosure integrates the functions of flow distribution, variable tilt, and hydrostatic support in the sliding plate pair. Since the sliding plate ball socket and the plunger ball head can be relatively tilted during the working process, they can be moved automatically It adapts to various situations due to the tilting of the swash plate and the tilting of the cylinder body, so that the sliding plate can always be close to the swash plate to complete the flow distribution, variable, support and other functions; at the same time, it is easier and more convenient to replace the sliding plate or the valve plate than replacing the cylinder. economic.
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Abstract
A duplex axial plunger motor, comprising two slide plate-type non-hollow shaft plunger motors and an end base (33) sandwiched between the two slide plate-type non-hollow shaft plunger motors. Each slide plate-type non-hollow shaft plunger motor comprises a distribution slide plate sub-assembly, a main shaft (10), a cylinder body (80), and a plunger (70). The distribution slide plate sub-assembly comprises a swash plate (40) and a slide plate (50) supported on the swash plate (40). The slide plate (50) is an integral structure, and the end face of the slide plate (50) facing the swash plate (40) is provided with a static pressure bearing surface (51). A plurality of plunger ball sockets (58) are provided on the end face of the slide plate (50) facing the cylinder body (80). An oil through hole (53) communicated with the plunger ball sockets (58) and the static pressure bearing surface (51) is provided on the slide plate (50). The swash plate (40) is provided with a distribution oil groove (42) communicated with oil inlet and outlet (33a, 33b). For the duplex axial plunger motor, the structure is greatly simplified, the number of friction pairs is reduced, and the performance of the axial plunger motor is improved.
Description
本申请要求于2019年3月13日递交的中国专利申请第201910189060.5号的优先权,在此全文引用上述中国专利申请公开的内容以作为本申请的一部分。This application claims the priority of the Chinese patent application No. 201910189060.5 filed on March 13, 2019, and the contents of the above-mentioned Chinese patent application are cited here in full as a part of this application.
本公开的实施例涉及一种轴向柱塞马达,特别涉及一种双联式非通轴柱塞马达。The embodiment of the present disclosure relates to an axial plunger motor, and more particularly to a double-connected non-through shaft plunger motor.
轴向柱塞马达是现代液压传动中使用最广的液压元件之一,其中无铰式斜轴马达和滑履斜盘式轴向柱塞马达是目前应用最广泛、也是最主要的两类轴向柱塞马达。这两种马达目前还在竞争,各自都在不断地改进和发展。The axial piston motor is one of the most widely used hydraulic components in modern hydraulic transmission. Among them, the hingeless inclined axis motor and the sliding shoe swash plate axial piston motor are the two most widely used and most important types of shafts. To the plunger motor. These two motors are still in competition, and each is constantly improving and developing.
发明内容Summary of the invention
本公开的至少一实施例提供一种双联式轴向柱塞马达,包括两个滑盘式非通轴柱塞马达以及夹设在两个滑盘式非通轴柱塞马达之间的端座,每个滑盘式非通轴柱塞马达包含主轴、斜盘、滑盘、柱塞和缸体,所述滑盘为整体结构且支承在斜盘上构成配流滑盘副组件,所述滑盘与斜盘对置的端面设置有静压支承面,所述滑盘与缸体对置的端面设置有多个柱塞球窝,在所述滑盘上设置有连通柱塞球窝和静压支承面的通油孔,所述柱塞一端置于柱塞球窝内,另一端***至缸体内,所述柱塞内部的柱塞中心孔一端与通油孔连通,另一端与缸体内的柱塞孔连通,在所述斜盘上设置有配流油槽,所述两个滑盘式非通轴柱塞马达的斜盘支承在共同的端座上,所述配流油槽与端座上设置的进、出油口连通,高压油液流经斜盘上的配流油槽、通油孔、柱塞中心孔和柱塞孔,驱使缸体和主轴同步旋转。At least one embodiment of the present disclosure provides a dual axial plunger motor, including two sliding plate non-through shaft plunger motors and a terminal sandwiched between the two sliding plate non-through shaft plunger motors Each sliding plate type non-through shaft plunger motor includes a main shaft, a swash plate, a sliding plate, a plunger and a cylinder. The sliding plate is an integral structure and is supported on the swash plate to form a flow distribution sliding plate sub-assembly. The end surface of the sliding plate opposite to the swash plate is provided with a static pressure support surface, the end surface of the sliding plate opposite to the cylinder is provided with a plurality of plunger ball sockets, and the sliding plate is provided with a connecting plunger ball socket and The oil through hole of the hydrostatic bearing surface, one end of the plunger is placed in the plunger ball socket, the other end is inserted into the cylinder, one end of the plunger center hole inside the plunger is connected to the oil through hole, and the other end is connected to the The plunger hole in the cylinder communicates with the swash plate. The swash plate of the two sliding plate type non-through shaft plunger motors is supported on a common end seat. The flow distribution oil groove and the end The oil inlet and outlet ports set on the seat are connected, and the high-pressure oil flows through the distribution oil groove, the oil through hole, the plunger center hole and the plunger hole on the swash plate to drive the cylinder body and the main shaft to rotate synchronously.
例如,在本公开一实施例提供的双联式轴向柱塞马达中,所述滑盘的静压支承面上设有多个油室,所述油室以滑盘轴心为中心间隔地分布在所 述静压支承面上,在每个油室底部与对应柱塞球窝之间设置有通油孔,所述通油孔作为吸排油液的主通道并将油液引入静压支承面与斜盘之间,使所述静压支承面与斜盘端面形成间隙配合的静压油膜支承。For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, a plurality of oil chambers are provided on the hydrostatic bearing surface of the sliding plate, and the oil chambers are spaced apart from the axis of the sliding plate. Distributed on the static pressure support surface, an oil through hole is provided between the bottom of each oil chamber and the corresponding plunger ball socket. The oil through hole serves as the main channel for sucking and discharging oil and introduces the oil into the static pressure support Between the surface and the swash plate, the static pressure supporting surface and the end surface of the swash plate form a static pressure oil film support with clearance fit.
例如,在本公开一实施例提供的双联式轴向柱塞马达中,在所述凸台面上设置有用于密封油液的密封部,所述密封部包括设置在油室径向内外侧的内密封部和外密封部,以及设置在相邻油室之间的间隔密封部。For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, a sealing portion for sealing oil is provided on the boss surface, and the sealing portion includes a radially inner and outer side of the oil chamber. The inner sealing part and the outer sealing part, and the interval sealing part arranged between adjacent oil chambers.
例如,在本公开一实施例提供的双联式轴向柱塞马达中,在所述静压支承面上设置有多个油室,所述斜盘上与滑盘对置的端面上设置有低压配流窗口和高压配流窗口,所述高、低压配流窗口与油室间歇地连通,所述斜盘上与端座对置的支承面具有成形为圆柱形的圆柱支承面,所述斜盘的圆柱支承面上具有构形为槽形的槽形低压口和槽形高压口,所述槽形低压口和槽形高压口分别与低压配流窗口和高压配流窗口对应连通。For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, a plurality of oil chambers are provided on the static pressure supporting surface, and the end surface of the swash plate opposite to the sliding plate is provided with The low-pressure distribution window and the high-pressure distribution window are intermittently communicated with the oil chamber. The supporting surface on the swash plate opposite to the end seat has a cylindrical supporting surface formed into a cylindrical shape. The cylindrical supporting surface is provided with a groove-shaped low-pressure port and a groove-shaped high-pressure port that are configured in a groove shape, and the groove-shaped low-pressure port and the groove-shaped high-pressure port are respectively communicated with the low-pressure distribution window and the high-pressure distribution window.
例如,在本公开一实施例提供的双联式轴向柱塞马达中,所述滑盘上的通油孔以及柱塞上的柱塞中心孔均为大孔径且作为吸排油的主油孔结构。For example, in a dual axial plunger motor provided by an embodiment of the present disclosure, the oil through hole on the sliding plate and the plunger center hole on the plunger are both large-diameter main oil holes for sucking and discharging oil. structure.
例如,在本公开一实施例提供的双联式轴向柱塞马达中,所述轴向柱塞马达设置为集中变量式结构,所述端座上设置有包含一个滑阀的变量机构,两个对置斜盘的轴销连接在共同的滑阀上,在变量机构的液压力和弹簧力作用下,所述滑阀带动两个斜盘做同步转动,实现同步变量。For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, the axial plunger motor is configured as a centralized variable structure, and the end seat is provided with a variable mechanism including a spool valve, two The shaft pins of the two opposite swash plates are connected to a common slide valve. Under the action of the hydraulic pressure and spring force of the variable mechanism, the slide valve drives the two swash plates to rotate synchronously to realize synchronous variable.
例如,在本公开一实施例提供的双联式轴向柱塞马达中,所述轴向柱塞马达设置为分开变量式结构,在所述轴向柱塞马达的壳体上连接有两个变量机构,所述变量机构分别与对应的斜盘连接,在各自变量机构的液压力和弹簧力作用下,实现独立变量。For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, the axial plunger motor is configured as a separate variable structure, and the housing of the axial plunger motor is connected with two Variable mechanism, the variable mechanism is respectively connected with the corresponding swash plate, and realizes independent variable under the action of hydraulic pressure and spring force of the respective variable mechanism.
例如,在本公开一实施例提供的双联式轴向柱塞马达中,分布在端座两侧的滑盘式非通轴柱塞马达以斜盘变量方式组合,其具体组合方式为两侧滑盘式非通轴柱塞马达均为变量式结构;或者两侧滑盘式非通轴柱塞马达均为定量式结构;或者两侧滑盘式非通轴柱塞马达一个为定量式结构、另一个为变量式结构。For example, in a dual axial plunger motor provided by an embodiment of the present disclosure, the sliding plate type non-through shaft plunger motors distributed on both sides of the end seat are combined in a variable manner of swash plate, and the specific combination method is two sides Slip-disk type non-thru-shaft plunger motors are of variable type structure; or both sides-slip-disk type non-thru-shaft plunger motors are of quantitative structure; or slide-plate type non-thru-shaft plunger motors on both sides are of quantitative structure , The other is a variable structure.
例如,在本公开一实施例提供的双联式轴向柱塞马达中,所述两个滑盘式非通轴柱塞马达的主轴一端伸出壳体并支承在第一轴承上,其另一端端部悬臂支承缸体并与缸体同步旋转,所述缸体的柱塞孔为一端封闭、一 端开口的结构,在所述缸体的封闭端端部不设置配流副,所述主轴和缸体在旋转工作时,液压轴向力通过缸体经第一轴承传递至壳体上。For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, one end of the main shaft of the two sliding disc type non-through shaft plunger motors extends out of the housing and is supported on the first bearing, and the other One end cantilever supports the cylinder body and rotates synchronously with the cylinder body. The plunger hole of the cylinder body is a structure with one end closed and one end open. The closed end of the cylinder body is not provided with a distribution pair. The main shaft and When the cylinder is rotating, the hydraulic axial force is transmitted to the housing through the cylinder through the first bearing.
例如,在本公开一实施例提供的双联式轴向柱塞马达中,支承所述主轴的第一轴承至少包含一个向心推力轴承或推力轴承,工作时,液压轴向力作用在柱塞孔封闭一端的缸体端面并经所述第一轴承传递至柱塞泵或马达的壳体上。For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, the first bearing supporting the main shaft includes at least one centripetal thrust bearing or thrust bearing, and hydraulic axial force acts on the plunger during operation. The hole closes the end surface of the cylinder at one end and is transmitted to the casing of the plunger pump or the motor through the first bearing.
例如,在本公开一实施例提供的双联式轴向柱塞马达中,在所述斜盘和滑盘之间夹设有第三轴承,所述滑盘以沿其径向受约束的状态支承在第三轴承上。For example, in a dual axial piston motor provided by an embodiment of the present disclosure, a third bearing is interposed between the swash plate and the sliding plate, and the sliding plate is in a state of being restricted in its radial direction. Supported on the third bearing.
例如,在本公开一实施例提供的双联式轴向柱塞马达中,所述斜盘中部具有向外延伸的支承轴或支承轴销,所述滑盘设置有中心通孔,所述第三轴承夹设在滑盘中心通孔内壁与支承轴或支承轴销之间,所述滑盘以沿其径向受约束状态支承在第三轴承上。For example, in the dual axial piston motor provided by an embodiment of the present disclosure, the middle part of the swash plate has a supporting shaft or a supporting shaft pin extending outward, the sliding plate is provided with a central through hole, and the first The three bearings are sandwiched between the inner wall of the central through hole of the sliding plate and the supporting shaft or the supporting shaft pin, and the sliding plate is supported on the third bearing in a state of being restrained in the radial direction.
例如,在本公开一实施例提供的双联式轴向柱塞马达中,所述斜盘外周部设置有凸起的支承挡部,所述第三轴承夹设在滑盘外侧与支承挡部内侧之间,所述滑盘以沿其径向受约束状态支承在第三轴承上。For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, the outer periphery of the swash plate is provided with a raised support stop, and the third bearing is sandwiched between the outer side of the swash plate and the support stop. Between the inner sides, the sliding plate is supported on the third bearing in a state of being restrained in its radial direction.
例如,在本公开一实施例提供的双联式轴向柱塞马达中,所述柱塞包含带锥形结构的连杆柱塞或者两端均设置有球头的连杆柱塞或者带万向铰的球面柱塞的一种,所述柱塞一端可相对缸体往复滑动的方式***缸体的柱塞孔内,另一端以相对滑盘端面远离受限且能够倾动的状态固定在滑盘的柱塞球窝内,所述柱塞上设置有连通柱塞球窝和柱塞孔的大孔径柱塞中心孔。For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, the plunger includes a connecting rod plunger with a tapered structure or a connecting rod plunger with a ball head or a belt on both ends. A type of spherical plunger with a hinge, one end of the plunger can be inserted into the plunger hole of the cylinder in a reciprocating manner relative to the cylinder, and the other end is fixed on the sliding plate in a state where the distance from the end surface of the sliding plate is restricted and can be tilted. In the plunger ball socket of the disc, the plunger is provided with a large-aperture plunger center hole communicating the plunger ball socket and the plunger hole.
例如,在本公开一实施例提供的双联式轴向柱塞马达中,所述滑盘与斜盘之间夹设有配流盘,所述滑盘支承在配流盘上且与配流盘保持滑动配合,所述配流盘上设置有高、低压配流口,高压油液流经斜盘上的配流油槽、配流盘的配流口、滑盘的油室、通油孔、柱塞中心孔和缸体柱塞孔,驱使缸体和主轴同步旋转。For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, a valve plate is sandwiched between the sliding plate and the swash plate, and the sliding plate is supported on the valve plate and kept sliding with the valve plate In cooperation, the valve plate is provided with high and low pressure valve ports, and the high pressure oil flows through the valve oil groove on the swash plate, the valve port of the valve plate, the oil chamber of the sliding plate, the oil through hole, the center hole of the plunger and the cylinder block. The plunger hole drives the cylinder body and the spindle to rotate synchronously.
图1为一种斜盘式非通轴柱塞马达的结构示意图;Figure 1 is a schematic diagram of a swash plate type non-through shaft plunger motor;
图2为本公开中双联集中变量轴向柱塞马达的一种实施例;Fig. 2 is an embodiment of the double-joint concentrated variable axial piston motor in the present disclosure;
图3为本公开中图2轴向柱塞马达的A-A剖面图;Figure 3 is a cross-sectional view of the axial plunger motor A-A of Figure 2 in this disclosure;
图4为本公开中滑盘一端的平面图;Figure 4 is a plan view of one end of the sliding plate in this disclosure;
图5为本公开中图4中滑盘的B-B剖面图;Fig. 5 is a B-B sectional view of the sliding plate in Fig. 4 in this disclosure;
图6为本公开中滑盘另一端的平面图;Figure 6 is a plan view of the other end of the sliding plate in this disclosure;
图7为本公开中与滑盘对置的斜盘一端支承面的一种平面图;7 is a plan view of the supporting surface of one end of the swash plate opposite to the sliding plate in the present disclosure;
图8为本公开中与滑盘对置的斜盘一端支承面的另一种平面图;Figure 8 is another plan view of the supporting surface of one end of the swash plate opposite to the sliding plate in the present disclosure;
图9为本公开中与端座对置的斜盘的平面图;Figure 9 is a plan view of the swash plate opposite to the end seat in this disclosure;
图10为本公开中图9斜盘的D-D剖面图;Figure 10 is a D-D cross-sectional view of the swash plate of Figure 9 in this disclosure;
图11为本公开中采用滑盘内支承方式的双联集中变量轴向柱塞马达实施例;FIG. 11 is an embodiment of a double-connected concentrated variable axial piston motor adopting a sliding disk internal support method in this disclosure;
图12为本公开中图11中轴向柱塞马达的E-E剖面图;Fig. 12 is an E-E sectional view of the axial piston motor in Fig. 11 in this disclosure;
图13为本公开中采用滑盘外支承方式的双联集中变量轴向柱塞马达实施例;FIG. 13 is an embodiment of a dual concentrated variable axial plunger motor adopting a sliding disk external support method in this disclosure;
图14为本公开中双联分开变量轴向柱塞马达的实施例;Fig. 14 is an embodiment of the double-coupled split variable axial piston motor in this disclosure;
图15为本公开中包含配流盘的滑盘式非通轴柱塞马达的剖面图;以及15 is a cross-sectional view of a sliding plate type non-through shaft plunger motor including a valve plate in this disclosure; and
图16为本公开中定量滑盘式轴向柱塞马达的结构示意图。FIG. 16 is a schematic diagram of the structure of the quantitative sliding disc type axial piston motor in this disclosure.
附图标记:10为主轴,10C为主轴轴心,12为主轴挡肩,21为第一轴承,21a为向心球轴承,21b为向心推力轴承或推力轴承,22为第二轴承,23为第三轴承,31为前壳,32为壳身,33为端座,33a为进油口,33b为出油口,33c为滑阀,33d为流道,33e为滑弧面,34为第一空腔,35为第二空腔,38变量连接部,40为斜盘,41为斜盘支承面,41a支承挡部,42为配流油槽,43为低压配流窗口,44为高压配流窗口,45为圆柱支承面,46为槽形低压口,47为槽形高压口,48为连通槽口,49为支承轴销,50为滑盘,50C为滑盘轴心,51为静压支承面,52为凸台面,53为通油孔,53a为油室,54为外密封部,55为内密封部,56为间隔密封部,58为柱塞球窝,60为压板,70为柱塞,71为柱塞球头,72为柱塞中心孔,73为锥形杆部,74为柱塞部,80为缸体,81为柱塞孔,82为主轴装配孔,84为缸套,80C为缸体中心轴心,90为配流盘,91配流支承面,92为低压配流口,93为高压配流口,100为中心弹簧,101为钢球,102为套筒,103为外套,120为滑靴,130为回程盘,140为卡合装置, 141为缸体卡簧。Reference signs: 10 is the spindle, 10C is the spindle axis, 12 is the spindle shoulder, 21 is the first bearing, 21a is the radial ball bearing, 21b is the radial thrust bearing or thrust bearing, 22 is the second bearing, 23 Is the third bearing, 31 is the front shell, 32 is the shell body, 33 is the end seat, 33a is the oil inlet, 33b is the oil outlet, 33c is the spool valve, 33d is the flow channel, 33e is the sliding surface, 34 is The first cavity, 35 is the second cavity, 38 is the variable connection part, 40 is the swash plate, 41 is the support surface of the swash plate, 41a is the support block, 42 is the distribution oil groove, 43 is the low pressure distribution window, 44 is the high pressure distribution window , 45 is a cylindrical support surface, 46 is a groove-shaped low-pressure port, 47 is a groove-shaped high-pressure port, 48 is a connecting slot, 49 is a supporting shaft pin, 50 is a sliding plate, 50C is a sliding plate axis, and 51 is a hydrostatic support Surface, 52 is the boss surface, 53 is the oil through hole, 53a is the oil chamber, 54 is the outer sealing part, 55 is the inner sealing part, 56 is the interval sealing part, 58 is the plunger ball socket, 60 is the pressure plate, 70 is the column Plug, 71 is the plunger ball head, 72 is the plunger center hole, 73 is the tapered rod, 74 is the plunger, 80 is the cylinder, 81 is the plunger hole, 82 is the spindle assembly hole, and 84 is the cylinder liner , 80C is the central axis of the cylinder, 90 is the valve plate, 91 is the support surface of the valve, 92 is the low pressure valve, 93 is the high pressure valve, 100 is the central spring, 101 is the steel ball, 102 is the sleeve, and 103 is the outer jacket. 120 is a sliding shoe, 130 is a return disk, 140 is a clamping device, and 141 is a cylinder circlip.
如图1所示,为一种非通轴式斜盘式轴向柱塞马达的典型结构,包含斜盘40、滑靴120、柱塞70、缸体80、配流盘90、主轴10、中心弹簧100、回程盘130等部件,主轴10一端支承在一端轴承上,另一端贯通配流盘90并与缸体80通过键连接,中心弹簧100通过套筒102、钢球101将所述滑靴120压紧,中心弹簧100通过外套103将缸体与配流盘压紧,在缸体80外周面设置有缸套84,在缸套84与马达壳身32之间夹设有第二轴承22。As shown in Figure 1, it is a typical structure of a non-through shaft swash plate type axial piston motor, which includes a swash plate 40, a sliding shoe 120, a plunger 70, a cylinder 80, a valve plate 90, a main shaft 10, and a center Spring 100, return plate 130 and other components. One end of the main shaft 10 is supported on a bearing at one end, and the other end penetrates the valve plate 90 and is connected to the cylinder block 80 by a key. The central spring 100 connects the sliding shoe 120 through the sleeve 102 and the steel ball 101. After pressing, the central spring 100 compresses the cylinder block and the valve plate through the outer sleeve 103, a cylinder liner 84 is provided on the outer peripheral surface of the cylinder block 80, and a second bearing 22 is interposed between the cylinder liner 84 and the motor housing 32.
这种非通轴斜盘式轴向柱塞马达的缺点是:一是,在液压力作用下,轴向柱塞马达的斜盘对柱塞产生的侧向力较大,该侧向分力经由柱塞传递至缸体、主轴,造成缸体和配流盘之间出现楔形间隙,增加了马达的功率损失,并使缸体与配流盘之间的密封面产生局部接触,造成缸体和配流盘之间的表面烧伤,进而使得马达完全丧失功能;二是,组成串联马达困难,尤其是大功率的高压大流量串联变量轴向柱塞马达较难实现;三是,外形结构尺寸较大,噪音偏高。The disadvantages of this kind of non-through shaft swash plate axial plunger motor are: First, under the action of hydraulic pressure, the swash plate of the axial plunger motor produces a large lateral force on the plunger, and the lateral component force It is transmitted to the cylinder block and the main shaft via the plunger, causing a wedge-shaped gap between the cylinder block and the valve plate, which increases the power loss of the motor, and makes the sealing surface between the cylinder block and the valve plate come into partial contact, causing the cylinder block and the valve plate. The surface between the disks is burned, which makes the motor completely lose its function; second, it is difficult to form a series motor, especially the high-power, high-pressure and large-flow series variable axial piston motor is difficult to achieve; third, the external structure is large, The noise is high.
随着大型机械对高压大排量轴向柱塞马达的日益需求,这种传统的单个非通轴斜盘式轴向柱塞马达,无论是从排量、功率方面,还是从结构的可靠性均无法满足其要求。With the increasing demand of large-scale machinery for high-pressure and large-displacement axial piston motors, this traditional single non-through shaft swash plate axial piston motor, whether in terms of displacement, power, or structural reliability Neither can meet its requirements.
本公开的目的在于:针对非通轴式轴向柱塞马达无法串联、可靠性不高、尺寸偏大等存在的问题,提供一种双联式轴向柱塞马达,旨在满足现代大型机械对大功率、高压大流量、结构紧凑、可靠性高的液压马达的需求。The purpose of the present disclosure is to provide a dual axial piston motor in view of the problems of non-thru-shaft axial piston motors that cannot be connected in series, are low in reliability, and are too large in size. Demand for hydraulic motors with high power, high pressure and large flow, compact structure and high reliability.
下面结合附图,对本公开的实施例作详细的说明。The following describes the embodiments of the present disclosure in detail with reference to the accompanying drawings.
尽管本公开容许有不同形式的实施例,但本说明书和附图仅仅公开了如本公开的示例的一些特定形式。然而本公开并不试图限于所述的实施例。本公开的范围在所附的权利要求中给出。Although the present disclosure allows embodiments in different forms, this specification and drawings only disclose some specific forms as examples of the present disclosure. However, the present disclosure is not intended to be limited to the described embodiments. The scope of the present disclosure is given in the appended claims.
为了方便描述,本公开的实施例以典型的取向示出,所述取向使得当轴向柱塞马达的主轴的中心轴线水平静置,描述中使用的“纵向”、“横向”“上”、“下”、“前”、“后”、“左”、“右”“水平”、“底”、“内”、“外”等术语都是参照这个位置而使用的,仅是为了便于描述本公开和简化描述,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、以及特定的方位构造和操 作,应理解的是本公开可以不同于所述的位置的取向进行制造、存放、运送、使用和销售。For the convenience of description, the embodiments of the present disclosure are shown in a typical orientation, the orientation is such that when the central axis of the spindle of the axial plunger motor stands horizontally, “longitudinal”, “lateral”, “up”, and “up” are used in the description. The terms "down", "front", "rear", "left", "right", "horizontal", "bottom", "inner", "outer" and other terms are all used with reference to this position, just for ease of description The present disclosure and simplified description do not indicate or imply that the device or element referred to must have a specific orientation, and a specific orientation structure and operation. It should be understood that the present disclosure can be manufactured and stored in an orientation different from the stated position. , Delivery, use and sale.
实施例1:Example 1:
如图2-10所示,为本公开的双联式集中变量滑盘式轴向柱塞马达的实施例,在所示的优选实施例中,双联式轴向柱塞马达包含两个滑盘式非通轴柱塞马达以及夹设在两个滑盘式非通轴柱塞马达之间的端座33,每个滑盘式非通轴柱塞马达包含配流滑盘副组件、主轴10、悬臂支承在主轴10一端上且与主轴10同步转动的缸体80和柱塞70,所述配流滑盘副组件包含斜盘40以及支承在斜盘40上的滑盘50,所述滑盘50为整体结构,所述滑盘50与斜盘40对置的端面设置有静压支承面51,所述滑盘50上设置有分布在一侧端面上的多个柱塞球窝58、分布在另一侧端面上的多个油室53a以及连通所述柱塞球窝58和油室53a的大孔径通油孔53,所述柱塞70一端置于柱塞球窝58内,另一端***至缸体80内,所述柱塞70内部的柱塞中心孔72一端与通油孔53连通,另一端与缸体80内的柱塞孔81连通,在所述斜盘40上设置有配流油槽42,所述两个滑盘式非通轴柱塞马达的斜盘40支承在共同的端座33上,所述配流油槽42与端座33上设置的进油口33a和出油口33b连通,高压油液流经斜盘40上的配流油槽42、滑盘50的油室53a及通油孔53、大孔径柱塞中心孔72、缸体柱塞孔81,驱使缸体80和主轴10旋转。As shown in Figures 2-10, this is an embodiment of the double-connected centralized variable sliding plate type axial piston motor of the present disclosure. In the preferred embodiment shown, the double-connected axial piston motor includes two sliding plates. A disc type non-through shaft plunger motor and an end seat 33 sandwiched between two sliding disc type non-through shaft plunger motors, each sliding disc type non-through shaft plunger motor includes a flow distribution sliding plate sub-assembly and a main shaft 10 , A cylinder 80 and a plunger 70 cantilever supported on one end of the main shaft 10 and rotating synchronously with the main shaft 10, the flow distribution sliding plate sub-assembly includes a swash plate 40 and a sliding plate 50 supported on the swash plate 40, the sliding plate 50 is an integral structure. The opposite end of the sliding plate 50 and the swash plate 40 is provided with a static pressure support surface 51, and the sliding plate 50 is provided with a plurality of plunger ball sockets 58 distributed on one end surface. A plurality of oil chambers 53a on the other end surface and a large-diameter oil through hole 53 connecting the plunger ball socket 58 and the oil chamber 53a. One end of the plunger 70 is placed in the plunger ball socket 58, and the other end Inserted into the cylinder 80, one end of the plunger center hole 72 inside the plunger 70 communicates with the oil through hole 53, and the other end communicates with the plunger hole 81 in the cylinder 80. The swash plate 40 is provided with Portion oil groove 42. The swashplates 40 of the two sliding plate type non-through shaft plunger motors are supported on a common end seat 33. The port flow groove 42 and the oil inlet 33a and the oil outlet provided on the end seat 33 33b is connected, the high-pressure oil flows through the distribution oil groove 42 on the swash plate 40, the oil chamber 53a of the sliding plate 50 and the oil through hole 53, the large-diameter plunger center hole 72, and the cylinder plunger hole 81 to drive the cylinder 80 and The main shaft 10 rotates.
其中,需要说明的是所述大孔径通油孔53和大孔径柱塞中心孔72中的大孔径是相对于另外一种结构中对应部位孔径的大小而言,该结构中的孔径为细长孔径,柱塞孔中的高压油液只有小部分经过此孔,且在细长孔径的作用下,油液压力降低,因此该采用细长孔径的结构中的孔径对油液主要起节流、减压作用,本公开中的大孔径通油孔53和大孔径柱塞中心孔72作为主油孔结构,液压油的吸入和排出均流经此主油孔结构,油液经过大孔径通油孔53和大孔径柱塞中心孔72无明显压降,因此其结构具有本质区别。具体地,在本公开的实施例中,所述通油孔53的孔径相比上述采用细长孔径的结构中对应部位的孔径增大至与腰形油室53a的宽度方向尺寸相近或一致。Among them, it should be noted that the large pore diameters in the large-diameter oil through hole 53 and the large-diameter plunger center hole 72 are relative to the pore diameter of the corresponding part in another structure, and the pore diameter in this structure is slender. Hole diameter, only a small part of the high-pressure oil in the plunger hole passes through this hole, and the oil pressure is reduced under the action of the slender pore diameter. Therefore, the pore diameter in the structure with the slender pore diameter is mainly used for throttling and For decompression, the large-aperture oil through hole 53 and the large-aperture plunger center hole 72 in the present disclosure are used as the main oil hole structure. Both suction and discharge of hydraulic oil flow through this main oil hole structure, and the oil passes through the large-aperture oil hole. There is no significant pressure drop between the hole 53 and the central hole 72 of the large-aperture plunger, so their structures are essentially different. Specifically, in the embodiment of the present disclosure, the pore diameter of the oil through hole 53 is increased to be similar to or consistent with the widthwise dimension of the waist-shaped oil chamber 53a compared with the pore diameter of the corresponding part in the above-mentioned slender pore structure.
如图2所示,所述双联式轴向柱塞马达实施例中,端座33设置在中部,左右两边各具有一个滑盘式非通轴柱塞马达,特殊地,左右两边的滑盘式非通轴柱塞马达为对称结构。左右两边的滑盘式非通轴柱塞马达共用一个端座33,所述端座33用于封闭两边马达壳体的一端开口,左右两侧的滑盘式非 通轴柱塞马达与端座33通过螺栓固定连接。由于端座两侧的滑盘式非通轴柱塞马达结构相似,为简便说明,以其中一边的滑盘式非通轴柱塞马达为例进行说明。As shown in Figure 2, in the embodiment of the dual axial plunger motor, the end seat 33 is arranged in the middle, and each of the left and right sides has a sliding plate type non-through shaft plunger motor. In particular, the sliding plate on the left and right sides The non-through shaft plunger motor is a symmetrical structure. The sliding disc type non-through shaft plunger motors on the left and right sides share one end seat 33, which is used to close one end opening of the motor housing on both sides, and the sliding disc type non-through shaft plunger motors on the left and right sides and the end seat 33 is connected by bolts. Since the sliding plate type non-through shaft plunger motors on both sides of the end seat are similar in structure, for simple description, the sliding plate type non-through shaft plunger motor on one side is taken as an example.
左右两侧的滑盘式非通轴柱塞马达的壳体可设置为双体式结构或整体式结构,当壳体设置为双体式结构时,壳体包含前壳31和壳身32,前壳31具有用于容纳第一轴承21的第一空腔34,所述壳身32具有用于容纳缸体和用于容纳所述配流滑盘副的第二空腔35。特殊地,轴向柱塞马达的壳体也可以设置为整体式结构,即可将马达前壳31和壳身32做成一体式结构,如图11至图14所示。The shells of the sliding disc type non-thru-shaft plunger motors on the left and right sides can be set in a double-piece structure or an integral structure. When the shell is set in a double-piece structure, the shell includes a front shell 31 and a shell body 32. The front shell 31 has a first cavity 34 for accommodating the first bearing 21, and the housing body 32 has a second cavity 35 for accommodating the cylinder and the valve sliding plate pair. In particular, the housing of the axial piston motor can also be configured as an integral structure, that is, the motor front shell 31 and the shell body 32 can be made into an integral structure, as shown in FIGS. 11 to 14.
其中,所述端座33用于封闭壳身32的一端开口,端座33上设置有马达的进油口33a和出油口33b、与斜盘配流油槽42连通的流道33d以及支承斜盘40的滑弧面33e;当轴向柱塞马达设置为集中变量式轴向柱塞马达时,在端座33上设置有用于变量摆动的变量机构,所述变量机构包含滑阀33c,所述滑阀33c两侧分别设置有轴销孔,所述对置的两个斜盘40上的轴销49共同连接在同一滑阀33c上,所述轴销49可在轴销孔内转动。在变量机构的作用下,滑阀33c发生移动并带动所述斜盘40连同滑盘50在第二空腔35内转动,实现端座两端的马达同步变量。这种结构的好处在于可只设置一个变量机构,实现两个串联马达的一起变量,因此结构简单,变量方便,尤其是对于要求双联式轴向柱塞马达两轴端同步运动的情况特别具有优势。Wherein, the end seat 33 is used to close the opening at one end of the shell body 32. The end seat 33 is provided with the oil inlet 33a and the oil outlet 33b of the motor, the flow passage 33d communicating with the swash plate distribution oil groove 42 and the supporting swash plate 40 sliding arc surface 33e; when the axial piston motor is set as a centralized variable type axial piston motor, a variable mechanism for variable swing is provided on the end seat 33, and the variable mechanism includes a slide valve 33c, the Axle pin holes are respectively provided on both sides of the spool valve 33c, and the axle pins 49 on the two opposed swash plates 40 are connected to the same spool valve 33c, and the axle pins 49 can rotate in the axle pin holes. Under the action of the variable mechanism, the slide valve 33c moves and drives the swash plate 40 together with the slide plate 50 to rotate in the second cavity 35 to realize the synchronous variable of the motors at both ends of the end seat. The advantage of this structure is that only one variable mechanism can be set to realize the same variable of the two serial motors, so the structure is simple and the variables are convenient, especially for the situation that requires the simultaneous movement of the two shaft ends of the dual axial piston motor. Advantage.
所述主轴10呈圆柱状并贯通马达前壳31的第一空腔34,在主轴与马达前壳31之间夹设有第一轴承21,所述主轴10一端伸出前壳31用于外接负载,并经由第一轴承21支承在马达前壳31上,所述主轴10的主轴轴心10C与缸体80的缸体中心轴心80C重合,所述主轴10一端支承在第一轴承21上,另一端与缸体80通过键连接,主轴10悬臂支承缸体80并与缸体80同步旋转,所述主轴10经由第一轴承21绕自身的轴心旋转自如,所述第一轴承21包含至少一个向心推力轴承或推力轴承21b,在靠近缸体80端部的主轴上设置有主轴挡肩12,所述主轴挡肩12用于止挡缸体并将作用在缸体上的轴向液压力传递至向心推力轴承或推力轴承21b上。The main shaft 10 is cylindrical and penetrates the first cavity 34 of the motor front housing 31. A first bearing 21 is interposed between the main shaft and the motor front housing 31. One end of the main shaft 10 extends out of the front housing 31 for external load. , And supported on the motor front housing 31 via a first bearing 21. The main shaft axis 10C of the main shaft 10 coincides with the cylinder center axis 80C of the cylinder block 80. One end of the main shaft 10 is supported on the first bearing 21, The other end is connected with the cylinder 80 by a key. The main shaft 10 cantilever supports the cylinder 80 and rotates synchronously with the cylinder 80. The main shaft 10 can rotate freely around its own axis via a first bearing 21. The first bearing 21 includes at least A centripetal thrust bearing or thrust bearing 21b is provided with a spindle shoulder 12 on the spindle close to the end of the cylinder 80. The spindle shoulder 12 is used to stop the cylinder and act on the axial hydraulic pressure on the cylinder. The force is transmitted to the centripetal thrust bearing or thrust bearing 21b.
所述缸体80具有沿径向截面为圆形的柱状构形,并容纳在马达的壳身32的第二空腔35内,所述缸体80具有以缸体中心轴心80C环向均匀分布的多个柱塞孔81和在中心处用于容纳主轴的主轴装配孔82,所述缸体80的柱 塞孔81为一端封闭、一端开口的盲孔结构。优选地,所述柱塞孔数量一般设置为7个或9个,所述主轴10穿过缸体80的主轴装配孔82并以其轴体外周面设置键连接方式与缸体80连接,所述缸体80以其与主轴10同步运动的方式支承在主轴10上。The cylinder 80 has a cylindrical configuration with a circular cross-section in the radial direction, and is accommodated in the second cavity 35 of the housing 32 of the motor. The cylinder 80 has a uniform circumferential direction about the central axis 80C of the cylinder. A plurality of distributed plunger holes 81 and a spindle assembly hole 82 at the center for accommodating the spindle, the plunger hole 81 of the cylinder 80 is a blind hole structure with one end closed and one end open. Preferably, the number of the plunger holes is generally set to 7 or 9, the spindle 10 passes through the spindle assembly hole 82 of the cylinder body 80 and is connected to the cylinder body 80 by a key connection on the outer circumference of the shaft body, so The cylinder 80 is supported on the main shaft 10 in a manner that it moves synchronously with the main shaft 10.
当马达工作时,缸体80端部抵接在主轴挡肩12上并与主轴同步旋转,轴向液压力和中心弹簧作用力经主轴挡肩12传递至向心推力球轴承或圆锥滚子轴承或推力轴承21b上,进而传递至马达壳上。When the motor is working, the end of the cylinder 80 abuts on the main shaft shoulder 12 and rotates synchronously with the main shaft. The axial hydraulic pressure and central spring force are transmitted to the radial thrust ball bearing or tapered roller bearing through the main shaft shoulder 12 Or the thrust bearing 21b, and then to the motor housing.
所述柱塞70包括一端支承在滑盘50的柱塞球窝58上且经由压板60固定在滑盘端面的柱塞球头71、用于连通柱塞孔81和柱塞球窝58的柱塞中心孔72、外周面呈圆锥形的锥形杆部73以及与缸体柱塞孔壁间隙配合的且可在其往复运动的柱塞部74。所述柱塞球头71呈球状且能够滑动自如地支承在滑盘50的柱塞球窝58上,所述柱塞中心孔72为大孔径通孔结构,作为吸入和排出油液通道,在柱塞部74上往往设置至少一道密封圈用于密封液体,所述锥形杆部73是大致从柱塞球端向柱塞部74逐渐增加的锥形状,当柱塞70运动到某一位置时,锥形杆部74与缸体柱塞孔81内环周面接触,起到传力作用。但需要说明的是,柱塞70不限于锥形柱塞类型,还可以包含两端均为球头的连杆-柱塞或者带万向铰的球面柱塞。The plunger 70 includes a plunger ball 71 with one end supported on the plunger ball socket 58 of the sliding plate 50 and fixed on the end surface of the sliding plate via a pressure plate 60, and a post for communicating the plunger hole 81 and the plunger ball socket 58 The central hole 72 of the plug, the conical rod portion 73 with a conical outer peripheral surface, and the plunger portion 74 that is clearance fit with the cylinder plunger hole wall and can reciprocate therebetween. The plunger ball head 71 is spherical and slidably supported on the plunger ball socket 58 of the sliding plate 50. The plunger center hole 72 has a large-diameter through-hole structure, which serves as a channel for sucking and discharging oil. The plunger portion 74 is often provided with at least one sealing ring for sealing the liquid. The tapered rod portion 73 has a tapered shape that gradually increases from the ball end of the plunger to the plunger portion 74. When the plunger 70 moves to a certain position At this time, the tapered rod portion 74 is in contact with the inner circumferential surface of the cylinder plunger hole 81 and plays a role of force transmission. However, it should be noted that the plunger 70 is not limited to the conical plunger type, and may also include a connecting rod-plunger with ball heads at both ends or a spherical plunger with a universal hinge.
如图4、5和6所示,所述滑盘50与斜盘对置的端面上设置有静压支承面51,滑盘轴心50C与主轴轴心10C呈一定角度,所述静压支承面51支承在斜盘40上且始终与所述斜盘40保持滑动配合,所述静压支承面51上设置有构形为腰形的多个油室53a,优选地,油室53a以滑盘轴心50C为中心呈均匀分布在静压支承面51上,在所述滑盘50上设置有连通柱塞球窝58与油室53a的大孔径通油孔53。As shown in Figures 4, 5 and 6, the end face of the sliding plate 50 opposite to the swash plate is provided with a static pressure support surface 51, the sliding plate axis 50C and the spindle axis 10C are at a certain angle, and the static pressure support The surface 51 is supported on the swash plate 40 and always maintains a sliding fit with the swash plate 40. The static pressure support surface 51 is provided with a plurality of lumbar-shaped oil chambers 53a. Preferably, the oil chambers 53a are smooth The disc axis 50C is uniformly distributed on the hydrostatic support surface 51 as the center, and the sliding disc 50 is provided with a large-diameter oil through hole 53 that communicates the plunger ball socket 58 and the oil chamber 53a.
进一步地,所述滑盘50与斜盘40对置的端面上设置有沿滑盘轴心50C向斜盘40一侧延伸的突起的凸台面52,该凸台面52是由内直径R1和外直径R2围成的区域构成,滑盘的凸台面52与斜盘40支承面以能够滑动的方式相互抵接。在所述凸台面52上与柱塞球窝58位置对应处设置有多个油室53a,优选地,该油室53a是以滑盘轴心50C为中心的共同的圆周均匀间隔地分布在所述凸台面52上。Further, the opposite end surface of the sliding plate 50 and the swash plate 40 is provided with a raised boss surface 52 extending along the axis 50C of the sliding plate to the side of the swash plate 40, and the boss surface 52 is formed by the inner diameter R1 and the outer diameter R1. The area enclosed by the diameter R2 is configured so that the boss surface 52 of the sliding plate and the supporting surface of the swash plate 40 abut against each other in a slidable manner. A plurality of oil chambers 53a are provided on the boss surface 52 corresponding to the position of the plunger ball socket 58. Preferably, the oil chambers 53a are distributed evenly on a common circumference centered on the sliding disc axis 50C. The boss surface 52 is on.
其中,所述凸台面52与斜盘40支承面之间形成有效的静压油膜支承,所述凸台面52上设置有用于密封油液作用的密封部,所述密封部以包围所 述油室53a的状态设置在油室53a的内外周,所述密封部包含分布在油室53a径向内外的内密封部55、外密封部54,以及分布在相邻油室53a之间的间隔密封部56。所述内密封部55是由油室53a内边缘与凸台面52的内直径R1围成的区域,所述外密封部54是由油室53a外边缘与凸台面52的外直径R2围成的区域,所述间隔密封部56是由相邻油室53a之间的间隔凸台面区域。所述凸台面52的密封部与斜盘40支承面之间始终保持一定合理的间隙使得油膜泄漏处于合理水平。Wherein, an effective hydrostatic oil film support is formed between the boss surface 52 and the support surface of the swash plate 40, and the boss surface 52 is provided with a sealing portion for sealing oil, and the sealing portion surrounds the oil chamber The state of 53a is set on the inner and outer circumferences of the oil chamber 53a, and the sealing portion includes an inner sealing portion 55 and an outer sealing portion 54 distributed radially inward and outward of the oil chamber 53a, and an interval sealing portion distributed between adjacent oil chambers 53a 56. The inner seal portion 55 is an area enclosed by the inner edge of the oil chamber 53a and the inner diameter R1 of the boss surface 52, and the outer seal portion 54 is enclosed by the outer edge of the oil chamber 53a and the outer diameter R2 of the boss surface 52. Area, the interval sealing portion 56 is a boss surface area formed by the interval between adjacent oil chambers 53a. A reasonable gap is always maintained between the sealing portion of the boss surface 52 and the supporting surface of the swash plate 40 so that the oil film leakage is at a reasonable level.
如图5和6所示,所述滑盘50朝向缸体一侧的端面与柱塞70相对位置设置有多个柱塞球窝58,所述柱塞球窝58在滑盘50端面形成开口大致成半球状的凹部,柱塞球窝58以滑盘轴心50C的共同的圆周均匀间隔地分布的状态对柱塞球头71进行支承,在柱塞70安装在柱塞球窝58后,通过压板60将其固定在滑盘50的端面上,使得柱塞70相对滑盘50的端面的远离移动受到限制。特殊地,用于将柱塞70固定在滑盘50的端面的方式也不限于采用压板的方式,例如,也可以在滑盘50上设置有形状锁合的压紧装置(未示出),该压紧装置可通过大于180度的包覆将柱塞球头71进行固定。As shown in Figures 5 and 6, a plurality of plunger ball sockets 58 are provided on the end surface of the sliding plate 50 facing the cylinder block opposite to the plunger 70, and the plunger ball sockets 58 form openings on the end surface of the sliding plate 50. A substantially hemispherical recess, the plunger ball sockets 58 support the plunger ball 71 in a state evenly distributed on the common circumference of the spool axis 50C. After the plunger 70 is mounted on the plunger ball socket 58, It is fixed on the end surface of the sliding plate 50 by the pressing plate 60, so that the movement of the plunger 70 relative to the end surface of the sliding plate 50 is restricted. In particular, the method for fixing the plunger 70 on the end surface of the sliding plate 50 is not limited to the way of using a pressing plate. For example, a form-locking pressing device (not shown) may also be provided on the sliding plate 50, The pressing device can fix the plunger ball head 71 through a covering greater than 180 degrees.
如图7-10示出了斜盘的实施例,所述斜盘具有与滑盘静压支承面匹配的斜盘支承面41,在所述斜盘支承面41上设置有腰形低压配流窗口43和腰形高压配流窗口44,所述低压配流窗口43和高压配流窗口44被经过斜盘中心轴的CC平面分割成两侧,所述低压配流窗口43和高压配流窗口44相对中心平面CC设置为对称结构,所述配流窗口可设置成单个或多个具有腰形的窗口。Figures 7-10 show an embodiment of the swash plate. The swash plate has a swash plate support surface 41 that matches the static pressure support surface of the swash plate. A waist-shaped low pressure distribution window is provided on the swash plate support surface 41. 43 and a waist-shaped high-pressure distribution window 44. The low-pressure distribution window 43 and the high-pressure distribution window 44 are divided into two sides by a CC plane passing through the central axis of the swash plate. The low-pressure distribution window 43 and the high-pressure distribution window 44 are arranged relative to the central plane CC For a symmetrical structure, the flow distribution window can be configured as a single or multiple windows having a waist shape.
特殊地,为了使得斜盘具有一定的预升压和预降压的作用,可以将低压配流窗口43和高压配流窗口44沿斜盘的中心轴旋转一定角度;可替换地,也可在低压配流窗口43端部上设置从低压配流窗口43过渡到高压配流窗口44方向以及在高压配流窗口44端部上设置从高压配流窗口44过渡到低压配流窗口43方向的节流槽或孔,起到从高压到低压或低压到高压起到预降压和预升压的作用。In particular, in order to make the swash plate have a certain pre-boosting and pre-decreasing effect, the low-pressure distribution window 43 and the high-pressure distribution window 44 can be rotated to a certain angle along the central axis of the swash plate; alternatively, the low-pressure distribution window can also be used. The end of the window 43 is provided with a throttle groove or hole that transitions from the low-pressure distribution window 43 to the high-pressure distribution window 44, and at the end of the high-pressure distribution window 44 is provided a throttle groove or hole that transitions from the high-pressure distribution window 44 to the low-pressure distribution window 43. High pressure to low pressure or low pressure to high pressure play the role of pre-pressure reduction and pre-boost.
所述斜盘40与端座33对置的支承面设置成具有成形为圆柱形的圆柱支承面45,所述端座33上具有与斜盘圆柱支承面45半径相同的滑弧面33e,使得斜盘圆柱支承面45在端座的滑弧面33e上滑动时始终保持密贴状态。所述斜盘的圆柱支承面45上具有构形为槽形的槽形低压口46和槽形高压口 47,所述圆柱支承面45上的槽形低压口46和槽形高压口47分别与所述斜盘圆柱面相反侧的支承面41上的低压配流窗口43和高压配流窗口44对应连通。所述圆柱支承面45上的槽形低压口46和槽形高压口47为设置为对称结构;所述圆柱支承面45上的槽形低压口46和槽形高压口47的周边具有密封所述槽口的密封带,使得斜盘圆柱支承面45在端座的滑弧面33e上滑动时密封油液。The supporting surface of the swash plate 40 opposite to the end seat 33 is configured to have a cylindrical supporting surface 45 shaped as a cylinder, and the end seat 33 has a sliding arc surface 33e with the same radius as the cylindrical supporting surface 45 of the swash plate, so that The cylindrical support surface 45 of the swash plate always maintains a close contact state when sliding on the sliding arc surface 33e of the end seat. The cylindrical support surface 45 of the swash plate has a groove-shaped low-pressure port 46 and a groove-shaped high-pressure port 47 that are configured in a groove shape. The groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the cylindrical support surface 45 are respectively connected to The low pressure distribution window 43 and the high pressure distribution window 44 on the supporting surface 41 on the opposite side of the cylindrical surface of the swash plate are correspondingly communicated. The groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the cylindrical support surface 45 are arranged in a symmetrical structure; the groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the cylindrical support surface 45 have a seal The sealing band of the notch makes the cylindrical support surface 45 of the swash plate seal oil when sliding on the sliding arc surface 33e of the end seat.
所述端座33上设置有轴向柱塞马达的进油口33a和出油口33b,所述出油口33b与圆柱支承面45上的槽形低压口46连通,所述进油口33a与圆柱支承面45上的槽形高压口47连通,所述端座33上设置的进油口33a和出油口33b的数量可以是一个或两个,特殊地,所述端座33上只设置一个进油口33a和一个出油口33b,这样左右两侧的马达共用一个进油口和一个出油口。The end seat 33 is provided with an oil inlet 33a and an oil outlet 33b of the axial piston motor. The oil outlet 33b is in communication with the groove-shaped low pressure port 46 on the cylindrical support surface 45. The oil inlet 33a Connected with the groove-shaped high-pressure port 47 on the cylindrical support surface 45, the number of the oil inlet 33a and the oil outlet 33b provided on the end seat 33 can be one or two. In particular, the end seat 33 has only One oil inlet 33a and one oil outlet 33b are provided, so that the motors on the left and right sides share one oil inlet and one oil outlet.
实施例2:Example 2:
如图15所示,与其他实施例的主要区别在于配流滑盘副组件中在滑盘50与斜盘40之间夹设有配流盘90,所述静压支承面51支承在配流盘90上且与配流盘90保持滑动配合,所述配流盘通过销钉等方式固定在斜盘上,所述配流盘90上设置有高压配流口93和低压配流口92,所述高压配流口93和低压配流口92分别与斜盘上的低压配流窗口43和高压配流窗口44连通。所述低压配流口和高压配流口相对中心平面可以设置为对称结构;进一步地,为使得配流盘具有一定的预升压和预降压的作用,可以将低压配流口和高压配流口沿配流盘的中心轴旋转一定角度;可替换地,也可在低压配流口端部上设置从低压配流口过渡到高压配流口方向以及在高压配流口端部上设置从高压配流口过渡到低压配流口方向的节流槽或孔,起到从高压到低压或低压到高压起到预降压和预升压的作用。As shown in FIG. 15, the main difference from other embodiments is that a valve plate 90 is sandwiched between the sliding plate 50 and the swash plate 40 in the valve plate sub-assembly, and the static pressure support surface 51 is supported on the valve plate 90 And maintain a sliding fit with the valve plate 90, the valve plate is fixed on the swash plate by means of pins or the like, the valve plate 90 is provided with a high pressure valve port 93 and a low pressure valve port 92, the high pressure valve port 93 and the low pressure valve plate The ports 92 respectively communicate with the low pressure distribution window 43 and the high pressure distribution window 44 on the swash plate. The low-pressure distribution port and the high-pressure distribution port can be arranged in a symmetrical structure relative to the central plane; further, in order to make the distribution plate have a certain pre-boosting and pre-decreasing effect, the low-pressure distribution port and the high-pressure distribution port can be arranged along the distribution plate The central axis rotates at a certain angle; alternatively, the direction of transition from the low-pressure port to the high-pressure port and the direction of the transition from the high-pressure port to the low-pressure port can be set on the end of the high-pressure port. The throttling groove or hole plays the role of pre-pressure reduction and pre-boosting from high pressure to low pressure or low pressure to high pressure.
在本公开的实施例中,在滑盘50与斜盘40之间夹设有配流盘90的好处在于,后期更换配流盘比更换斜盘更容易且费用更省。In the embodiment of the present disclosure, the advantage of sandwiching the valve plate 90 between the sliding plate 50 and the swash plate 40 is that it is easier and cheaper to replace the valve plate later than replacing the swash plate.
实施例3:Example 3:
如图11-14所示,与其他实施例的主要区别在于配流滑盘副组件中在滑盘50与斜盘40之间夹设有第三轴承23,使得所述滑盘50以沿其径向受约束的状态支承在所述第三轴承23上,设置第三轴承23的配流滑盘副,其结构受力更加有利。As shown in Figures 11-14, the main difference from other embodiments is that a third bearing 23 is sandwiched between the sliding plate 50 and the swash plate 40 in the flow distribution sliding plate sub-assembly, so that the sliding plate 50 follows its diameter. It is supported on the third bearing 23 in a constrained state, and the valve sliding plate pair of the third bearing 23 is arranged, and its structure is more favorable for stress.
如图11和12所示,示出了滑盘内支承式串联变量轴向柱塞马达的一种实施例,在所示的优选实施例中,支承在端座33上的两对置的配流滑盘组件中,在斜盘40中部具有向外延伸的支承轴或支承轴销49,在所述斜盘支承轴或支承轴销49和滑盘50内侧之间夹设有第三轴承23,所述滑盘50以沿其径向受约束的状态支承在所述第三轴承23上,所述第三轴承23可以设置为包含但不限于向心推力球轴承、滚针轴承、圆柱滚子轴承、圆锥滚子轴承、向心球轴承的一种,所述主轴10和缸体80在旋转工作时,所述柱塞70在缸体80的柱塞腔内做往复运动,实现马达的吸排油工作。As shown in Figures 11 and 12, there is shown an embodiment of a series variable axial piston motor supported in the sliding disk. In the preferred embodiment shown, two opposed flow distributions supported on the end seat 33 In the sliding plate assembly, a supporting shaft or supporting shaft pin 49 extending outward is provided in the middle of the swash plate 40, and a third bearing 23 is interposed between the swash plate supporting shaft or supporting shaft pin 49 and the inner side of the sliding plate 50, The sliding plate 50 is supported on the third bearing 23 in a state of being constrained in its radial direction. The third bearing 23 may be configured to include, but is not limited to, a radial thrust ball bearing, a needle roller bearing, and a cylindrical roller. One of bearings, tapered roller bearings, and radial ball bearings. When the spindle 10 and the cylinder 80 are rotating, the plunger 70 reciprocates in the plunger cavity of the cylinder 80 to realize the suction and discharge of the motor. Oil work.
如图13和14所示,示出了滑盘外支承式串联变量轴轴向柱塞马达的一种实施例。在所示的优选实施例中,支承在端座33上的两对置的配流滑盘组件中,在所述滑盘50外周与支承挡部41a内侧之间夹设有第三轴承23,所述滑盘50以沿其径向受约束状态支承在第三轴承23。所述主轴10和缸体80在旋转工作时,在所述斜盘40的支承力及回程机构的回程力作用下,所述柱塞70在缸体80的柱塞腔内做往复运动,实现马达的吸排油工作。As shown in Figures 13 and 14, there is shown an embodiment of a sliding disc externally supported series variable shaft axial piston motor. In the preferred embodiment shown, in the two opposed flow distribution sliding plate assemblies supported on the end seat 33, a third bearing 23 is interposed between the outer circumference of the sliding plate 50 and the inner side of the supporting block 41a, so The sliding plate 50 is supported by the third bearing 23 in a state of being restrained in its radial direction. When the main shaft 10 and the cylinder 80 are rotating, under the action of the supporting force of the swash plate 40 and the return force of the return mechanism, the plunger 70 reciprocates in the plunger cavity of the cylinder 80 to achieve The motor sucks and discharges oil.
在轴向柱塞马达运行过程中,高压区柱塞70受到缸体柱塞孔81的高压油液压力作用,经柱塞球头71对滑盘50施加一个接近水平的液压力作用,该液压力将滑盘50推向斜盘40并与斜盘40端面紧密接触。斜盘40端面对滑盘50施加一个反作用力,由于滑盘50端面与斜盘40端面是以斜面形式接触,斜盘40的反作用力可分解成沿主轴轴心10C方向的水平分力以及沿垂直主轴轴心10C方向的侧向分力,该侧向分力有使滑盘向侧向运动的趋势。在所述斜盘40和滑盘50之间夹设有第三轴承23后,滑盘受到第三轴承23的反作用力,作用在滑盘上的反作用力也可分解成沿主轴轴心10C方向的水平分力以及沿垂直主轴轴心10C方向的侧向分力。除此之外,滑盘还受到中心轴处的回程力作用、惯性力作用(相互抵消)以及摩擦力作用(未示出)等,上述几种力构成滑盘的力的平衡。需要说明的是,各力沿主轴轴心方向的水平分力与柱塞70作用在滑盘50的液压力平衡。作用在滑盘50上沿垂直主轴轴心10C方向的侧向分力在滑盘50内能够得到抵消,而不需要进一步经由柱塞70传递至缸体80中。During the operation of the axial piston motor, the plunger 70 in the high-pressure zone is acted on by the high-pressure oil pressure from the plunger hole 81 of the cylinder block, and a nearly horizontal hydraulic pressure is exerted on the sliding plate 50 through the plunger ball 71. The force pushes the sliding plate 50 toward the swash plate 40 and makes close contact with the end surface of the swash plate 40. The end of the swash plate 40 exerts a reaction force on the sliding plate 50. Since the end face of the swash plate 50 and the end face of the swash plate 40 are in inclined contact, the reaction force of the swash plate 40 can be decomposed into a horizontal component force along the spindle axis 10C and The lateral component force along the direction perpendicular to the spindle axis 10C has a tendency to move the sliding plate sideways. After the third bearing 23 is interposed between the swash plate 40 and the sliding plate 50, the sliding plate receives the reaction force of the third bearing 23, and the reaction force acting on the sliding plate can also be decomposed into a direction along the spindle axis 10C The horizontal component and the lateral component along the direction perpendicular to the spindle axis 10C. In addition, the sliding plate is also subjected to the return force at the central axis, the inertial force (to cancel each other), and the frictional force (not shown), etc. The above-mentioned forces constitute the force balance of the sliding plate. It should be noted that the horizontal component force of each force along the axis of the main shaft is balanced with the hydraulic pressure of the plunger 70 acting on the sliding plate 50. The lateral component force acting on the sliding plate 50 in the direction perpendicular to the spindle axis 10C can be offset in the sliding plate 50 without being further transmitted to the cylinder 80 via the plunger 70.
这种采用了轴承支承滑盘的结构具有以下特点:第三轴承23约束了滑盘50沿径向的运动或运动趋势,平衡了滑盘50作用力的侧向分力,使得滑盘50经由柱塞70作用在缸体80上的侧向力被消除或大幅度降低,提高了 轴向柱塞泵或马达的工作可靠性、工作压力和工作寿命。This structure adopting the bearing to support the sliding plate has the following characteristics: the third bearing 23 restricts the movement or movement trend of the sliding plate 50 in the radial direction, and balances the lateral component of the sliding plate 50, so that the sliding plate 50 passes through The lateral force of the plunger 70 on the cylinder 80 is eliminated or greatly reduced, which improves the working reliability, working pressure and working life of the axial piston pump or motor.
同时,尤其明显地是,所述轴向柱塞泵或马达的回程方式得到较大简化,该回程结构包含在配流滑盘副一侧设置的约束装置,所述约束装置限制滑盘50在回程力作用下远离斜盘40端面。At the same time, it is particularly obvious that the return stroke of the axial piston pump or motor is greatly simplified. The return structure includes a restraining device provided on the side of the valve sliding plate pair, and the restraining device restricts the slide plate 50 in the return stroke. Keep away from the end face of the swash plate 40 under the action of force.
以滑盘内支承式串联变量轴轴向柱塞马达为例,如图11和12所示,所述约束装置包含在滑盘50靠近静压支承面51一侧具有向内侧凸起的止挡部57以及在所述斜盘支承轴或支承轴销49外侧设置的卡合装置140。所述止挡部57用于止挡第三轴承23的移动,所述卡合装置140包含在所述斜盘支承轴或支承轴销49外侧设置的卡合周槽以及在卡合周槽上设置卡簧(未示出),所述卡簧以约束所述第三轴承23沿支承轴41向外移动的方式限制滑盘远离斜盘40端面。特殊地,所述约束装置140也可以设置成止挡部与预紧螺母(未示出)组合形式,即在支承轴或支承轴销49外侧设置螺纹,通过螺母拧紧从而约束第三轴承和滑盘远离斜盘端面。Taking a sliding plate internally supported tandem variable shaft axial piston motor as an example, as shown in Figures 11 and 12, the restraining device includes a stop protruding inward on the side of the sliding plate 50 close to the hydrostatic support surface 51 The portion 57 and the engagement device 140 provided outside the swash plate support shaft or the support shaft pin 49. The stop portion 57 is used to stop the movement of the third bearing 23, and the engagement device 140 includes an engagement circumferential groove provided on the outer side of the swash plate support shaft or the support shaft pin 49 and an engagement circumferential groove A circlip (not shown) is provided, and the circlip restricts the sliding plate from moving away from the end surface of the swash plate 40 in a manner of restraining the third bearing 23 from moving outward along the supporting shaft 41. In particular, the restraining device 140 can also be configured as a combination of a stop portion and a pre-tightening nut (not shown), that is, a thread is provided on the outside of the supporting shaft or the supporting shaft pin 49, and the nut is tightened to restrain the third bearing and sliding The disk is away from the end face of the swash plate.
以滑盘外支承式串联变量轴轴向柱塞马达为例,如图13和14所示,所述约束装置包含在滑盘50靠近静压支承面51一侧具有向外侧凸起的止挡部57以及在所述支承挡部41a上设置的卡合装置140。所述止挡部57用于限制第三轴承23的移动,所述卡合装置包含在所述支承挡部41a上、邻近第三轴承23处设置的卡合周槽以及在所述卡合内周槽上设置卡簧(未示出),所述卡簧以约束所述第三轴承23向外移动的方式限制滑盘远离斜盘40端面。Taking the sliding plate externally supported tandem variable shaft axial piston motor as an example, as shown in Figures 13 and 14, the restraining device includes a stop protruding outward on the side of the sliding plate 50 close to the hydrostatic bearing surface 51 Portion 57 and an engagement device 140 provided on the supporting stop portion 41a. The stop portion 57 is used to restrict the movement of the third bearing 23, and the engagement device includes an engagement circumferential groove provided on the support stop portion 41a and adjacent to the third bearing 23 and in the engagement A retaining spring (not shown) is provided on the circumferential groove, and the retaining spring restricts the sliding plate from moving away from the end surface of the swash plate 40 in a manner of restricting the third bearing 23 to move outward.
可以预测地,在止挡部57与第三轴承23之间或者在卡簧与第三轴承23之间也可以适当设置弹性垫片(未示出),使得约束组件除了限制滑盘远离斜盘端面外,还具有一定的初始预紧力保持滑盘与斜盘的预紧状态。Predictably, an elastic washer (not shown) can also be appropriately provided between the stop portion 57 and the third bearing 23 or between the circlip and the third bearing 23, so that the restraint assembly can not only restrict the sliding plate from moving away from the swash plate, Outside the end face, there is also a certain initial preload to maintain the preload state of the sliding plate and the swash plate.
同理,所述约束装置140的约束方式还可以通过第三轴承23的过盈配合来实现,在邻近第三轴承23处设置卡合周槽及与卡合周槽配合的卡簧起进一步约束作用。In the same way, the restraining method of the restraining device 140 can also be realized by the interference fit of the third bearing 23, and the engaging circumferential groove is provided adjacent to the third bearing 23 and the circlip that cooperates with the engaging circumferential groove is further restrained. effect.
需要说明的的是,由于缸体80端部不设置配流盘,无静压油膜支承的摩擦副,不需要通过对缸体80端部施加预紧力来达到密封目的,因此只需在滑盘副上设置约束装置140,即可满足柱塞的回程要求,不需要另外增设中心弹簧等预紧或回程部件,使得该约束装置较大幅度地简化了结构,也避免了中心弹簧因疲劳损坏而断裂等现象。当然,为了防止轴向柱塞泵在非水 平放置时(例如存放、运送、使用过程中将其倒置等),缸体80沿主轴10向滑盘方向移动,在主轴10上、邻近缸体端面设置缸体卡簧141以约束缸体80的串动。It should be noted that since there is no valve plate at the end of the cylinder body 80 and there is no friction pair supported by a static pressure oil film, it is not necessary to apply a pre-tightening force to the end of the cylinder body 80 to achieve the purpose of sealing. The constraining device 140 is provided on the auxiliary to meet the requirements of the plunger's return stroke. There is no need to add additional pre-tensioning or return components such as a central spring, so that the constraining device greatly simplifies the structure and avoids fatigue damage to the central spring. Phenomena such as fracture. Of course, in order to prevent the axial piston pump from being placed in a non-horizontal position (such as storing, transporting, turning it upside down during use, etc.), the cylinder 80 moves along the main shaft 10 in the direction of the sliding plate, on the main shaft 10, adjacent to the end surface of the cylinder. A cylinder circlip 141 is provided to restrict the string movement of the cylinder 80.
实施例4:Example 4:
如图14所示,与实施例1的主要区别在于所述双联式轴向柱塞马达的变量方式采用分开式变量。所述双联变量轴向柱塞马达设置有两个独立的变量机构,所述变量机构分别连接在端座两侧的壳身32上,所述斜盘端部设置有变量连接部38,所述两侧的斜盘的变量连接部38分别与变量机构连接。所述变量机构分别控制各自的斜盘运动,实现同步或异步变量。As shown in FIG. 14, the main difference from Embodiment 1 is that the variable mode of the dual axial piston motor adopts a separate variable. The double variable axial plunger motor is provided with two independent variable mechanisms, the variable mechanisms are respectively connected to the housing 32 on both sides of the end seat, the end of the swash plate is provided with a variable connecting portion 38, so The variable connection portions 38 of the swash plate on both sides are respectively connected to the variable mechanism. The variable mechanism respectively controls the respective swash plate movement to realize synchronous or asynchronous variable.
实施例5:Example 5:
根据变量方式的不同,所述双联式轴向柱塞马达中分布在端座33左右两侧的马达可以有不同组合,包含以下其中一种组合:1)端座33左右两侧的马达均为变量式轴向柱塞马达,如图2和3所示,端座两端均设置圆柱形滑弧面33e且与变量斜盘圆柱形支承面45紧密抵接;2)端座33左右两侧的马达均为定量式轴向柱塞马达,如图16所示,左右两侧的斜盘40为固定倾斜角度,且支承在共同的端座33上;3)端座33左右两侧的马达有一个为定量式轴向柱塞马达,另一个为变量式轴向柱塞马达,端座一端设置圆柱形滑弧面33e且与变量斜盘的圆柱支承面45紧密抵接,另一端设置平面支承面且与固定角度的斜盘40连接。According to the different variable modes, the motors distributed on the left and right sides of the end seat 33 in the dual axial piston motor can have different combinations, including one of the following combinations: 1) The motors on the left and right sides of the end seat 33 are both It is a variable type axial piston motor, as shown in Figures 2 and 3, both ends of the end seat are provided with cylindrical sliding arc surfaces 33e and tightly abutted with the cylindrical support surface 45 of the variable swash plate; 2) the left and right sides of the end seat 33 The motors on the side are all quantitative axial piston motors. As shown in Fig. 16, the swash plates 40 on the left and right sides have a fixed inclination angle and are supported on a common end seat 33; 3) the left and right sides of the end seat 33 One of the motors is a quantitative axial piston motor, and the other is a variable axial piston motor. One end of the end seat is provided with a cylindrical sliding arc surface 33e and is in close contact with the cylindrical support surface 45 of the variable swash plate, and the other end is provided The plane supporting surface is connected with the swash plate 40 with a fixed angle.
基于上述技术方案,本公开的实施例的有益效果至少包括:Based on the above technical solutions, the beneficial effects of the embodiments of the present disclosure include at least:
1、本公开的至少一实施例将两个滑盘式非通轴柱塞马达串联一起,马达功率提高了两倍,可满足大排量、高压、大功率要求,解决了非通轴柱塞马达无法串联或串联困难等问题。1. At least one embodiment of the present disclosure connects two sliding plate type non-through shaft plunger motors in series, and the motor power is increased by two times, which can meet the requirements of large displacement, high pressure and high power, and solves the problem of non-through shaft plunger. Motors cannot be connected in series or difficult to connect in series.
2、在本公开的至少一实施例提供的双联式轴向柱塞马达中,对置设置斜盘,并使斜盘支承在共同的一个端座上,斜盘上设置吸排油通道并与设置在端座上的进出油口连通,可使结构大大简化,尺寸更小、结构更加紧凑,马达的重量更小,因此提高了其单位质量功率密度,同时,双联式轴向柱塞马达由于结构优化后的缸体离轴承较近,使得作用在悬臂主轴上的弯矩减少,这对主轴受力更加有利,轴承寿命更长,且工作过程中机械噪声更小。2. In the dual axial plunger motor provided by at least one embodiment of the present disclosure, the swash plate is arranged oppositely, and the swash plate is supported on a common end seat, and the swash plate is provided with an oil suction and discharge channel and is connected with The connection between the inlet and outlet ports provided on the end seat can greatly simplify the structure, make the size smaller, the structure more compact, and the weight of the motor is smaller, thus increasing its power density per unit mass. At the same time, the dual axial piston motor As the optimized structure of the cylinder is closer to the bearing, the bending moment acting on the cantilever main shaft is reduced, which is more beneficial to the main shaft, the bearing life is longer, and the mechanical noise during operation is smaller.
3、本公开的至少一实施例将配流、变量倾斜、静压支承功能集成在滑盘副中,主要摩擦副为滑盘副和柱塞副,一是,减少了一个配流副,因此减 少了油液的漏损,提高了其效率;二是,柱塞的侧向力的大大降低,消除或降低了缸体倾覆现象。由于缸体端部无配流副,因此缸体端部不存在磨损、泄漏等问题,即便是存在侧向力对缸体产生倾覆作用,也不会产生偏磨导致失效等问题,同时这种结构使得缸体的寿命更长,后期维修更少,降低了使用成本。3. At least one embodiment of the present disclosure integrates the functions of flow distribution, variable tilt, and hydrostatic support into the sliding plate pair. The main friction pairs are the sliding plate pair and the plunger pair. One is that one valve pair is reduced, thereby reducing The leakage of oil improves its efficiency; secondly, the lateral force of the plunger is greatly reduced, which eliminates or reduces the overturning phenomenon of the cylinder. Since there is no valve pair at the end of the cylinder, there are no problems such as wear and leakage at the end of the cylinder. Even if there is a side force that overturns the cylinder, it will not cause problems such as partial wear and failure. At the same time, this structure Makes the life of the cylinder longer, less maintenance later, and reduces the cost of use.
4、本公开的至少一实施例提供的双联式轴向柱塞马达变量方式可设置成集中式和分开式变量方式,可以适应于不同工况,且各有其特点,其中集中式变量方式,将两个对置的斜盘可以连接在共同的一个滑阀上,当滑阀运动时,可带动两个斜盘做同步运动,这种结构只设置一个变量机构,因此结构简单,变量方便,对于要求双联式轴向柱塞马达两轴端同步运动的情况特别具有优势。4. The variable mode of the dual axial plunger motor provided by at least one embodiment of the present disclosure can be set to a centralized and separate variable mode, which can be adapted to different working conditions and each has its own characteristics, of which the centralized variable mode , Two opposite swash plates can be connected to a common slide valve. When the slide valve moves, it can drive the two swash plates to move synchronously. This structure only has one variable mechanism, so the structure is simple and the variables are convenient , It is especially advantageous for the situation that requires the simultaneous movement of the two shaft ends of the dual axial piston motor.
5、本公开的至少一实施例将配流、变量倾斜、静压支承功能集成在滑盘副中,由于滑盘球窝与柱塞球头在工作过程中是可相对倾动的,因此,可自适应因斜盘倾动、缸体倾动等各种情况,使得滑盘始终能紧贴斜盘完成配流、变量、支承等功能;同时,相比更换缸体,更换滑盘或配流盘更加容易、更经济。5. At least one embodiment of the present disclosure integrates the functions of flow distribution, variable tilt, and hydrostatic support in the sliding plate pair. Since the sliding plate ball socket and the plunger ball head can be relatively tilted during the working process, they can be moved automatically It adapts to various situations due to the tilting of the swash plate and the tilting of the cylinder body, so that the sliding plate can always be close to the swash plate to complete the flow distribution, variable, support and other functions; at the same time, it is easier and more convenient to replace the sliding plate or the valve plate than replacing the cylinder. economic.
以上内容是结合具体的优选技术方案对本公开所作的进一步详细说明,不能认定本公开的具体实施只局限与这些说明。对于本公开所属技术领域的普通技术人员来说,在不脱离本公开构思的前提下,还可以做出若干简单推演或替换,而一切不脱离本公开的精神和范围的技术方案及及其改进,其均应涵盖在本公开的权利要求范围中。The above content is a further detailed description of the present disclosure in combination with specific preferred technical solutions, and it cannot be considered that the specific implementation of the present disclosure is limited to these descriptions. For those of ordinary skill in the technical field of the present disclosure, without departing from the concept of the present disclosure, several simple deductions or substitutions can be made, and all technical solutions and improvements thereof that do not depart from the spirit and scope of the present disclosure All of them shall be covered in the scope of the claims of the present disclosure.
Claims (15)
- 一种双联式轴向柱塞马达,包括两个滑盘式非通轴柱塞马达以及夹设在两个滑盘式非通轴柱塞马达之间的端座(33),每个滑盘式非通轴柱塞马达包含主轴(10)、斜盘(40)、滑盘(50)、柱塞(70)和缸体(80),所述滑盘(50)为整体结构且支承在斜盘(40)上构成配流滑盘副组件,所述滑盘(50)与斜盘(40)对置的端面设置有静压支承面(51),所述滑盘(50)与缸体(80)对置的端面设置有多个柱塞球窝(58),在所述滑盘(50)上设置有连通柱塞球窝(58)和静压支承面(51)的通油孔(53),所述柱塞(70)一端置于柱塞球窝(58)内,另一端***至缸体(80)内,所述柱塞(70)内部的柱塞中心孔(72)一端与通油孔(53)连通,另一端与缸体(80)内的柱塞孔(81)连通,在所述斜盘(40)上设置有配流油槽(42),所述两个滑盘式非通轴柱塞马达的斜盘(40)支承在共同的端座(33)上,所述配流油槽(42)与端座(33)上设置的进、出油口(33a、33b)连通,高压油液流经斜盘(40)上的配流油槽(42)、通油孔(53)、柱塞中心孔(72)和柱塞孔(81),驱使缸体(80)和主轴(10)同步旋转。A double-connected axial plunger motor, comprising two sliding plate type non-through shaft plunger motors and an end seat (33) sandwiched between the two sliding plate type non-through shaft plunger motors, each sliding plate The disc type non-through shaft plunger motor includes a main shaft (10), a swash plate (40), a sliding plate (50), a plunger (70) and a cylinder (80). The sliding plate (50) is an integral structure and supports The swash plate (40) constitutes a flow distribution sliding plate sub-assembly. The end surface of the sliding plate (50) and the swash plate (40) is provided with a static pressure support surface (51). The sliding plate (50) and the cylinder The opposite end surface of the body (80) is provided with a plurality of plunger ball sockets (58), and the sliding plate (50) is provided with an oil passage connecting the plunger ball sockets (58) and the hydrostatic bearing surface (51) Hole (53), one end of the plunger (70) is placed in the plunger ball socket (58), and the other end is inserted into the cylinder (80). The plunger center hole (72) inside the plunger (70) ) One end is connected to the oil through hole (53), and the other end is connected to the plunger hole (81) in the cylinder (80). The swash plate (40) is provided with a distribution oil groove (42), the two The swash plate (40) of the sliding plate type non-through shaft plunger motor is supported on a common end seat (33). The distribution oil groove (42) and the oil inlet and outlet ports (33a, 33a, 33a, 33b) Connected, high-pressure oil flows through the distribution oil groove (42), the oil through hole (53), the plunger center hole (72) and the plunger hole (81) on the swash plate (40) to drive the cylinder block (80) It rotates synchronously with the main shaft (10).
- 根据权利要求1所述的双联式轴向柱塞马达,其中,所述滑盘(50)的静压支承面(51)上设有多个油室(53a),所述油室(53a)以滑盘轴心(50C)为中心间隔地分布在所述静压支承面(51)上,在每个油室(53a)底部与对应柱塞球窝(58)之间设置有通油孔(53),所述通油孔(53)作为吸排油液的主通道并将油液引入静压支承面(51)与斜盘(40)之间,使所述静压支承面(51)与斜盘(40)端面形成间隙配合的静压油膜支承。The dual axial piston motor according to claim 1, wherein a plurality of oil chambers (53a) are provided on the hydrostatic bearing surface (51) of the sliding plate (50), and the oil chambers (53a) ) Is distributed on the static pressure support surface (51) with the sliding disc axis (50C) as the center, and an oil passage is provided between the bottom of each oil chamber (53a) and the corresponding plunger ball socket (58) Hole (53), the oil through hole (53) serves as the main channel for sucking and discharging oil and introduces the oil between the static pressure bearing surface (51) and the swash plate (40), so that the static pressure bearing surface (51) ) A static pressure oil film support with clearance fit is formed with the end surface of the swash plate (40).
- 根据权利要求1所述的双联式轴向柱塞马达,其中,在所述凸台面(52)上设置有用于密封油液的密封部,所述密封部包括设置在油室(53a)径向内外侧的内密封部(55)和外密封部(54),以及设置在相邻油室(52)之间的间隔密封部(56)。The dual axial piston motor according to claim 1, wherein a sealing portion for sealing oil is provided on the boss surface (52), and the sealing portion includes a diameter provided in the oil chamber (53a). An inner sealing part (55) and an outer sealing part (54) facing inward and outward, and an interval sealing part (56) provided between adjacent oil chambers (52).
- 根据权利要求1所述的双联式轴向柱塞马达,其中,在所述静压支承面(51)上设置有多个油室(53a),所述斜盘(40)上与滑盘(50)对置的端面上设置有低压配流窗口(43)和高压配流窗口(44),所述高、低压配流窗口(44、43)与油室(53a)间歇地连通,所述斜盘(40)上与端座(33)对置的支承面具有成形为圆柱形的圆柱支承面(45),所述斜盘(40)的圆 柱支承面(45)上具有构形为槽形的槽形低压口(46)和槽形高压口(47),所述槽形低压口(46)和槽形高压口(47)分别与低压配流窗口(43)和高压配流窗口(44)对应连通。The dual axial piston motor according to claim 1, wherein a plurality of oil chambers (53a) are provided on the static pressure bearing surface (51), and the swash plate (40) is connected to the sliding plate (50) A low-pressure distribution window (43) and a high-pressure distribution window (44) are provided on the opposite end surfaces, and the high and low-pressure distribution windows (44, 43) are intermittently communicated with the oil chamber (53a), and the swash plate (40) The supporting surface opposite to the end seat (33) has a cylindrical supporting surface (45) shaped as a cylinder, and the cylindrical supporting surface (45) of the swash plate (40) has a groove-shaped cylindrical supporting surface (45). The groove-shaped low-pressure port (46) and the groove-shaped high-pressure port (47), the groove-shaped low-pressure port (46) and the groove-shaped high-pressure port (47) respectively communicate with the low-pressure distribution window (43) and the high-pressure distribution window (44) .
- 根据权利要求1所述的双联式轴向柱塞马达,其中,所述滑盘(50)上的通油孔(53)以及柱塞(70)上的柱塞中心孔(72)均为大孔径且作为吸排油的主油孔结构。The dual axial piston motor according to claim 1, wherein the oil through hole (53) on the sliding plate (50) and the plunger center hole (72) on the plunger (70) are both Large diameter and used as the main oil hole structure for oil suction and discharge.
- 根据权利要求1所述的双联式轴向柱塞马达,其中,所述轴向柱塞马达设置为集中变量式结构,所述端座(33)上设置有包含一个滑阀(33c)的变量机构,两个对置斜盘(40)的轴销(49)连接在共同的滑阀(33c)上,在变量机构的液压力和弹簧力作用下,所述滑阀(33c)带动两个斜盘(40)做同步转动,实现同步变量。The dual axial plunger motor according to claim 1, wherein the axial plunger motor is arranged in a centralized variable structure, and the end seat (33) is provided with a spool valve (33c) Variable mechanism, the shaft pins (49) of two opposed swash plates (40) are connected to a common slide valve (33c). Under the action of the hydraulic pressure and spring force of the variable mechanism, the slide valve (33c) drives the two A swash plate (40) rotates synchronously to realize synchronous variable.
- 根据权利要求1所述的双联式轴向柱塞马达,其中,所述轴向柱塞马达设置为分开变量式结构,在所述轴向柱塞马达的壳体上连接有两个变量机构,所述变量机构分别与对应的斜盘(40)连接,在各自变量机构的液压力和弹簧力作用下,实现独立变量。The dual axial piston motor according to claim 1, wherein the axial piston motor is configured as a separate variable structure, and two variable mechanisms are connected to the housing of the axial piston motor The variable mechanism is respectively connected with the corresponding swash plate (40), and the independent variable is realized under the action of the hydraulic pressure and spring force of the respective variable mechanism.
- 根据权利要求1所述的双联式轴向柱塞马达,其中,分布在端座(33)两侧的滑盘式非通轴柱塞马达以斜盘变量方式组合,其具体组合方式为两侧滑盘式非通轴柱塞马达均为变量式结构;或者两侧滑盘式非通轴柱塞马达均为定量式结构;或者两侧滑盘式非通轴柱塞马达一个为定量式结构、另一个为变量式结构。The dual axial piston motor according to claim 1, wherein the sliding plate non-through shaft piston motors distributed on both sides of the end seat (33) are combined in a variable swash plate, and the specific combination is two Side-slip disc type non-thru-shaft plunger motors are of variable type structure; or both sides-slip disc type non-thru-shaft plunger motors are all quantitative structure; or both sides are sliding disc type non-thru-shaft piston motors, one is quantitative type The structure, the other is a variable structure.
- 根据权利要求1所述的双联式轴向柱塞马达,其中,所述两个滑盘式非通轴柱塞马达的主轴(10)一端伸出壳体并支承在第一轴承(21)上,其另一端端部悬臂支承缸体(80)并与缸体(80)同步旋转,所述缸体(80)的柱塞孔(81)为一端封闭、一端开口的结构,在所述缸体(80)的封闭端端部不设置配流副,所述主轴(10)和缸体(80)在旋转工作时,液压轴向力通过缸体(80)经第一轴承(21)传递至壳体上。The dual axial piston motor according to claim 1, wherein one end of the main shaft (10) of the two sliding disc type non-through shaft piston motors extends out of the housing and is supported by the first bearing (21) The other end cantilever supports the cylinder (80) and rotates synchronously with the cylinder (80). The plunger hole (81) of the cylinder (80) is a structure with one end closed and one end open. The closed end of the cylinder (80) is not provided with a flow distribution pair. When the main shaft (10) and the cylinder (80) are rotating, the hydraulic axial force is transmitted through the cylinder (80) through the first bearing (21) To the shell.
- 根据权利要求9所述的双联式轴向柱塞马达,其中,支承所述主轴(10)的第一轴承(21)至少包含一个向心推力轴承或推力轴承,工作时,液压轴向力作用在柱塞孔(81)封闭一端的缸体端面并经所述第一轴承(21)传递至柱塞泵或马达的壳体上。The dual axial piston motor according to claim 9, wherein the first bearing (21) supporting the main shaft (10) includes at least one centripetal thrust bearing or thrust bearing, and the hydraulic axial force The cylinder end surface acting on the closed end of the plunger hole (81) is transmitted to the housing of the plunger pump or the motor through the first bearing (21).
- 根据权利要求1所述的双联式轴向柱塞马达,其中,在所述斜盘(40)和滑盘(50)之间夹设有第三轴承(23),所述滑盘(50)以沿其径向受约束的状态支承在第三轴承(23)上。The dual axial piston motor according to claim 1, wherein a third bearing (23) is interposed between the swash plate (40) and the sliding plate (50), and the sliding plate (50) ) Is supported on the third bearing (23) in a state of being restrained in its radial direction.
- 根据权利要求11所述的双联式轴向柱塞马达,其中,所述斜盘(40)中部具有向外延伸的支承轴或支承轴销(49),所述滑盘(50)设置有中心通孔,所述第三轴承(23)夹设在滑盘(50)中心通孔内壁与支承轴或支承轴销(49)之间,所述滑盘(50)以沿其径向受约束状态支承在第三轴承(23)上。The dual axial piston motor according to claim 11, wherein the middle part of the swash plate (40) has a supporting shaft or a supporting shaft pin (49) extending outward, and the sliding plate (50) is provided with The third bearing (23) is sandwiched between the inner wall of the central through hole of the sliding plate (50) and the supporting shaft or the supporting shaft pin (49), and the sliding plate (50) is to receive radially The restrained state is supported on the third bearing (23).
- 根据权利要求11所述的双联式轴向柱塞马达,其中,所述斜盘(40)外周部设置有凸起的支承挡部(41a),所述第三轴承(23)夹设在滑盘(50)外侧与支承挡部(41a)内侧之间,所述滑盘(50)以沿其径向受约束状态支承在第三轴承(23)上。The dual axial plunger motor according to claim 11, wherein the outer periphery of the swash plate (40) is provided with a raised support stop (41a), and the third bearing (23) is sandwiched between Between the outer side of the sliding plate (50) and the inner side of the supporting block (41a), the sliding plate (50) is supported on the third bearing (23) in a state of being restrained in its radial direction.
- 根据权利要求1所述的双联式轴向柱塞马达,其中,所述柱塞(70)包含带锥形结构的连杆柱塞或者两端均设置有球头的连杆柱塞或者带万向铰的球面柱塞的一种,所述柱塞(70)一端可相对缸体(80)往复滑动的方式***缸体(80)的柱塞孔(81)内,另一端以相对滑盘(50)端面远离受限且能够倾动的状态固定在滑盘(50)的柱塞球窝(58)内,所述柱塞(70)上设置有连通柱塞球窝(58)和柱塞孔(81)的大孔径柱塞中心孔(72)。The dual axial plunger motor according to claim 1, wherein the plunger (70) comprises a connecting rod plunger with a tapered structure or a connecting rod plunger with a ball head at both ends or a belt A type of universal hinged spherical plunger. One end of the plunger (70) is inserted into the plunger hole (81) of the cylinder (80) in a reciprocating manner relative to the cylinder (80), and the other end is relatively sliding The disc (50) is fixed in the plunger ball socket (58) of the sliding disc (50) in a state where the end surface of the disc (50) is restricted away from and can be tilted. The plunger (70) is provided with a connecting plunger ball socket (58) and a post The central hole (72) of the large-diameter plunger of the plug hole (81).
- 根据权利要求1至14中任意一项所述的双联式轴向柱塞马达,其中,所述滑盘(50)与斜盘(40)之间夹设有配流盘(90),所述滑盘(50)支承在配流盘(90)上且与配流盘(90)保持滑动配合,所述配流盘(90)上设置有高、低压配流口(93、92),高压油液流经斜盘(40)上的配流油槽(42)、配流盘的配流口、滑盘(50)的油室(53a)、通油孔(53)、柱塞中心孔(72)和缸体柱塞孔(81),驱使缸体(80)和主轴(10)同步旋转。The dual axial piston motor according to any one of claims 1 to 14, wherein a valve plate (90) is interposed between the sliding plate (50) and the swash plate (40), and the The sliding plate (50) is supported on the valve plate (90) and maintains a sliding fit with the valve plate (90). The valve plate (90) is provided with high and low pressure orifices (93, 92) through which high-pressure oil flows The valve oil groove (42) on the swash plate (40), the valve port of the valve plate, the oil chamber (53a) of the sliding plate (50), the oil through hole (53), the plunger center hole (72) and the cylinder plunger The hole (81) drives the cylinder (80) and the main shaft (10) to rotate synchronously.
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CN110067692A (en) | 2019-07-30 |
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