CN111120198A - Hydraulic motor fixed by cylinder body - Google Patents

Hydraulic motor fixed by cylinder body Download PDF

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Publication number
CN111120198A
CN111120198A CN202010094475.7A CN202010094475A CN111120198A CN 111120198 A CN111120198 A CN 111120198A CN 202010094475 A CN202010094475 A CN 202010094475A CN 111120198 A CN111120198 A CN 111120198A
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China
Prior art keywords
window
oil
cylinder
flow distribution
oil inlet
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CN202010094475.7A
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Chinese (zh)
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杨健
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Individual
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Individual
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Priority to CN202010094475.7A priority Critical patent/CN111120198A/en
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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
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0435—Particularities relating to the distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0415—Cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/047—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the outer ends of the cylinders

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)

Abstract

A cylinder body fixed hydraulic motor comprises a static flow distribution surface and a rotary flow distribution surface, wherein a cylinder hole window, an oil inlet window and an oil outlet window are arranged on the static flow distribution surface; when the plunger is in the oil outlet section, a cylinder hole window communicated with the plunger is communicated with the oil outlet window through a flow distribution window, and oil is discharged from a cylinder hole; when the plunger is in the oil inlet section, a cylinder hole window communicated with the plunger is communicated with the oil inlet window through a flow distribution window, and oil enters a cylinder hole; the flow distribution window, the oil inlet window and the oil outlet window on the flow distribution surface are all arranged on the window belt of the cylinder hole, so that the width of the flow distribution belt can be effectively reduced, the structure of the flow distributor is more compact, and the variable displacement of the hydraulic motor can be realized by disconnecting the oil inlet channel of a part of the oil inlet window under the condition of not increasing the width of the flow distribution belt.

Description

Hydraulic motor fixed by cylinder body
Technical Field
The invention relates to the technical field of hydraulic motors, in particular to a hydraulic motor with a fixed cylinder body.
Background
At present, most of domestic shell rotary hydraulic motors are fixed by cylinder bodies, and rotary shells with guide rails output power. As is known, both the port plate motor and the pump are reversible, i.e. the hydraulic motor can also be used as a hydraulic pump, and according to the prior art, for the sake of understanding, the structural names and the related parameters in such hydraulic motors or hydraulic pumps are defined and explained in the following.
(1) In the cylinder body, the surface of the cylinder body contacting with the flow distributor is called a static flow distribution surface, the windows on the static flow distribution surface communicated with the plunger cylinder holes are called cylinder hole windows, the number of the cylinder hole windows is z, and the argument of the cylinder hole windows is αzThe central argument of two adjacent cylinder hole windows is ϕz。
When the plunger is at the oil inlet section of the track, oil enters the window of the cylinder hole from the oil inlet window through the flow distribution window, and the argument of the oil inlet window is αa。
When the plunger is at the oil outlet section of the track, oil enters the oil outlet window from the window of the cylinder hole through the flow distribution window, and the breadth angle of the oil outlet window is αb。
The argument between the oil inlet window and the cylinder hole window is αazThe argument between the oil outlet window and the cylinder hole window is αbzThe central argument of the two adjacent oil outlet windows and the central argument of the oil inlet window are ϕabThe edge width angles of two adjacent oil outlet windows and two adjacent oil inlet windows are αab。
The argument of the cylinder bore center and the center of the cylinder bore window communicating therewith is called the cylinder bore phase displacement argument βz。
For the convenience of distinction, the plungers in the upward direction are numbered as 1, and the plungers are numbered according to 1, 2 and 3 … in sequence along the clockwise direction, wherein the nth plunger is called as Qn; the cylinder hole window in the upward direction is numbered as 1, and the cylinder hole windows in the clockwise direction are numbered in sequence as 1, 2, 3 … Z, wherein the nth plunger is called Zn.
(2) Guide rail: the cylinder body is fixed, and the guide rail rotates relative to the cylinder body. The guide rail is specified to rotate clockwise, namely to rotate clockwise, and to rotate anticlockwise, namely to rotate reversely, and the rotation direction is not specified, and the guide rail rotates clockwise.
The guide rail action number is x, a near dead point D point and a near dead point F point are near dead zone central points of the guide rail, and a far dead point C point, a far dead point E point and a far dead zone G point are far dead zone central points of the guide rail; the angle of the zero-speed area at the C point is C, the angle of the zero-speed area at the D point is D, the angle of the zero-speed area at the E point is E, the angle of the zero-speed area at the F point is F, the angle of the zero-speed area at the G point is G, and the current-matching parameters are calculated by taking the angle C = D = E = F = G =0 in a general theoretical calculation.
DF corresponding breadth of action of ϕxGuide rail phase displacement argument βx=0, when rotating clockwise, the FE section is an oil outlet section, and the ED section is an oil inlet section; namely, the oil inlet section is arranged on the outer dead center in the rotating direction, and the oil outlet section is arranged on the outer dead center in the reverse rotating direction.
(3) A flow distributor: the flow distributor and the guide rail rotate synchronously relative to the cylinder body, so the logarithm of the flow distribution windows is equal to the action number of the guide rail, and the flow distribution windows can be communicated with the oil inlet windows and the oil outlet windows, so the number of the flow distribution windows is equal to the action number of the guide rail.
The number of the flow distribution windows is r, the central argument of two adjacent flow distribution windows is ϕrThe argument of the distribution window is αrThe argument between two adjacent current distribution windows is αr0. ϕr=2π/r，αr0=2π/r–αr。
The argument of the central line of the guide rail outer dead center and the central line of the current distribution window is called guide rail phase displacement argument βx。
(4) A flow distribution belt: the end-to-end curved surface belts formed by all windows and channels on the flow distribution surface rotating for a circle along the rotating central shaft of the hydraulic motor/pump are called flow distribution belts; the cylinder hole window is characterized in that a curved surface belt formed by rotating the cylinder hole window for one circle along the rotating center is called a cylinder hole window belt, a curved surface belt formed by rotating the oil inlet window for one circle along the rotating center is called an oil inlet window belt, a curved surface belt formed by rotating the oil outlet window for one circle along the rotating center is called an oil outlet window belt, and a curved surface belt formed by rotating the flow distribution window for one circle along the rotating center is called a flow distribution window belt. The width of the distribution belt is called as the width of the distribution belt, and the smaller the width of the distribution belt is, the more compact the distributor can be.
The swedish hagglongweijing motor is a radial shaft, flow-distributing plunger motor with a double-displacement cylinder fixed housing that rotates. The flow distribution belt of the Weijing motor comprises an oil inlet window B belt, an oil inlet window A belt, an oil outlet window C belt and three sealing belts. The hydraulic motor has the problems of complex flow distribution belt structure and large flow distribution belt width.
Patent document 1: application No.: 201621055806.1 (publication No. CN 206092285U) discloses a cylinder fixed hydraulic motor, the flow distribution structure is that there is a ring window on the inner and outer sides of the cylinder hole window, the cylinder hole window is connected with the ring oil inlet window or the oil outlet window through the flow distribution window to complete the flow distribution, the flow distribution structure also has the problems of large flow distribution width, large radial size of the flow distribution pair and complex structure.
Patent document 2: application No.: 201621249879.4 (publication No. CN 206221143U) discloses a fixed hydraulic motor with cylinder body, whose flow distribution structure is that two annular windows are arranged at two sides outside a cylinder hole window, the cylinder hole window is communicated with an annular oil inlet window or an oil outlet window through a bridge type flow distribution window to complete flow distribution, the flow distribution band comprises a cylinder hole window band, an oil outlet window band, an oil inlet window band and two sealing widths, and the flow distribution structure also has the problems of large flow distribution band width and overlarge structure size.
Disclosure of Invention
Aiming at the problems of large flow distribution bandwidth and large structural size in the prior art, the invention provides a hydraulic motor with a fixed cylinder body.
In order to achieve the purpose, the technical scheme adopted by the invention is as follows:
a cylinder stationary hydraulic motor comprising: the static flow distribution surface is provided with a cylinder hole window, an oil inlet window and an oil outlet window, the rotating flow distribution surface is provided with a flow distribution window, the flow distribution window is a groove which is inwards recessed along the rotating flow distribution surface, and the oil inlet window belt, the oil outlet window belt, the flow distribution window belt and the cylinder hole window belt are overlapped.
Furthermore, the number of the flow distribution windows is equal to the number of the guide rail functions, at any position of the guide rail, when the plunger is in the oil outlet section, the cylinder hole window is communicated with the oil outlet window through the flow distribution window, and when the plunger is in the oil inlet section, the cylinder hole window is communicated with the oil inlet window through the flow distribution window.
Furthermore, any cylinder hole window has at least one oil inlet window in the anticlockwise direction, and at least one oil outlet window in the clockwise direction.
Furthermore, the number of the cylinder hole windows on the static flow distribution surface is even, any cylinder hole window with the odd number has at least one oil inlet window in the anticlockwise direction, at least one oil outlet window in the clockwise direction, any cylinder hole window with the even number has at least one oil outlet window in the anticlockwise direction, and at least one oil inlet window in the clockwise direction.
Further, any adjacent cylinder bore window center fillets ϕ thereinz=2 pi/z, and the central argument ϕ of any adjacent oil inlet window and oil outlet windowab=2π/z。
Further, the guide rail phase displacement amplitude β of at least one group of guide railsx=0, guide rail phase shift argument β of at least one group of guide railsx=π/x。
Further, the cylinder bores connected to the odd-numbered cylinder bore windows have cylinder bore phase shift amplitudes βz=0, cylinder bores connected to even-numbered cylinder bore windows and having cylinder bore phase displacement argument βzAnd (n is an odd number).
Further, at least one of the oil inlet windows is divided into two independent oil inlet windows.
Further, at least one independent oil inlet window can be disconnected from the oil inlet channel.
Further, the on-off of at least one oil inlet window and the oil inlet channel can be controlled.
Compared with the prior art, the invention has the following beneficial effects: the oil inlet window belt, the oil outlet window belt, the flow distribution window belt and the cylinder hole window belt are overlapped, so that the width of the flow distribution belt can be effectively reduced, the structure of the flow distributor is more compact, and meanwhile, as no other flow distribution belt is arranged on the outer side of the cylinder hole window belt, the leakage in the width direction of the flow distribution belt is reduced, and the variable displacement of a hydraulic motor/pump can be realized under the condition of not increasing the width of the flow distribution belt.
Drawings
Fig. 1 is a schematic view of a flow distribution structure of a hydraulic motor of the present invention.
Fig. 2 is a schematic view of a hydraulic motor shaft flow distribution structure of the present invention.
FIG. 3 is a schematic diagram of the phase shift between the distribution window and the guide rail according to the present invention.
FIG. 4 is a schematic diagram of the phase displacement of the cylinder hole window and the cylinder hole in the present invention.
Fig. 5 is a schematic cross-sectional view of a ten-action three-plunger hydraulic motor of the present invention.
Fig. 6 is a schematic view showing the development of the components of a ten-action three-plunger hydraulic motor according to the present invention.
Fig. 7 is a schematic cross-sectional view of a ten-action six-ram hydraulic motor of the present invention.
Fig. 8 is an expanded view of the components of a ten-action six-plunger hydraulic motor of the present invention.
Fig. 9 is a schematic cross-sectional view of a ten-action nine-plunger hydraulic motor of the present invention.
Fig. 10 is an expanded view of the components of a ten-action nine-plunger hydraulic motor of the present invention.
Fig. 11 is a schematic cross-sectional view of a ten-action nine-plunger end-face port hydraulic motor of the present invention.
Fig. 12 is an expanded schematic view of the components of a ten-action nine-plunger end-face flow distribution hydraulic motor in the invention.
100, a cylinder body, 101, cylinder hole windows, 102, oil inlet windows, 102C, oil inlet windows C, 102D, oil inlet windows D, 103, oil outlet windows, 103C, oil outlet windows C, 103D, oil outlet windows D, 104, cylinder holes, 105, plungers, 106, oil inlet channels, 106C, oil inlet channels C, 106D, oil inlet channels D, 107, oil outlet channels, 107C, oil outlet channels C, 107D, oil outlet channels D, 200, guide rails, 200a, guide rails A, 200B, guide rails B, 201, oil outlet sections, 202, oil inlet sections, 300, flow distributors, 301, flow distribution windows, 400 and flow distribution belts.
Detailed Description
The embodiments and examples of the invention are further described below with reference to the accompanying drawings:
as is known, except for the valve type flow distribution type plunger pump which cannot be used as a motor, the flow distribution plate or the flow distribution shaft type plunger pump can be used as a hydraulic motor by changing the structure of a flow distribution device, and the two types of flow distribution plate or the flow distribution shaft type plunger pump can be reversible.
As shown in fig. 1, when the flow distribution structure is used as a pump, the guide rail 200 drives the plunger 105 to move horizontally, the oil inlet window 102 is actually an oil inlet of the pump, the oil outlet window 103 is actually an oil outlet of the pump, oil is sucked in the oil inlet section 202, and high-pressure oil is discharged in the oil outlet section 201.
When the hydraulic oil pump is used as a motor, the oil inlet window 102 is actually a pressure oil window, the oil outlet window 103 is actually an oil return window, pressure oil pushes the plunger 105 to move outwards in the oil inlet section 202 to drive the guide rail 200 to rotate to output power, and the plunger 105 retracts in the oil outlet section 201 to discharge oil through the oil outlet window 103.
As shown in fig. 1 and 2, a cylinder fixed hydraulic motor includes a stationary flow distribution surface and a rotary flow distribution surface, the stationary flow distribution surface has a cylinder hole window 101, an oil inlet window 102 and an oil outlet window 103, the rotary flow distribution surface has a flow distribution window 301, the flow distribution window 301 is a groove recessed inward along the rotary flow distribution surface, and on the flow distribution surface, the cylinder hole window 101 and the oil inlet window 102 or the oil outlet window 103 are communicated with each other through a space left by the groove on the flow distribution window 301.
In the prior art, an oil inlet window 102 and an oil outlet window 103 are arranged outside a cylinder hole window 101, oil is fed into the cylinder hole window 101 through a flow distribution window 301 by the outer oil inlet window 102, and the oil in the cylinder hole window 101 is discharged into the oil outlet window 103 outside the cylinder hole window 101 through the flow distribution window 301.
The flow distribution belt 400 has a large width and occupies a large space.
The invention enables the oil inlet window belt, the oil outlet window belt, the flow distribution window belt and the cylinder hole window belt to be superposed, and the width of the flow distribution belt 400 is minimum. The guide rail 200 and the distributor 300 rotate synchronously, and the number of the distribution windows 301 on the distributor 300 is equal to the number of the guide rail functions.
At any position of guide rail 200, when plunger 105 is in oil outlet section 201, cylinder bore window 101 communicates with oil outlet window 103 through flow distribution window 301, and when plunger 105 is in oil inlet section 202, cylinder bore window 101 communicates with oil inlet window 102 through flow distribution window 301.
As shown in fig. 1 and 2, points C, D, E, F and G on the guide rail 200 are intersections of the oil inlet and the oil outlet, and if point E is an end point of the oil inlet and is a starting point of the oil outlet, the oil inlet and the oil outlet are caused to be internally leaked, so that a closed dead zone should be formed near the points, but the effective operating amplitude of the curve is reduced due to the existence of the closed dead zone.
For ease of computational illustration, there may theoretically be no dead-space zone, i.e., the plunger 105 is either in the oil intake section 202 or in the oil output section 201. While one cylinder bore window 101 and the oil inlet window 102 and the oil outlet window 103 communicating therewith in the illustration are defined as one structural unit.
According to the schematic diagrams of the structural units in fig. 1 and 2, the motion of a single structural unit is analyzed as follows:
the plunger 105 on the structural unit shown in fig. 1 acts on the outer dead zone E point, and at this time, the continuous transition of the oil inlet and the oil outlet should satisfy:
αab=αaz+αz+αbz=αr
when the guide rail 200 rotates clockwise, the action point of the plunger 105 moves from the point E to the point F, the flow distribution window 301 rotates synchronously along with the guide rail 200 to communicate the cylinder hole window 101 and the oil outlet window 103, oil in the cylinder hole 104 is discharged, when the action point rotates to the point F, the flow distribution window 301 leaves the cylinder hole window 101 to disconnect the cylinder hole window 101 and the oil outlet window 103, at the moment, the next flow distribution window 301 is about to communicate the oil inlet window 102 and the cylinder hole window 101, and the continuous transition of oil inlet and outlet is met:
αz=αr0=2π/r–αr
α while port window 301 is away from cylinder bore window 101r0Coincides with cylinder bore window 101.
As shown in fig. 2, the plunger 105 on the structural unit acts on the inner dead point F of the guide rail 200 and continues to rotate clockwise, the acting point of the plunger 105 moves from the point F to the point G, in the process, the flow distribution window 301 rotates synchronously with the guide rail 200 to communicate with the cylinder hole window 101 and the oil inlet window 102, and oil enters the cylinder hole 104.
From the point E to the point G, the hydraulic motor completes the work of an action amplitude angle, and the continuous rotation periodically and continuously works.
In practical design, in order to prevent the oil inlet and outlet chambers from being directly communicated, the problem can be solved by independently reducing the argument of the flow distribution window 301.
As shown in fig. 5 and 6, embodiment 1 of the present invention: an application of a cylinder body fixing hydraulic motor in a ten-action three-plunger hydraulic motor.
One structural unit can independently fulfill the requirements of the pump, but when used as a hydraulic motor, it cannot actively rotate in the dead zone position, and the utilization of the cylinder block 100 is too low. Therefore, a plurality of structural units can be arranged on the cylinder block 100, improving the utilization rate of the cylinder block 100.
α is satisfied when the structural units can be arranged on the cylinder body 100 at will, but the oil inlet and outlet communication between two adjacent structural units can not existab≥αr。
For ease of manufacture, the structural elements are generally distributed evenly around the circumference.
As in this embodiment 1, in an ideal state, the structural parameters may be selected as:
x=10，r=10，z=3，αz=12°，αr=24°，αaz=αbz=6°，ϕab=π/z =60°，ϕz=2π/z=120°
satisfy αaz+αz+αbz=αrAnd αz=αr0=2π/r–αrThe operating conditions of (1).
At this time, oil inlet window 102, oil outlet window 103, and cylinder bore window 101 on the stationary flow distribution surface are circularly arranged in the order of oil inlet window 102-cylinder bore window 101-oil outlet window 103-oil inlet window 102-cylinder bore window 101-oil outlet window 103 clockwise.
Each structural unit meets the operating requirements of the motor and the analysis of the movement of the plunger 105 is not described separately.
As shown in fig. 6, the plunger 105Q 1 is located at the outer dead center, and the cylinder hole window 101Z 1 is not communicated with the oil inlet window 102 and the oil outlet window 103; q2 is located in the oil intake section 202, and Z2 is communicated with the oil intake window 102 through the flow distribution window 301, so that a force for rotating the guide rail 200 in a clockwise direction is generated; q3 is located in the oil outlet section 201, and Z3 is communicated with the oil outlet window 103 through the distribution window 301 to discharge oil.
As can be seen from the description of embodiment 1, α shows that when the number z of cylinder hole windows 101 increasesaAnd αbWill become smaller and smaller, which limits the increase in the number of cylinder bore windows 101.
In order to increase the number of the cylinder hole windows 101 continuously, one cylinder hole window 101 can be added between two adjacent structural units, and the cylinder hole window 101 is respectively connected with the oil outlet window 103 and the oil inlet window 102 on the adjacent structural units to form a reverse structural unit, namely, in the rotating direction, the positions of the oil inlet window 102 and the oil outlet window 103 are exchanged compared with the structural units.
The reverse structure unit can make the newly added plunger 105 on the cylinder hole window 101 work disorderly to generate the force for preventing the motor from rotating, and influence the normal work of the motor, and in order to make the reverse structure unit meet the work requirement, the phase displacement amplitude angle β of the guide rail can be changedx(shown in FIG. 3) and cylinder bore phase displacement argument βz(as shown in fig. 4), or both amplitudes may be changed to meet the operational requirements.
As shown in fig. 7 and 8, embodiment 2 of the present invention: an application of a cylinder fixed hydraulic motor on a ten-action six-plunger hydraulic motor.
After the addition of the reverse structural unit, in order to realize the working requirement, the embodiment 2 changes the amplitude β of the phase displacement of the guide railxTo be implemented.
The structural parameters are as follows:
x=10，r=10，z=6，αz=12°，αr=24°，αaz=αbz=6°，αa=αb=36°，ϕab=2π/z =60°，ϕz=2π/z=60°。
satisfy αaz+αz+αbz=αrAnd αz=αr0=2π/r–αrThe operating conditions of (1).
Track phase displacement amplitude β of track A200ax=0。
Track phase displacement argument β of track B200Bx=π/x=18°。
Cylinder bore 104 communicating with odd-numbered cylinder bore windows 101 (Z1, Z3, Z5), plunger 105 (Q1, Q3, Q5) inside acting on guide rail a200 a; cylinder bore 104 communicating with even-numbered cylinder bore windows 101 (Z2, Z4, Z6), and plunger 105 (Q2, Q4, Q6) inside acts on guide rail B200B.
At this time, oil inlet window 102, oil outlet window 103, and cylinder bore window 101 on the stationary metering face are cyclically arranged in the clockwise direction of oil inlet window 102, cylinder bore window 101, oil outlet window 103, cylinder bore window 101, oil inlet window 102, cylinder bore window 101, oil outlet window 103, cylinder bore window 101.
The odd-numbered cylinder hole windows 101 are structural units and meet working requirements, and the even-numbered cylinder hole windows 101 are reverse structural units.
The reverse structure unit, cylinder hole window 101 anticlockwise is oil outlet window 103, clockwise is oil inlet window 102, if act on βxIn the guide rail a200a of =0, a force for blocking the rotation of the motor is generated, so that the motor cannot normally operate, and since the action sections of the guide rail B200B and the guide rail a200a are opposite, the phase of the plunger 105 of the reversing structure unit is corrected after acting on the guide rail B200B, so that the plunger 105 communicated with the reversing structure unit acts on the correct guide rail section, so that the motor normally operates.
As shown in fig. 8, the plunger 105Q 1 is located at the outer dead center of the guide rail a200a, and the cylinder hole window 101Z 1 is not communicated with the oil inlet window 102 and the oil outlet window 103; q2 is located in the oil intake section 202 of the guide rail B200B, and Z2 is communicated with the oil intake window 102 through the flow distribution window 301, so that a force for rotating the guide rail in a clockwise direction is generated; q3 is located in the oil intake section 202 of the guide rail A200a, and Z3 is communicated with the oil intake window 102 through the distribution window 301, so that a force for rotating the guide rail in a clockwise direction is generated; q4 is positioned at the inner dead center of the guide rail B200B, and the cylinder hole window 101Z 4 is not communicated with the oil inlet window 102 and the oil outlet window 103; q5 is located at the oil outlet section 201 of the guide rail A200a, and Z5 is communicated with the oil outlet window 103 through the distributing window 301 to discharge oil; q6 is located in the oil outlet section 201 of the guide rail B200B, and Z6 is communicated with the oil outlet window 103 through the distribution window 301 to discharge oil.
As can be seen from the above, this embodiment 2 satisfies the working requirements.
As shown in fig. 9 and 10, embodiment 3 of the present invention: an application of a cylinder body fixed hydraulic motor on a ten-action nine-plunger hydraulic motor.
Embodiment 2 can increase the utilization rate of the cylinder block 100, but increases the thickness of the hydraulic motor since the plunger 105 is divided into at least two working bank surfaces.
In order to increase the number of plungers 105 without increasing the thickness of the motor, it is also possible to increase the cylinder bore phase displacement argument β by changing the cylinder bore phase displacement argument β of the inverted structural unitzTo locate the plunger 105 on the correct track section.
In embodiment 2, the angle between the outer dead center and the inner dead center is n · pi/x (n is an odd number), and the guide rail 200 has a period of 2 pi/x, so that only one angle pi/x is provided, and if the action of the reverse structure unit is not changed, the guide rail can be changed by changing the phase displacement amplitude angle of the cylinder hole
βzAnd = n · pi/x (n is an odd number) to cause the plunger 105 in the cylinder hole 104 of the inverted structural unit to act on the correct rail section.
Embodiment 3 changes cylinder bore phase displacement amplitude βz= pi/x =18 ° to achieve the active region problem of the inverted structural unit.
The structural parameters are as follows:
x=10，r=10，z=9，αz=12°，αr=24°，αaz=αbz=6°，αac=αad=12°，αb=36°，ϕz=60°。
satisfy αaz+αz+αbz=αrAnd αz=αr0=2π/r–αrThe operating conditions of (1).
The oil inlet window 102 is divided into two independent oil inlet windows C102C and an oil inlet window D102D in the clockwise direction, wherein the oil inlet window C102C is communicated with the oil inlet channel C106C, and the oil inlet window D102D is communicated with the oil inlet channel D106D.
At this time, oil intake window 102, oil outlet window 103, and cylinder bore window 101 on the stationary metering face are cyclically arranged in a clockwise direction in the order of oil intake window C102C-oil intake window D102D-cylinder bore window 101-oil outlet window 103-cylinder bore window 101-oil intake window C102C-oil intake window D102D-cylinder bore window 101-oil outlet window 103-cylinder bore window 101-oil intake window C102C-oil intake window D102D-cylinder bore window 101-oil outlet window 103-cylinder bore window 101.
Odd-numbered cylinder bore windows 101 (Z1, Z3, Z5) are each in communication with one plunger 105, even-numbered cylinder bore windows 101 (Z2, Z4, Z6) are each in communication with two plungers 105, and cylinder bore phase displacement argument β of the two cylinder bores 104 from the center of cylinder bore window 101z= π/x =18 °; wherein oil-taking window C102C is adjacent to cylinder hole window 101 whose number is an even number, and oil-taking window D102D is adjacent to cylinder hole window 101 whose number is an odd number.
In embodiment 2, each oil inlet window 102 can feed liquid to two adjacent cylinder hole windows 101 in the clockwise direction and the counterclockwise direction.
In example 3, oil feed window C102C feeds even-numbered cylinder bore windows 101, and oil feed window D102D feeds odd-numbered cylinder bore windows 101.
As shown in fig. 10, the plunger 105Q 1 is located at the outer dead center of the guide rail 200, and the cylinder hole window 101Z 1 is not communicated with the oil inlet window 102 and the oil outlet window 103; q2, Q3 are located in the oil intake section 202 of the rail 200, and Z2 communicates with the oil intake window C102C through the distribution window 301, generating a force that rotates the rail 200 in a clockwise direction; q4 is located in the oil intake section 202 of the rail 200, and Z3 is in communication with the oil intake window D102D through the port window 301, creating a force that rotates the rail 200 in a clockwise direction; q5 and Q6 are positioned at the inner dead center of the guide rail 200, and the cylinder hole window 101Z 4 is not communicated with the oil inlet window 102 and the oil outlet window 103; q7 is located in the oil outlet section 201 of the guide rail 200, and Z5 is communicated with the oil outlet window 103 through the distribution window 301 to discharge oil; q8, Q9 are located in the oil outlet section 201 of the guide rail 200, and Z6 is communicated with the oil outlet window 103 through the distribution window 301 to discharge oil.
As can be seen from the above, this embodiment 3 satisfies the working requirements.
Communicating the oil inlet window C102C with the oil pressing pipeline A1, communicating the oil inlet window D102D with the oil pressing pipeline A2, and if the displacement of each plunger 105 is V:
when pressure oil is supplied to both A1 and A2, the displacement of the motor is 9V (Q1-Q9).
When pressure oil is introduced into A1 and pressure oil is not introduced into A2, the displacement of the motor is 6V (Q2, Q3, Q5, Q6, Q8 and Q9).
If pressure oil is supplied to A2 and pressure oil is not supplied to A1, the displacement of the motor is 3V (Q1, Q4, Q7).
Therefore, by disconnecting a portion of the individual oil intake windows 102 from the pressurized oil, the displacement of the motor can be varied.
As shown in fig. 11 and 12, embodiment 4 of the present invention: an application of a cylinder body fixed hydraulic motor on a ten-action nine-plunger end face flow distribution hydraulic motor.
Embodiment 3 can realize that the displacement when the motor rotates clockwise changes, and when anticlockwise rotates, former oil feed window 102 becomes out oil window 103, and former oil outlet window 103 becomes oil feed window 102, and as can be known from fig. 9, when anticlockwise rotates, oil feed window 102 becomes 3, though can change the displacement like the displacement when just rotating like this, can not change the displacement.
In order to change the displacement of the motor in the positive and negative rotation, the oil inlet window 102 and the oil outlet window 103 are designed into two independent windows.
The structural parameters are as follows:
x=10，r=10，z=9，αz=12°，αr=24°，αaz=αbz=6°，αac=αad=12°，αbc=αbd=12°，ϕz=60°。
satisfy αaz+αz+αbz=αrAnd αz=αr0=2π/r–αrThe operating conditions of (1).
The oil inlet window 102 is divided into two independent oil inlet windows C102C and an oil inlet window D102D in the clockwise direction, wherein the oil inlet window C102C is communicated with the oil inlet channel C106C, and the oil inlet window D102D is communicated with the oil inlet channel D106D. The oil outlet window 103 is divided into two independent oil outlet windows C103C and D103D in the clockwise direction, wherein the oil outlet window C103C is communicated with the oil outlet channel C107C, and the oil outlet window D103D is communicated with the oil outlet channel D107D.
At this time, oil intake window 102, oil outlet window 103, and cylinder bore window 101 on the static flow-metering surface are cyclically arranged in a clockwise direction according to the sequence of oil intake window C102C-oil intake window D102D-cylinder bore window 101-oil outlet window C103C-oil outlet window D103D-cylinder bore window 101-oil inlet window C102C-oil inlet window D102D-cylinder bore window 101-oil outlet window C103C-oil outlet window D103D-cylinder bore window 101-oil intake window C102C-oil inlet window D102D-cylinder bore window 101-oil outlet window C103C-oil outlet window D103D-cylinder bore window 101.
The structure of embodiment 4 is similar to that of embodiment 3, and the curved surface section acting in the reverse rotation and the forward rotation is changed due to the change of the oil inlet and outlet window 103.
As with any of the hydraulic motors of fig. 5-12, when any of the oil intake windows 102 is disconnected from the oil intake passage 106, no fluid flows into the cylinder bore window 101 in cooperation with it, and the motor displacement is reduced, as in fig. 5, when the oil intake window 102 in the counterclockwise direction of Z1 is disconnected from the oil intake passage 106, Z1 is no longer engaged, and the motor displacement is reduced.
The present invention is not limited to the above-described embodiments, and those skilled in the art will be able to make various modifications without inventive changes from the above-described structures, and fall within the scope of the present invention.

Claims (10)

1. A cylinder stationary hydraulic motor comprising:
a static flow distribution surface, wherein the static flow distribution surface is provided with a cylinder hole window, an oil inlet window and an oil outlet window,
the rotary flow distribution surface is provided with a flow distribution window which is a groove sunken inwards along the rotary flow distribution surface,
the device is characterized in that the oil inlet window belt, the oil outlet window belt, the flow distribution window belt and the cylinder hole window belt are overlapped.
2. A cylinder-fixed hydraulic motor as claimed in claim 1, wherein the number of distribution windows is equal to the number of guide rail functions,
at any position of the guide rail, when the plunger is in the oil outlet section, the cylinder hole window is communicated with the oil outlet window through the flow distribution window, and when the plunger is in the oil inlet section, the cylinder hole window is communicated with the oil inlet window through the flow distribution window.
3. The cylinder block fixed hydraulic motor of claim 1, wherein any cylinder bore window has at least one oil inlet window in a counter-clockwise direction and at least one oil outlet window in a clockwise direction.
4. The cylinder block fixed hydraulic motor of claim 1, wherein the number of cylinder bore windows on the stationary port surface is even, any cylinder bore window with odd number has at least one oil inlet window in the counterclockwise direction, at least one oil outlet window in the clockwise direction, any cylinder bore window with even number has at least one oil outlet window in the counterclockwise direction, and at least one oil inlet window in the clockwise direction.
5. A cylinder block stationary hydraulic motor as in claim 4, wherein any adjacent cylinder bore window center fillet ϕz=2 pi/z, and the central argument ϕ of any adjacent oil inlet window and oil outlet windowab=2π/z。
6. A cylinder-stationary hydraulic motor as claimed in any one of claims 1 or 4, wherein the guide rail phase shift argument β of at least one set of guide railsx=0, guide rail phase shift argument β of at least one group of guide railsx=π/x。
7. According to claimA cylinder block stationary hydraulic motor as claimed in any one of claims 1 or 4, wherein cylinder bores connected to odd-numbered cylinder bore windows have cylinder bore phase displacement amplitudes βz=0，
Cylinder bore associated with even numbered cylinder bore windows having cylinder bore phase shift argument βzAnd (n is an odd number).
8. The cylinder stationary hydraulic motor of claim 4, wherein at least one oil intake window is divided into two separate oil intake windows.
9. A cylinder stationary hydraulic motor as in claim 8, wherein at least one independent oil intake window can be disconnected from the oil intake passage.
10. The hydraulic motor with the fixed cylinder body as claimed in any one of claims 1 to 5, wherein the on-off of at least one oil inlet window and the oil inlet channel can be controlled.
CN202010094475.7A 2020-02-16 2020-02-16 Hydraulic motor fixed by cylinder body Pending CN111120198A (en)

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Application Number Priority Date Filing Date Title
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021160005A1 (en) * 2020-02-16 2021-08-19 杨健 Cylinder body fixed hydraulic motor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021160005A1 (en) * 2020-02-16 2021-08-19 杨健 Cylinder body fixed hydraulic motor

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