WO2021160005A1

WO2021160005A1 - Cylinder body fixed hydraulic motor

Info

Publication number: WO2021160005A1
Application number: PCT/CN2021/075144
Authority: WO
Inventors: 杨健; 颜继
Original assignee: 杨健
Priority date: 2020-02-16
Filing date: 2021-02-04
Publication date: 2021-08-19
Also published as: CN211598918U

Abstract

A cylinder body fixed hydraulic motor, comprising a static flow distribution surface and a rotary flow distribution surface. The static flow distribution surface is provided with a cylinder hole window (101), an oil inlet window (102) and an oil outlet window (103), the rotary flow distribution surface is provided with a flow distribution window (301), and the flow distribution window (301) is a groove recessed inwards along the rotary flow distribution surface; when a plunger (105) is in an oil outlet section (201), the cylinder hole window (101) in communication with the plunger (105) is in communication with the oil outlet window (103) by means of the flow distribution window (301), and an oil liquid is discharged from a cylinder hole (104); when the plunger (105) is in an oil inlet section (202), the cylinder hole window (101) in communication with the plunger (105) is in communication with the oil inlet window (102) by means of the flow distribution window (301), and the oil liquid enters the cylinder hole (104); the flow distribution window (301), the oil inlet window (102) and the oil outlet window (103) on the flow distribution surfaces are all arranged on a cylinder hole window belt. The hydraulic motor can effectively reduce the width of a flow distribution belt, so that the structure of a flow distributor is more compact; and under the condition that the width of the flow distribution belt is not increased, the variable displacement of the hydraulic motor can also be achieved by disconnecting a part of an oil inlet channel of the oil inlet window.

Description

Cylinder fixed hydraulic motor

Technical field

The invention relates to the technical field of hydraulic motors, in particular to a hydraulic motor with a fixed cylinder.

Background technique

At present, most of the domestic shell-rotating hydraulic motors are fixed by the cylinder, and the rotating shell with guide rails outputs power. As we all know, the valve plate motor and the pump are both reversible, that is, hydraulic motors can also be used as hydraulic pumps.

The current commonly used motor is a radial shaft distribution plunger motor with a double-displacement cylinder block and a fixed housing rotating. The distribution belt includes oil inlet window B belt, oil inlet window A belt, oil outlet window C belt and three sealing belts. This kind of hydraulic motor has the problem of complicated structure of the distribution belt and large width of the distribution belt.

In the existing fixed cylinder block hydraulic motor, some of the flow distribution structure is that there is an annular window on both sides of the cylinder bore window. The distribution structure also has the problems of large distribution band width, large radial size of the distribution pair, and complex structure.

There are also fixed-cylinder hydraulic motors whose flow distribution structure is that there are two annular windows on both sides of the cylinder hole window. The cylinder hole window is connected to the annular oil inlet window or the oil outlet window through the bridge-type flow distribution window to complete the flow distribution. The flow distribution belt includes a cylinder hole window belt, an oil outlet window belt, an oil inlet window belt and two sealing widths. The flow distribution structure also has the problem of a large distribution belt width and an excessively large structure size.

Summary of the invention

Aiming at the problems of large distribution band width and large structural size existing in the above prior art, the present invention provides a cylinder fixed hydraulic motor. The distribution structure can effectively reduce the distribution band width and make the distributor structure more compact.

In order to achieve the above objectives, the technical solutions adopted by the present invention are:

A cylinder fixed hydraulic motor, comprising: a static flow distribution surface, the static flow distribution surface has a cylinder hole window, an oil inlet window and an oil outlet window, a rotating flow distribution surface, the rotating flow distribution surface has a flow distribution window, and the flow distribution surface The window is a groove recessed inward along the rotating flow distribution plane, in which the oil inlet window belt, the oil outlet window belt, the flow distribution window belt and the cylinder bore window belt overlap.

Further, the number of flow distribution windows is equal to the number of actions of the guide rail. At any position of the guide rail, when the plunger is in the oil outlet section, the cylinder hole window communicates with the oil outlet window through the flow distribution window. When the plunger is in the oil inlet section, the cylinder The hole window communicates with the oil inlet window through the flow distribution window.

Further, any one of the cylinder bore windows has at least one oil inlet window in a counterclockwise direction, and at least one oil outlet window in a clockwise direction.

Further, the number of cylinder hole windows on the stationary distribution surface is an even number, any cylinder hole window with an odd number has at least one oil inlet window in the counterclockwise direction, and at least one oil outlet window in the clockwise direction, and any number is an even number. The cylinder bore window has at least one oil outlet window in the counterclockwise direction, and at least one oil inlet window in the clockwise direction.

Further, the central argument of any adjacent cylinder bore window φ _z = 2π/z, and the central argument of any adjacent oil inlet window and outlet window φ _ab = 2π/z.

Furthermore, at least one of the guide rails has a guide rail phase displacement angle β _x =0, and at least one of the guide rails has a guide rail phase displacement angle β _x =π/x.

Further, the cylinder bore connected to the odd-numbered cylinder bore window has its cylinder bore phase displacement angle β _z =0, and the cylinder bore connected to the even-numbered cylinder bore window has its cylinder bore phase displacement angle β _z = n·π/x (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 connection between at least one oil inlet window and the oil inlet channel can be controlled.

According to the prior art, in order to facilitate understanding, the structure names and related parameters in this type of hydraulic motors or hydraulic pumps are now collectively defined and explained as follows.

(1) Cylinder body: The surface of the cylinder body that is in contact with the distributor is called the static distribution surface, and the window on the static distribution surface that communicates with the plunger cylinder bore is called the cylinder bore window. The number of cylinder bore windows is z, and the cylinder bore window The argument is α _z , and the central argument of two adjacent cylinder hole windows is φ _z .

The channel through which the liquid enters the stationary distribution surface from the cylinder is called the oil inlet channel, and the window formed by the oil inlet channel on the stationary distribution surface is called the oil inlet window; The oil window enters the cylinder bore window through the flow distribution window, and the angle of the oil inlet window is α _a .

The channel through which the liquid enters the cylinder from the static distribution surface is called the oil outlet channel, and the window formed by the oil outlet channel on the stationary distribution surface is called the oil outlet window; The hole window enters the oil outlet window through the flow distribution window, and the argument of the oil outlet window is α _b .

The argument between the oil inlet window and the cylinder bore window is α _az , the argument between the oil outlet window and the cylinder bore window is α _bz , the centre of the two adjacent oil outlet windows and the centre of the oil inlet window are φ _ab , The edge angle of the two adjacent oil outlet windows and oil inlet windows is α _ab .

The argument between the center of the cylinder bore and the center of the cylinder bore window communicating with it is called the phase displacement argument β _{z of the} cylinder bore.

In order to facilitate the distinction, the upward plunger is numbered 1, and the plunger in the clockwise direction is numbered according to 1, 2, 3..., the nth plunger is called Qn; the upward cylinder hole window is numbered 1. , Along the clockwise direction, the cylinder hole windows are numbered according to 1, 2, 3...Z, and the nth plunger is called Zn.

(2) Guide rail: the cylinder body is fixed, and the guide rail rotates relative to the cylinder body. It is now stipulated that when the guide rail rotates in a clockwise direction, it is forward rotation, and when it rotates in a counterclockwise direction, it is reverse rotation. If the direction of rotation is not clear, the guide rail is always rotated in the clockwise direction.

The number of action of the guide rail is x, the near dead center point D and F are the center points of the near dead zone of the guide rail, and the far dead center points C, E and G are the center points of the far dead zone of the guide rail; the angle of the zero speed zone at point C is Δc, the argument of zero speed zone at point D is Δd, the argument of zero speed zone at point E is Δe, the argument of zero speed zone at point F is Δf, and the argument of zero speed zone at point G is Δg. The general theoretical calculation is Δc=Δd =Δe=Δf=Δg=0 to calculate each distribution parameter.

The action angle corresponding to DF is φ _x , the phase displacement angle of the guide rail β _x =0, when rotating clockwise, the FE section is the oil outlet section, and the ED section is the oil inlet section; that is, the direction of the outer dead center rotation is the inlet section. In the oil section, the direction of rotation is reversed as the oil outlet section.

(3) Distributor: the distributor and the guide rail rotate synchronously with respect to the cylinder, so the logarithm of the distribution window is equal to the number of action of the guide rail. Because the distributor window of the present invention can communicate with the oil inlet window and the oil outlet window, the distributor of the present invention The number of windows is equal to the number of guide rails.

The number of distribution windows is r, the central argument of two adjacent distribution windows is φ _r , the argument of the distribution windows is α _r , and the argument between two adjacent distribution windows is α _r0 . Then φ _r = 2π/r, α _r0 = 2π/r-α _r .

The argument between the centerline of the outer dead center of the guide rail and the center line of the distribution window is called the guide rail phase displacement argument β _x .

(4) Distribution belt: all windows and channels on the distribution surface rotate along the central axis of the hydraulic motor/pump to form a curved band connected end-to-end, which is called the distribution belt; the curved band formed by the cylinder hole window rotating one circle along the center of rotation is called the distribution belt. It is a cylinder hole window belt. The curved belt formed by one revolution of the oil inlet window along the center of rotation is called the oil inlet window belt, and the curved belt formed by the oil outlet window rotating one round along the center of rotation is called the oil outlet window belt, and the flow distribution window rotates along the center of rotation. The curved surface zone formed in one round is called the distribution window zone. The width of the distribution belt is called the distribution belt width. The smaller the distribution belt width, the smaller and more compact the distributor can be.

Compared with the prior art, the present invention has the following beneficial effects: since the four of the oil inlet window belt, the oil outlet window belt, the flow distribution window belt and the cylinder bore window belt of the present invention overlap, the width of the flow distribution belt can be effectively reduced, The structure of the distributor is more compact. At the same time, because there is no other distribution belt outside the cylinder hole window belt, the leakage in the width direction of the distribution belt is reduced. Further, the hydraulic motor/pump can be changed without increasing the width of the distribution belt. Displacement.

Description of the drawings

Fig. 1 is a schematic diagram of the flow distribution structure of the hydraulic motor of the present invention.

Fig. 2 is a schematic diagram of the shaft distribution structure of the hydraulic motor of the present invention.

Fig. 3 is a schematic diagram of the phase displacement of the distribution window and the guide rail in the present invention.

Figure 4 is a schematic diagram of the phase displacement of the cylinder bore window and the cylinder bore in the present invention.

Figure 5 is a schematic cross-sectional view of the ten-acting three-plunger hydraulic motor in the present invention.

Fig. 6 is an exploded schematic diagram of the parts of the ten-acting three-plunger hydraulic motor in the present invention.

Fig. 7 is a schematic cross-sectional view of the ten-acting six-piston hydraulic motor in the present invention.

Figure 8 is an exploded schematic diagram of the ten-acting six-plunger hydraulic motor parts in the present invention.

Figure 9 is a schematic cross-sectional view of the ten-acting nine-plunger hydraulic motor in the present invention.

Fig. 10 is an exploded schematic diagram of the parts of the ten-acting nine-plunger hydraulic motor in the present invention.

Figure 11 is a schematic cross-sectional view of a hydraulic motor with ten-acting nine-plunger end face distribution in the present invention.

Figure 12 is an exploded schematic view of the parts of the ten-acting nine-plunger end-distribution hydraulic motor in the present invention.

Shown in the picture: 100, cylinder block, 101, cylinder hole window, 102, oil inlet window, 102c, oil inlet window C, 102d, oil inlet window D, 103, oil outlet window, 103c, oil outlet window C, 103d , Oil outlet window D, 104, cylinder bore, 105, plunger, 106, oil inlet channel, 106c, oil inlet channel C, 106d, oil inlet channel D, 107, oil outlet channel, 107c, oil outlet channel C, 107d , Oil outlet channel D, 200, guide rail, 200a, guide rail A, 200b, guide rail B, 201, oil outlet section, 202, oil inlet section, 300, flow distributor, 301, flow distribution window, 400, flow distribution belt.

Detailed ways

The following is a further description of the embodiments and examples of the present invention with reference to the accompanying drawings.

Example 1

As we all know, except that the valve-type flow-distribution type cannot be used as a motor, the piston pump can be used as a hydraulic motor by changing the structure of the flow-distributor with a valve plate or a shaft-type plunger pump. The two are reversible.

The flow distribution structure shown in Figure 1, when used as a pump, the guide rail 200 drives the plunger 105 to translate, the oil inlet window 102 is actually the oil suction port of the pump, and the oil outlet window 103 is actually the oil pressure port of the pump. The section 202 sucks in oil, and then discharges the high-pressure oil in the oil outlet section 201.

When used as a motor, the oil inlet window 102 is actually a pressure oil window, and the oil outlet window 103 is actually an oil return window. The pressure oil pushes the plunger 105 outside the oil inlet section 202 to drive the guide rail 200 to rotate and output power. The section 201 plunger 105 retracts through the oil outlet window 103 to discharge the oil.

As shown in Figure 1 and Figure 2, a hydraulic motor with a fixed cylinder block includes a static distribution surface and a rotating distribution surface. The stationary distribution surface has a cylinder hole window 101, an oil inlet window 102 and an oil outlet window 103. There is a distribution window 301. The distribution window 301 is a groove recessed inward along the rotating distribution surface. On the distribution surface, the cylinder hole window 101 and the oil inlet window 102 or the oil outlet window 103 are the spaces left by the groove on the distribution window 301 Connected.

In the prior art, the cylinder hole window 101 has an oil inlet window 102 and an oil outlet window 103 outside. The outer oil inlet window 102 sends the oil into the cylinder hole window 101 through the distribution window 301, and the oil in the cylinder hole window 101 The oil is drained into the oil outlet window 103 outside the cylinder bore window 101 through the flow distribution window 301.

This kind of distribution belt is 400 wide and occupies a lot of space.

The invention makes the four of the oil inlet window belt, the oil outlet window belt, the flow distribution window belt and the cylinder hole window belt overlap, and the flow distribution belt 400 has the smallest width. Wherein, the guide rail 200 and the distributor 300 of the present invention rotate synchronously, and the number of distributor windows 301 on the distributor 300 is equal to the number of guide rails.

At any position of the guide rail 200, when the plunger 105 is in the oil outlet section 201, the cylinder bore window 101 communicates with the oil outlet window 103 through the flow distribution window 301, and when the plunger 105 is in the oil inlet section 202, the cylinder bore window 101 passes through The flow distribution window 301 communicates with the oil inlet window 102.

As shown in Figure 1 and Figure 2, the points C, D, E, F, and G on the guide rail 200 are the intersection of the oil inlet and the oil outlet. For example, the E point is the end point of the oil inlet and the oil outlet. The starting point of the oil will cause the oil in and out of the oil cavity to communicate and leak, so there should be a closed dead zone near these points, but the existence of the closed dead zone will reduce the effective working angle of the curve.

In order to facilitate calculation and explanation, theoretically, there may be no closed dead zone, that is, the plunger 105 is either in the oil inlet section 202 or the oil outlet section 201. At the same time, a cylinder hole window 101 and the oil inlet window 102 and the oil outlet window 103 connected with it are defined as a structural unit.

According to the schematic diagrams of the structural units in Figure 1 and Figure 2, the motion analysis of a single structural unit is as follows:

The plunger 105 on the structural unit as shown in Figure 1 acts on the dead zone E point outside the band. At this time, the continuous transition of the inlet and outlet ports should meet:

α _ab =α _az +α _z +α _bz =α _r

When the guide rail 200 rotates clockwise, the point of action of the plunger 105 moves from point E to point F, and the flow distribution window 301 rotates synchronously with the guide rail 200, connecting the cylinder bore window 101 and the oil outlet window 103, and the oil in the cylinder bore 104 is discharged. When rotating to point F, the flow distribution window 301 leaves the cylinder bore window 101 and disconnects the cylinder bore window 101 and the oil outlet window 103. At this time, the next flow distribution window 301 is about to connect the oil inlet window 102 and the cylinder bore window 101. The continuous transition of oil inlet and outlet should meet :

α _z ＝α _r0 ＝2π/r–α _r

That is, while the distribution window 301 is away from the cylinder bore window 101, _{the argument position of α r0} coincides with the cylinder bore window 101.

As shown in Figure 2, the plunger 105 on the structural unit acts on the inner dead center point F of the guide rail 200 and continues to rotate clockwise. The point of action of the plunger 105 moves from point F to point G. During this process, the flow distribution window 301 With the synchronous rotation of the guide rail 200, the cylinder hole window 101 and the oil inlet window 102 are connected, and the oil enters the cylinder hole 104.

From point E to point G, the hydraulic motor completes the work of an angle of action, and continues to rotate and will continue to work periodically.

In the actual design, in order to prevent the direct communication between the inlet and outlet of the oil chamber, it can be solved by separately reducing the angle of the distribution window 301.

As shown in Figures 5 and 6, it is the first embodiment of the present invention: an application of a hydraulic motor with a fixed cylinder block on a ten-acting three-piston hydraulic motor.

A 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 rate of the cylinder 100 is too low. Therefore, multiple structural units can be arranged on the cylinder block 100 to improve the utilization rate of the cylinder block 100.

The structural units can be arbitrarily arranged on the cylinder 100, but there can be no oil connection between two adjacent structural units. At this time, it should satisfy: α _ab ≥ _{α r} .

In order to facilitate processing and manufacturing, structural units are generally evenly distributed on the circumference.

As in Example 1, in an ideal state, the structural parameters can be selected as:

x=10, r=10, z=3, α _z =12°, α _r =24°, α _az =α _bz =6°, φ _ab =π/z=60°, φ _z =2π/z= 120°

It satisfies the working conditions of α _az + α _z + α _bz = α _r and α _z = α _r0 = 2π/r-α _r .

At this time, the oil inlet window 102, the oil outlet window 103 and the cylinder bore window 101 on the static valve surface are clockwise in accordance with the oil inlet window 102-cylinder bore window 101-oil outlet window 103-oil inlet window 102-cylinder bore window 101 -Oil outlet window 103-Oil inlet window 102-Cylinder hole window 101-Oil outlet window 103 are arranged cyclically in order.

Each structural unit meets the working requirements of the motor, and the movement analysis of the plunger 105 will not be described separately.

As shown in Figure 6, the plunger 105Q1 is located at the outer dead center, and the cylinder bore window 101 Z1 is not connected to the oil inlet window 102 and the oil outlet window 103; Q2 is located in the oil inlet section 202, and Z2 is connected to the oil inlet window through the flow distribution window 301 102. Generate a force to rotate the guide rail 200 in a clockwise direction; Q3 is located in the oil outlet section 201, and Z3 is connected to the oil outlet window 103 through the distribution window 301 to discharge oil.

It can be seen from the description of Embodiment 1 that when the number z of cylinder bore windows 101 increases, α _a and α _b will become smaller and smaller, which limits the increase in the number of cylinder bore windows 101.

In order to continue to increase the number of cylinder bore windows 101, a cylinder bore window 101 can be added between two adjacent structural units. This cylinder bore window 101 respectively borrows the oil outlet window 103 and the oil inlet window 102 on the adjacent structural unit to form A reverse structural unit, that is, in the direction of rotation, the positions of the oil inlet window 102 and the oil outlet window 103 are reversed compared to the structural unit.

The reverse structure unit makes the plunger 105 on the newly added cylinder hole window 101 work out of adjustment, generates a force that prevents the motor from rotating, and affects the normal operation of the motor. In order to make the reverse structure unit meet the work requirements, you can change the phase displacement amplitude of the guide rail. Angle β _x (shown in Figure 3) and the cylinder bore phase displacement argument β _z (shown in Figure 4), or change both arguments at the same time to meet work needs.

As shown in Figures 7 and 8, it is the second embodiment of the present invention: an application of a hydraulic motor with a fixed cylinder block on a ten-acting six-piston hydraulic motor.

After adding the reverse structure unit, in order to realize the work requirement, this embodiment 2 is realized by changing the phase displacement angle β _{x of the} guide rail.

The structure parameters are:

x=10, r=10, z=6, α _z =12°, α _r =24°, α _az =α _bz =6°, α _a =α _b =36°, φ _ab =2π/z=60 °, φ _z = 2π/z = 60°.

The rail phase displacement angle β _x =0 of the rail A 200a.

The rail phase displacement angle of the rail B 200b is β _x =π/x=18°.

The cylinder hole 104 communicates with the odd-numbered cylinder hole window 101 (Z1, Z3, Z5), and the plunger 105 (Q1, Q3, Q5) inside acts on the guide rail A 200a; and the even-numbered cylinder hole window 101 (Z2, Z4, Z6) the communicating cylinder hole 104, the plunger 105 (Q2, Q4, Q6) inside acts on the guide rail B 200b.

At this time, the oil inlet window 102, the oil outlet window 103 and the cylinder bore window 101 on the static valve surface are clockwise in accordance with the oil inlet window 102-cylinder bore window 101-oil outlet window 103-cylinder bore window 101-oil inlet window 102 -Cylinder hole window 101-Oil outlet window 103-Cylinder hole window 101-Oil inlet window 102-Cylinder hole window 101-Oil outlet window 103-Cylinder hole window 101 are arranged cyclically.

The odd-numbered cylinder bore window 101 is a structural unit that meets the working requirements, and the even-numbered cylinder bore window 101 is a reverse structural unit.

Reverse structural unit, the cylinder bore window 101 window 103 in the counterclockwise direction is oil, the oil inlet is clockwise window 102, when acting on the guide rail β _x = A 200a 0, will produce a rotating force of the motor impede the The motor can’t work normally, because the active sections of guide rail B 200b and guide rail A 200a are exactly opposite, so the phase of the plunger 105 on the reverse structure unit is corrected after it acts on the guide rail B 200b, making it communicate with the reverse structure unit. The plunger 105 acts on the correct rail section to make the motor work normally.

As shown in Figure 8, the plunger 105Q1 is located at the outer dead point of the guide rail A 200a, and the cylinder bore window 101 Z1 is not connected with the oil inlet window 102 and the oil outlet window 103; Q2 is located at the oil inlet section 202 of the guide rail B 200b, Z2 is connected to the oil inlet window 102 through the flow distribution window 301, which generates a force that causes the guide rail to rotate in a clockwise direction; Q3 is located in the oil inlet section 202 of the guide rail A 200a, and Z3 is connected to the oil inlet window 102 through the flow distribution window 301, generating a force that makes the guide rail smooth. Force of rotation in the clockwise direction; Q4 is located at the inner dead point of guide rail B 200b, cylinder hole window 101 Z4 is not connected with oil inlet window 102 and oil outlet window 103; Q5 is located at oil outlet section 201 of guide rail A 200a, Z5 passes The distribution window 301 is connected to the oil outlet window 103 to discharge the oil; Q6 is located in the oil discharge section 201 of the guide rail B 200b, and the Z6 is connected to the oil outlet window 103 through the distribution window 301 to discharge the oil.

It can be concluded from the above that this embodiment 2 meets the working requirements.

As shown in Figures 9 and 10, it is the third embodiment of the present invention: an application of a hydraulic motor with a fixed cylinder block on a ten-acting nine-plunger hydraulic motor.

Embodiment 2 can increase the utilization rate of the cylinder 100, but because the plunger 105 is divided into at least two working rows, the thickness of the hydraulic motor is increased.

In order to increase the number of plungers 105 without increasing the thickness of the motor, it is also possible to change the phase displacement angle β _z of the cylinder bore of the reverse structure unit to make the plungers 105 on the correct guide rail section.

In Embodiment 2, the angle between the outer dead point and the inner dead point is n·π/x (n is an odd number), and the guide rail 200 has a period of 2π/x, so there is only one angle π/x, if the reverse structure If the unit's active guide rail remains unchanged, the phase displacement angle of the cylinder bore can be changed

β _z =n·π/x (n is an odd number) to make the plunger 105 in the cylinder bore 104 of the inverted structural unit act on the correct rail section.

In the third embodiment, by changing the phase displacement angle of the cylinder bore β _z =π/x=18°, the problem of the action section of the reverse structure unit is realized.

The structure parameters are:

x=10, r=10, z=9, α _z =12°, α _r =24°, α _az =α _bz =6°, α _ac =α _ad =12°, α _b =36°, φ _z = 60°.

The oil inlet window 102 is divided into two independent oil inlet windows C 102c and oil inlet windows D 102d in a clockwise direction. The oil inlet window C 102c is connected to the oil inlet channel C 106c, and the oil inlet window D 102d and the oil inlet channel D 106d is connected.

At this time, the oil inlet window 102, the oil outlet window 103 and the cylinder bore window 101 on the static valve surface are clockwise according to the oil inlet window C 102c-oil inlet window D 102d—cylinder bore window 101—oil outlet window 103—cylinder bore Window 101-Oil Inlet Window C 102c-Oil Inlet Window D 102d-Cylinder Hole Window 101-Oil Out Window 103-Cylinder Hole Window 101-Oil Inlet Window C 102c-Oil Inlet Window D 102d-Cylinder Hole Window 101-Oil Out Window 103-The order of the cylinder hole window 101 is arranged in a circular manner.

The odd-numbered cylinder bore windows 101 (Z1, Z3, Z5) are each connected to a plunger 105; the even-numbered cylinder bore windows 101 (Z2, Z4, Z6) are each connected to two plungers 105, this _{The phase displacement angle β z} =π/x=18° between the two cylinder holes 104 and the center of the cylinder hole window 101; where the oil inlet window C 102c is adjacent to the even-numbered cylinder bore window 101, and the oil inlet window D 102d is adjacent to the odd-numbered cylinder bore window 101.

In Embodiment 2, each oil inlet window 102 can supply liquid to two adjacent cylinder bore windows 101 in a clockwise direction and a counterclockwise direction.

In Embodiment 3, the oil inlet window C 102c supplies liquid to the even-numbered cylinder bore window 101, and the oil inlet window D 102d supplies liquid to the odd-numbered cylinder bore window 101.

As shown in Figure 10, the plunger 105Q1 is located at the outer dead point of the guide rail 200, and the cylinder bore window 101 Z1 is not connected to the oil inlet window 102 and the oil outlet window 103; Q2 and Q3 are located in the oil inlet section 202 of the guide rail 200, Z2 is connected to the oil inlet window C 102c through the flow distribution window 301, which generates a force to rotate the guide rail 200 in a clockwise direction; Q4 is located in the oil inlet section 202 of the guide rail 200, and Z3 is connected to the oil inlet window D 102d through the flow distribution window 301, generating a force The force that the guide rail 200 rotates clockwise; Q5 and Q6 are located at the inner dead point of the guide rail 200, and the cylinder hole window 101 Z4 is not connected to 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 , Z5 is connected to the oil outlet window 103 through the flow distribution window 301 to discharge oil; Q8 and Q9 are located in the oil outlet section 201 of the guide rail 200, and Z6 is connected to the oil outlet window 103 through the flow distribution window 301 to discharge oil.

It can be concluded from the above that this embodiment 3 meets the working requirements.

Connect the oil inlet window C 102c with the oil pressure pipeline A1, and the oil inlet window D 102d communicate with the oil pressure pipeline A2. If the displacement of each plunger 105 is V:

If both A1 and A2 are supplied with pressure oil, the displacement of the motor is 9V (Q1 ~ Q9).

If A1 is connected to pressure oil and A2 is not connected to pressure oil, the displacement of the motor is 6V (Q2, Q3, Q5, Q6, Q8, Q9).

If A2 is connected to pressurized oil and A1 is not connected to pressurized oil, the displacement of the motor is 3V (Q1, Q4, Q7).

Therefore, by disconnecting a part of the independent oil inlet window 102 to communicate with the pressure oil, the displacement of the motor can be changed.

As shown in Figures 11 and 12, it is the fourth embodiment of the present invention: an application of a hydraulic motor with a fixed cylinder block in a ten-acting nine-piston end-distribution hydraulic motor.

Embodiment 3 can realize the displacement change when the motor rotates in the clockwise direction. When rotating in the counterclockwise direction, the original oil inlet window 102 becomes the oil outlet window 103, and the original oil outlet window 103 becomes the oil inlet window 102, as can be seen from Figure 9 , When rotating counterclockwise, the oil inlet window 102 becomes three, so although the displacement can be changed, the displacement cannot be changed like the forward rotation.

In order to change the displacement of the motor in forward and reverse rotations, both the oil inlet window 102 and the oil outlet window 103 are designed as two independent windows.

The structure parameters are:

x=10, r=10, z=9, α _z =12°, α _r =24°, α _az =α _bz =6°, α _ac =α _ad =12°, α _bc ＝α _bd =12° , Φ _z = 60°.

The oil inlet window 102 is divided clockwise into two independent oil inlet windows C 102c and oil inlet windows D 102d. The oil inlet window C 102c is connected to the oil inlet channel C 106c, and the oil inlet window D 102d and the oil inlet channel D 106d is connected. The oil outlet window 103 is divided into two independent oil outlet windows C 103c and oil outlet D 103d in a clockwise direction. The oil outlet window C 103c is connected to the oil outlet channel C 107c, and the oil outlet window D 103d and the oil outlet channel D are connected. 107d is connected.

At this time, the oil inlet window 102, the oil outlet window 103 and the cylinder bore window 101 on the static valve surface are clockwise in accordance with the oil inlet window C 102c-oil inlet window D 102d-cylinder bore window 101-oil outlet window C 103c-out Oil Window D 103d-Cylinder Hole Window 101-Oil Inlet Window C 102c-Oil Inlet Window D 102d-Cylinder Hole Window 101-Oil Outlet Window C 103c-Oil Outlet Window D 103d-Cylinder Hole Window 101-Oil Inlet Window C 102c- Oil inlet window D 102d-cylinder bore window 101-oil outlet window C 103c-oil outlet window D 103d-cylinder bore window 101 are arranged in a circular sequence.

The structure of Embodiment 4 is similar to that of Embodiment 3, and the curved section that acts during the reverse rotation and the forward rotation has also changed due to the change of the oil inlet and outlet window 103.

As for any hydraulic motor shown in Figure 5 to Figure 12, when any one of the oil inlet window 102 and the oil inlet channel 106 is disconnected, the cylinder bore window 101 acting on it will not flow in, which will reduce the displacement of the motor. As shown in Fig. 5, when the oil inlet window 102 in the counterclockwise direction of Z1 is disconnected from the oil inlet channel 106, Z1 no longer participates in the work, and the motor displacement is reduced.

The present invention is not limited to the above-mentioned specific embodiments. Those skilled in the art start from the above-mentioned structure without creative work and make various changes that fall within the protection scope of the present invention.

Claims

A cylinder fixed hydraulic motor, including:

A static flow distribution surface, the static flow distribution surface has a cylinder hole window, an oil inlet window and an oil outlet window,

A rotating distribution surface, the rotating distribution surface has a distribution window, and the distribution window is a groove recessed inward along the rotating distribution surface,

It is characterized in that the oil inlet window belt, the oil outlet window belt, the flow distribution window belt and the cylinder bore window belt overlap.
The hydraulic motor with a fixed cylinder block according to claim 1, wherein the number of distribution windows is equal to the number of guide rails.

At any position of the guide rail, when the plunger is in the oil outlet section, the cylinder bore window is connected to the oil outlet window through the flow distribution window, and when the plunger is in the oil inlet section, the cylinder bore window communicates with the oil inlet window through the flow distribution window.
The hydraulic motor with a fixed cylinder block according to claim 1, wherein any cylinder hole window has at least one oil inlet window in a counterclockwise direction, and at least one oil outlet window in a clockwise direction.
The hydraulic motor with a fixed cylinder block according to claim 1, wherein the number of cylinder hole windows on the static distribution surface is an even number, and any cylinder hole window with an odd number has at least one oil inlet window in the counterclockwise direction, There is at least one oil outlet window in the clockwise direction, any even-numbered cylinder bore window has at least one oil outlet window in the counterclockwise direction, and at least one oil inlet window in the clockwise direction.
The hydraulic motor with fixed cylinder block according to claim 4, characterized in that, any adjacent cylinder hole window center angle φ z = 2π/z, any adjacent oil inlet window center and oil outlet window center width The angle φ ab = 2π/z.
The hydraulic motor with a fixed cylinder block according to any one of claims 1 or 4, characterized in that at least one set of guide rails has a guide rail phase displacement angle β x =0, and at least one set of guide rails has a guide rail phase displacement angle β x =π/x.
The hydraulic motor with a fixed cylinder block according to any one of claims 1 or 4, wherein the cylinder hole connected to the odd-numbered cylinder hole window has a cylinder hole phase displacement angle β z =0,

The cylinder hole connected to the even-numbered cylinder hole window has the cylinder hole phase displacement angle β z =n·π/x, and n is an odd number.
The hydraulic motor with a fixed cylinder block according to claim 4, wherein at least one oil inlet window is divided into two independent oil inlet windows.
The hydraulic motor with a fixed cylinder block according to claim 8, wherein at least one independent oil inlet window can be disconnected from the oil inlet channel.
The hydraulic motor with a fixed cylinder block according to any one of claims 1 to 5, wherein the on-off of at least one oil inlet window and the oil inlet channel is controlled.