A unidirectional oil supply type arterial-like diverging channel

Abstract

The application discloses a one-way oil supply artery-like manifold, which comprises a main pipeline and a plurality of branch pipelines branched from the main pipeline, the branch pipelines comprise a first branch pipeline, a second branch pipeline, a third branch pipeline, an n-th branch pipeline, and the like, the preferred included angle between the branch pipelines and the axis of the main pipeline is not greater than 60 degrees, and a springless one-way valve is arranged at the end of the branch pipeline, and the opening direction of the springless one-way valve is from the main pipeline to a control valve arranged at the rear part of the springless one-way valve. The springless one-way valve applied in the manifold has the effects of small opening resistance and prevention of backflow, so that the high-speed pulsating flow in the manifold can quickly pass through the springless one-way valve and enter an oil-consuming actuator behind the control valve; the angle between the main pipeline and the branch pipeline is adjusted to be not greater than 90 degrees, so that the kinetic energy loss of the high-speed pulsating flow can be reduced, the springless one-way valve can be quickly and conveniently opened, the layout of the main pipeline and the branch pipeline can be ensured, the reasonable docking of the interface with the actuator can be facilitated, and the high-speed pulsating flow transmission can be prevented from being affected by a large included angle.

Description

Technical Field

[0001] This invention belongs to the field of oil supply pipeline technology for mechanical equipment, and specifically relates to an arterial manifold that can supply oil in one direction. Background Technology

[0002] In the hydraulic supply process of construction machinery, such as excavators, there are multiple actuators, such as cylinders and motors. Supplying hydraulics to each actuator individually would require numerous pipelines. Existing solutions use manifolds connected to check valves. While this allows for independent control of the load port, for a digital hydraulic intelligent control system and excavator (ZL 202022935836.4), the hydraulic supply line transmits discrete pulsating flow. Each working unit pressure requires the convergence of n discrete pulsations. Existing check valves, due to their high opening pressure, hinder the high-speed transmission of the pulsating flow. Furthermore, after the pulsating flow opens the check valve, it needs to accumulate momentum or operate under static pressure. The minimum opening pressure of existing check valves is no less than 0.2 MPa. Even if easily opened, each pulsating flow loses 0.2 MPa of energy. Therefore, each working unit pressure requires n 0.2 MPa of energy loss, severely impacting the hydraulic supply to each actuator. Therefore, there is a need for a unidirectional oil supply pipeline that can supply oil to multiple actuators and has low opening resistance and prevents backflow. Summary of the Invention

[0003] The present invention provides an arterial manifold that can supply oil in one direction, in order to solve at least one of the above-mentioned technical problems.

[0004] The technical solution adopted in this invention is as follows: a unidirectional oil supply-like arterial manifold, comprising a main pipeline and multiple branch pipelines branched from the main pipeline, wherein the branch pipelines include a first branch, a second branch, a third branch, ... and an nth branch, the included angle between the axis of the branch pipeline and the axis of the main pipeline is not greater than 90°, and a springless check valve is provided at the end of the branch pipeline, wherein the opening direction of the springless check valve is from the main pipeline to the control valve provided at the rear of the springless check valve.

[0005] In a preferred embodiment, the springless one-way valve includes a valve body and a valve core. The valve body has an oil inlet channel, a magnetic snap ring groove, a speed-increasing start-up chamber, a valve core sealing chamber, a flow-through snap ring groove, and an oil outlet channel sequentially formed in its axial direction. A first snap ring is provided in the magnetic snap ring groove, and a second snap ring is provided in the flow-through snap ring groove. The valve body also has a magnetic groove located outside the speed-increasing start-up chamber. The valve core is disposed in the valve core sealing chamber and can slide in the valve core sealing chamber along the axial direction of the valve body. The valve core includes a sealing body and a plurality of support feet evenly arranged on the side of the sealing body along the circumferential direction of the sealing body. An oil passage is formed between two adjacent support feet. The diameter of the sealing body is larger than the diameter of the speed-increasing start-up chamber.

[0006] In a preferred embodiment, the main pipeline is a pipeline with a gradually decreasing inner diameter, and its end coincides with the nth branch.

[0007] The spatial angle between any of the branch pipes and the axis of the main pipe is no greater than 90°, preferably no greater than 60°, and except for the nth branch pipe, the spatial angle between the other branch pipes and the axis of the main pipe is no less than 10°.

[0008] The branch pipes are arranged symmetrically about the axis of the main pipe, and / or sequentially along the contraction direction of the main pipe.

[0009] In a preferred embodiment, the end of the main pipeline coincides with the nth branch pipeline. Let the diameter of the branch pipeline be Dbranch, the diameter of the main pipeline at the front end of the branch pipeline be Dmain, and the diameter of the nth branch pipeline be Dn, then Dmain > Dbranch and Dmain ≥ Dn.

[0010] In a preferred embodiment, the control valve is connected to a control system. When the control valve is open, the oil between the springless check valve and the control valve flows to the working device. The valve core of the springless check valve moves towards the oil outlet channel under the impact of the pulsating fluid flow in the main pipeline, and tends to move towards the oil inlet channel to close due to the backflow impact of the overflow spring groove in the gap after the pulsating fluid flow impact. When the control valve is closed, the valve core of the springless check valve is closed by the rigid action of the oil column between the springless check valve and the control valve.

[0011] In a preferred embodiment, a first step is formed between the valve core sealing chamber and the speed-up opening chamber of the springless one-way valve. The valve core sealing chamber is provided with a conical sealing ring surface. The speed-up opening chamber can be shortened to the first step. Let the diameter of the speed-up opening chamber be d1, and the diameter of the through hole opened at the small end of the conical sealing ring surface be d1. The diameter of the through hole opened at the large end of the conical sealing ring surface is the same as the diameter of the oil outlet channel. The diameter of the flow-through snap ring groove is larger than the diameter of the oil outlet channel, and the diameter of the speed-up opening chamber is smaller than the diameter of the oil outlet channel.

[0012] In a preferred embodiment, the magnet slot of the springless check valve is an annular magnet slot or a plurality of cylindrical magnet slots arranged in a ring. When the magnet slot is an annular magnet slot, it is filled with an annular magnetic element; or when the magnet slot is a cylindrical magnet slot, it is filled with a cylindrical magnetic element. The magnetic orientation of the cylindrical magnetic element is consistent with the axial direction of the valve body, and the magnetic orientation of the cylindrical magnetic elements is consistent among themselves. The magnetic element utilizes the property that magnetic lines of force follow the shortest path to improve the accuracy of the valve core return.

[0013] In a preferred embodiment, when an annular magnet groove is provided in the valve body, the maximum diameter of the annular magnet groove is not greater than the diameter of the oil inlet channel, the minimum diameter of the annular magnet groove is not less than (d1+3mm), and the groove depth of the annular magnet groove is not greater than 2mm.

[0014] When a cylindrical magnet groove is provided in the valve body, the distance between the cylindrical magnet groove and the oil inlet channel in the radial direction of the valve body is not less than 0.1 mm, the distance between the cylindrical magnet groove and the speed-up chamber is not less than 3 mm, and the groove depth of the cylindrical magnet groove is not greater than 2 mm.

[0015] In a preferred embodiment, the sealing body is bowl-shaped or cone-shaped, and the number of supporting feet is an odd number and not less than 3.

[0016] In a preferred embodiment, the valve core of the springless one-way valve is formed by extrusion technology with tube end forming to ensure that the side wall of the valve core has a conical or spherical sealing surface that matches the inner wall of the valve core sealing chamber. When the sealing surface that matches the valve body and the valve core is conical, the included angle of the conical sealing surface is set to 2θ, and 2θ is not greater than 74°, so as to ensure that the speed-up opening chamber of the valve body with the annular magnet groove has sufficient strength.

[0017] In a preferred embodiment, the valve core of the springless check valve has a blocking state and an overflow state;

[0018] When the valve core is in a blocked state, the blocking body of the valve core fits against the conical sealing ring surface of the valve core blocking chamber to form a ring-shaped rigid static seal. In the radial direction of the valve body, let H be the shortest distance between the conical sealing ring surface and the axis of the valve body, H1 be the shortest distance between the annular magnet groove and the axis of the valve body, and H2 be the shortest distance between the cylindrical magnet groove and the axis of the valve body. Then H > H1 and H > H2.

[0019] When the valve core is in the flow-through state, the maximum distance between the valve core and the conical sealing ring surface, which is equal to the maximum distance that the end face of the support foot of the valve core can be away from the contact surface of the second snap ring, is denoted as L. When the valve core is in the blocking state, the diameter of the contact circle between the valve core and the conical sealing ring surface is d2. Then, 4(Ltgθ)^2+4d2*tgθ≥d1^2, to ensure sufficient flow-through area and thus reduce flow resistance.

[0020] Due to the adoption of the above technical solution, the beneficial effects achieved by this invention are as follows:

[0021] 1. In a preferred embodiment of the present invention, when liquid flows in a pipeline, especially when a high-speed pulsating flow passes through the intersection of the main pipeline and the branch pipeline, the pulsating flow impacts the pipe wall. During this process, the impact of the pulsating flow on the pipe wall is similar to the reflection of light, changing the direction of the pulsating flow. At the same time, due to the obstruction of the pipe wall, its kinetic energy is reduced. In this process, the larger the angle between the main pipeline and the branch pipeline, the greater the obstruction of the pulsating flow by the pipe wall, and the more significant the reduction in its kinetic energy. The present invention limits the angle between the main pipeline and the branch pipeline of the manifold to within 90°. On the one hand, this can reduce the kinetic energy loss of the pulsating flow, and in the oil supply direction, it can achieve on-demand and orderly oil supply to multiple actuators, such as cylinders, motors, and pipelines. On the other hand, it can also facilitate faster opening of the springless check valve, and can also ensure the layout of the main pipeline and the branch pipeline, facilitating reasonable docking with the actuator interface, and avoiding excessive angles affecting the transmission of high-speed pulsating flow.

[0022] 2. As a preferred embodiment of the present invention, a novel springless check valve is used in the manifold, which makes the valve core very lightweight and eliminates the need for spring closure support, thus enabling fast start-up. Furthermore, the impact of the flow through the snap ring groove and the converging action ensures that the valve core moves towards the conical surface guided by the magnet, resulting in a fast sealing response. This gives the manifold low opening resistance and timely prevention of backflow.

[0023] 3. As a preferred embodiment of the present invention, the novel springless one-way valve used in the manifold has the following advantages: the valve core is attracted by the magnet, and the attraction is strongest at the point where the magnetic circuit density is greatest. Since the magnetic circuit prefers to take the shortest path, it can effectively ensure that the sealing contact surface between the valve core and the conical sealing ring is automatically adjusted to the position and state of the shortest magnetic circuit path in the previous operation. This is beneficial for the seamless sealing surface to be evenly connected each time, thus extending the sealing life. This avoids leakage caused by factors such as increased gaps and increased clearances in the rigid sealing surface due to misalignment of the one-way valve core with the valve body each time, thereby extending the service life of the manifold. Attached Figure Description

[0024] The accompanying drawings, which are included to provide a further understanding of the invention and form part of this invention, illustrate exemplary embodiments of the invention and are used to explain the invention, but do not constitute an undue limitation of the invention. In the drawings:

[0025] Figure 1 This is a schematic diagram illustrating the connection of the main pipeline, branch pipelines, springless check valve, and control valve of the arterial manifold in this invention.

[0026] Figure 2 This is a schematic diagram of a structure for changing the diameter of the main arterial manifold in this invention;

[0027] Figure 3 This is a schematic diagram of another structure for the diameter reduction of the main artery manifold in this invention;

[0028] Figure 4 This is a schematic diagram illustrating one embodiment of the main and branch tubing of the arterial manifold in this invention.

[0029] Figure 5 This is a schematic diagram illustrating another embodiment of the arterial manifold in this invention.

[0030] Figure 6 This is a schematic diagram illustrating one embodiment of a springless check valve according to the present invention.

[0031] Figure 7 This is a schematic structural diagram of one embodiment of a springless one-way valve according to the present invention;

[0032] Figure 8 This is a schematic diagram of a possible embodiment of the present invention where the valve core has an even number of support legs;

[0033] Figure 9 This is a schematic diagram of a possible embodiment of the present invention where the valve core has an odd number of support legs;

[0034] Figure 10This is a schematic diagram illustrating the layout of an annular magnet groove of a springless one-way valve according to the present invention.

[0035] Figure 11 This is a schematic diagram illustrating the layout of a cylindrical magnet slot in a springless one-way valve according to the present invention.

[0036] Figure label:

[0037] 100. Main Road;

[0038] 200. Branch pipes;

[0039] 300. Springless check valve;

[0040] 400. Control valve;

[0041] 1. Valve body; 11. Oil inlet channel; 12. Magnet circlip groove; 13. Speed-up opening chamber; 14. Valve core sealing chamber; 141. Conical sealing ring surface; 15. Flow circlip groove; 16. Oil outlet channel; 17. Annular magnet groove; 18. Cylindrical magnet groove;

[0042] 2. Valve core; 21. Sealing body; 22. Support foot; 23. Oil passage; 3. First snap ring; 4. Second snap ring; 5. Annular magnetic component; 6. Cylindrical magnetic component; 7. First step; 8. Second step. Detailed Implementation

[0043] To more clearly illustrate the overall concept of the present invention, a detailed description will be provided below with reference to the accompanying drawings and examples.

[0044] Many specific details are set forth in the following description in order to provide a full understanding of the invention. However, the invention may also be practiced in other ways different from those described herein, and therefore the scope of protection of the invention is not limited to the specific embodiments disclosed below.

[0045] Furthermore, in the description of this invention, it should be understood that the terms "top," "bottom," "inner," "outer," "axial," "radial," "circumferential," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0046] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a communication connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0047] In this invention, unless otherwise expressly specified and limited, the first feature "on" or "below" the second feature may be in direct contact with the first and second features, or indirect contact through an intermediate medium. In the description of this specification, references to terms such as "implementation," "example," "aspect," "specific example," or "specific example" indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0048] like Figure 1 , Figure 2 , Figure 3 , Figure 4 , Figure 5 As shown, a unidirectional oil supply-type arterial manifold includes a main pipe 100 and multiple branch pipes 200 branching from the main pipe 100. Each branch pipe 200 includes a first branch, a second branch, a third branch, ..., and an nth branch. When the fluid flows within the pipes, especially high-speed pulsating flow, when passing through the intersection of the main pipe 100 and the branch pipes 200, the pulsating flow impacts the pipe wall. During this process, the impact on the pipe wall is similar to the reflection of light, changing the direction of the pulsating flow. Simultaneously, due to the obstruction from the pipe wall, its kinetic energy decreases. In this process, the larger the angle between the main pipe 100 and the branch pipes 200, the greater the obstruction of the pulsating flow by the pipe wall, and the more significant the reduction in its kinetic energy. The present invention limits the angle between the main pipe 100 and the branch pipe 200 of the manifold to within 90°. On the one hand, this can reduce the kinetic energy loss of the pulsating flow, and on the other hand, it can prevent leakage and damage caused by the long-term impact of the high-speed pulsating flow on the pipe wall at the connection between the main pipe 100 and the branch pipe 200.

[0049] In one embodiment, such as Figure 1 A springless check valve 300 is installed at the end of the branch pipe 200 shown. The opening direction of the springless check valve 300 is from the main pipe 100 to the control valve 400 installed at the rear of the springless check valve 300.

[0050] Specifically, such as Figure 6 , Figure 7 As shown, the springless check valve 300 includes a valve body 1 and a valve core 2. The valve body 1 has an oil inlet channel 11, a magnetic snap ring groove 12, a speed-increasing start-up chamber 13, a valve core sealing chamber 14, a flow-through snap ring groove 15, and an oil outlet channel 16 sequentially formed in its axial direction. A first snap ring 3 is provided in the magnetic snap ring groove 12, and a second snap ring 4 is provided in the flow-through snap ring groove 15. A magnetic groove located outside the speed-increasing start-up chamber 13 is also formed in the valve body 1. The valve core 2 is disposed in the valve core sealing chamber 14 and can move along the valve body within the valve core sealing chamber 14. The valve core 2 slides in the axial direction of valve body 1. The valve core 2 includes a sealing body 21 and multiple support feet 22 evenly arranged on the side of the sealing body 21 in the circumferential direction. An oil passage 23 is formed between two adjacent support feet 22. The diameter of the sealing body 21 is larger than the diameter of the speed-increasing opening chamber 13. The new valve core 2 structure used in the valve body 1 can not only reduce the resistance of opening the valve body 1, but also effectively enhance the stability of the valve core 2 by using a conical surface and a second snap ring 4 to limit the valve core 2.

[0051] Furthermore, a first retaining ring 3 and a second retaining ring 4 are respectively provided on both sides of the valve core 2 to limit and protect the valve core 2, preventing the valve core 2 from being damaged or accidentally flowing out of the valve core sealing chamber 14 when it moves within the valve core sealing chamber 14.

[0052] In a preferred embodiment, the main pipeline 100 preferably adopts a pipeline with a gradually decreasing inner diameter, such as... Figure 2 , Figure 3 As shown, there are two different ways to reduce the inner diameter. Specifically, one is that a certain section of the main pipeline 100 has the same diameter, and then transitions to another section of the main pipeline 100 with the same diameter by changing the diameter. The other is that the inner diameter of the main pipeline 100 gradually decreases from one end to the other.

[0053] The end can coincide with the nth branch; as oil is supplied from the main pipeline 100 to each actuator, the liquid flow rate in the main pipeline 100 decreases. In order to prevent cavitation caused by the liquid flow, especially the pulsating flow, during the flow process, the inner diameter of the main pipeline 100 gradually decreases along its liquid flow direction. On the other hand, the gradually decreasing pipeline is conducive to reducing the liquid volume of the downstream liquid, increasing the acceptance of the pulsating liquid flow of the upstream first branch, second branch, etc., and reducing the counter-current loss caused by liquid volume lag.

[0054] Furthermore, the spatial angle between any branch pipe 200 and the axis of the main pipe 100 is no greater than 90°. To reduce kinetic energy loss, it is preferable that the spatial angle between any branch pipe 200 and the axis of the main pipe 100 is no greater than 60°, and except for the nth branch pipe, the spatial angle between the axis of the other branch pipe 200 and the axis of the main pipe 100 is no less than 10°.

[0055] Furthermore, when there are many branch pipes of 200, such as Figure 5 As shown, multiple branch pipes 200 can be arranged symmetrically about the axis of the main pipe 100, or they can be arranged as follows: Figure 4 The branch pipes shown are arranged sequentially in the contraction direction of the main pipe 100. Alternatively, they can be arranged as follows: Figure 2 , Figure 3 The hybrid arrangement shown combines these two methods. On the one hand, this branch pipe 200 layout can avoid pipe chaos and optimize the pipe layout. On the other hand, it makes the mechanical structure of the pipe more stable and extends the service life of the branch pipe.

[0056] Furthermore, the end of the main pipeline 100 coincides with the nth branch. Let the diameter of the branch pipeline 200 be D_branch, the diameter of the main pipeline 100 at the front end of the branch pipeline 200 be D_main, and the diameter of the nth branch be D_n_branch. Then, D_main > D_branch, and D_main ≥ D_n_branch.

[0057] In a preferred embodiment, the control valve 400 is connected to a control system. When the control valve 400 is open, the oil between the springless check valve 300 and the control valve 400 flows to the working device. The valve core 2 of the springless check valve 300 moves towards the oil outlet channel 16 under the impact of the pulsating fluid flow in the main pipeline 100, and tends to move towards the oil inlet channel 11 to close due to the backflow impact of the flow spring groove 15 in the gap after the pulsating fluid flow impact. When the control valve 400 is closed, the valve core 2 of the springless check valve 300 is closed by the rigid action of the oil column between the springless check valve 300 and the control valve 400.

[0058] In one embodiment, such as Figure 6 , Figure 7 , Figure 8 , Figure 9 , Figure 10 , Figure 11As shown, a first step 7 is formed between the valve core sealing chamber 14 and the speed-increasing opening chamber 13 of the springless check valve 300. A conical sealing ring surface 141 is provided inside the valve core sealing chamber 14. The speed-increasing opening chamber 13 can be shortened to the first step 7. Let the diameter of the speed-increasing opening chamber 13 be d1, and the diameter of the through hole at the small end of the conical sealing ring surface 141 be d1, to achieve a smooth transition between the speed-increasing opening chamber 13 and the conical sealing ring surface 141. The diameter of the through hole at the large end of the conical sealing ring surface 141 is the same as the diameter of the oil outlet channel 16, achieving a smooth transition between the conical sealing ring surface 141 and the oil outlet channel 16, which facilitates the flow of oil within the valve body 1. To reduce the obstruction of the conical sealing ring surface 141 to the oil fluid, the diameter of the flow-through circlip groove 15 is larger than the diameter of the oil outlet channel 16, so that after the second circlip 4 is installed into the flow-through circlip groove 15, the second circlip 4 can be snapped into the flow-through circlip groove 15, preventing the second circlip 4 from sliding out of the valve body 1 along the inner wall of the valve body 1. The diameter of the speed-increasing opening chamber 13 is smaller than the diameter of the oil outlet channel 16, so that the flow velocity of the fluid at the speed-increasing opening chamber 13 is increased. The speed-increasing opening chamber 13 is adjacent to the valve core sealing chamber 14, so that the valve core 2 can seal the valve core sealing chamber 14, preventing the fluid from flowing into the speed-increasing opening chamber 13 through the valve core sealing chamber 14.

[0059] In one embodiment, such as Figure 6 In the indicated state, when the oil inlet pipe supplies oil to the oil inlet channel 11, the oil exerts an upward pushing force on the valve core 2, causing the valve core 2 to move upward in the vertical direction along the valve core sealing chamber 14. At this time, the sealing body 21 below the valve core 2 separates from the conical sealing ring surface 141 of the valve core sealing chamber 14, and the oil flows sequentially through the oil inlet channel 11, the speed-increasing flushing chamber 13, the gap between the sealing body 21 and the conical sealing ring surface 141, the oil passage 23, and the oil outlet channel 16. When the oil outlet pipe returns oil to the oil outlet channel 16, the oil exerts a downward pushing force on the valve core 2, causing the valve core 2 to move downward in the vertical direction along the valve core sealing chamber 14 until the sealing body 21 of the valve core 2 is squeezed against the conical sealing ring surface 141 of the valve core sealing chamber 14 to achieve sealing of the valve core sealing chamber 14. After the oil flows back from the oil outlet channel 16 to the valve core sealing chamber 14, it cannot continue to flow back through the valve core sealing chamber 14, thus achieving control over the oil backflow. Through the impact of the oil on the valve core 2, the valve core 2 is moved, thereby enabling the valve core 2 to have both a sealing state and a flow-through state.

[0060] In one embodiment, the valve body 1 of the springless check valve 300 does not have a spring compared to the existing valve body 1. When the valve core 2 switches from the blocking state to the flow state, since there is no spring installed at the valve core 2 for rebound, an annular magnetic element 5 or a cylindrical magnetic element 6 is provided to guide the valve core 2 back to its original position, preventing premature damage to the seal between the valve core 2 and the conical surface. This eliminates the adverse effects of premature damage to the sealing surface caused by misalignment between the valve core 2 and the conical surface due to the use of a springless design compared to the prior art, and can also improve the response characteristics of the valve core 2.

[0061] In a preferred embodiment, the magnet slot of the springless check valve 300 is an annular magnet slot 17 or a plurality of cylindrical magnet slots 18 arranged in a ring. When the magnet slot is an annular magnet slot 17, an annular magnetic element 5 is filled inside the annular magnet slot 17; or when the magnet slot is a cylindrical magnet slot 18, a cylindrical magnetic element 6 is filled inside the cylindrical magnet slot 18. The magnetic placement direction of the cylindrical magnetic element 6 is consistent with the axial direction of the valve body 1, and the magnetic placement directions of the cylindrical magnetic elements 6 are consistent. The magnetic elements utilize the property that magnetic lines of force follow the shortest path to improve the accuracy of the valve core 2's return position.

[0062] In a preferred embodiment, when an annular magnet groove 17 is provided in the valve body 1, the maximum diameter of the annular magnet groove 17 is not greater than the diameter of the oil inlet channel 11, the minimum diameter of the annular magnet groove 17 is not less than (d1+3mm), and the groove depth of the annular magnet groove 17 is not greater than 2mm.

[0063] When a cylindrical magnet groove 18 is provided inside the valve body 1, the distance between the cylindrical magnet groove 18 and the oil inlet channel 11 in the radial direction of the valve body 1 is not less than 0.1 mm, the distance between the cylindrical magnet groove 18 and the speed-up chamber 13 is not less than 3 mm, and the groove depth of the cylindrical magnet groove 18 is not greater than 2 mm.

[0064] Preferably, when an annular magnet groove 17 is provided in the valve body 1, it is necessary to ensure that the maximum diameter of the annular magnet groove 17 is not greater than the diameter of the oil inlet channel 11, and the minimum diameter of the annular magnet groove 17 is not less than (d1+3mm), so that the annular magnet groove 17 on both sides in the valve body 1 has sufficient strength to prevent fluid impact damage.

[0065] In a preferred embodiment, the sealing body 21 is bowl-shaped or cone-shaped, and the number of support feet 22 is odd and not less than 3. An odd number of support feet 22 can reduce the closure of the magnet's attraction to the valve core 2.

[0066] In one embodiment, the structural diagram of the valve core 2 is as follows: Figure 8 , Figure 9As shown, the number of support feet 22 of the valve core 2 can be set differently according to the actual application scenario. The number of support feet 22 is preferably odd to facilitate the flow of oil in the flow channel. When the number of support feet 22 is odd, it can reduce the symmetry of the magnetic lines of force, reduce the interference magnetic attraction of the first retaining ring 3 and the second retaining ring 4 on the valve core 2, and facilitate the valve core 2 to fit at the conical sealing ring surface 141, preventing the valve core 2 from flipping.

[0067] Preferably, the oil inlet channel 11, the magnet snap ring groove 12, the speed-increasing opening chamber 13, the valve core sealing chamber 14, the flow-through snap ring groove 15, and the oil outlet channel 16 are coaxially arranged to facilitate the flow of oil within the valve body 1 and reduce flow resistance. The first snap ring 3 is made of magnetic material, ensuring that its magnetic direction is opposite to the magnetic direction of the annular magnetic element 5 in the annular magnet groove 17, i.e., NN or SS, to form mutual repulsion.

[0068] Preferably, a second step 8 is formed between the valve core sealing chamber 14 and the flow-through circlip groove 15. The second step 8 cooperates with the oil passage 23 of the support foot 22. Let the groove width of the flow-through circlip groove 15 be L1, the length of the support foot 22 be L2, and the thickness of the second circlip 4 be L3, then L1 > L2 + L3. Let the diameter of the flow-through circlip groove 15 be D, and the outer diameter of the second circlip 4 be d, then D > d, so as to ensure that the second circlip 4 can fit against the end face of the flow-through circlip groove 15 away from the valve core sealing chamber 14. The second circlip 4 is made of magnetic material to ensure that the magnetic direction is opposite to the magnetic direction of the annular magnetic element 5 in the annular magnet groove 17, that is, NN or SS correspond to form mutual repulsion.

[0069] Preferably, the outer sides of the oil inlet channel 11 and the oil outlet channel 16 are provided with 24° cone sealing interfaces and corner seals or end face seals at the root of the thread of the valve body 1.

[0070] When the aforementioned springless one-way valve 300 is used, the attraction force is strongest at the point of maximum magnetic circuit density under the attraction of the valve core 2. Since the magnetic circuit prefers the shortest path, it effectively ensures that the sealing contact surface between the valve core 2 and the conical sealing ring surface 141 is automatically adjusted to the position and state of the shortest magnetic circuit path from the previous operation. This avoids leakage from the rigid sealing surface caused by misalignment of the one-way valve core 2 with the valve body 1 each time they engage, thus extending the sealing life. The valve core 2 is very lightweight and does not require spring closure support. Therefore, the impact of the flow and confluence effect of the snap ring groove ensures that the valve core 2 closes and moves towards the conical surface guided by the magnet. Because valve core 2 is very lightweight, it can not only close and seal quickly, but also start very quickly. When a pulsating flow impacts the concave surface of valve core 2, and the subsequent pulsating flow simultaneously impacts the convex surface, due to the absence of a spring, the two pulsating flows directly compare and interact before and after valve core 2. The impact of the subsequent pulsating flow can provide follow-up power to the previous pulsating flow within the concave surface, enabling it to pulsate forward quickly. It can also utilize the reaction force of the previous pulsating flow and the guiding effect of the convex surface to quickly impact the second retaining spring 4 through valve core 2, transforming it into a preceding pulsating flow. At this time, valve core 2 is as if suspended between the pulsating flows, vibrating back and forth at a frequency not exceeding the transmission frequency of the pulsating flows. When the last pulsating flow arrives, the suspended valve core 2 can quickly close, meeting the needs of discrete hydraulic technology development. Simultaneously, this springless check valve 300 is also a check valve with low opening power and long sealing life.

[0071] In a preferred embodiment, the valve core 2 of the springless check valve 300 is formed by extrusion technology with tube end forming to ensure that the side wall of the valve core 2 has a conical or spherical sealing surface that matches the inner wall of the valve core sealing chamber 14. When the sealing surface that matches the valve body 1 and the valve core 2 is conical, the included angle of the conical sealing surface is set to 2θ, and 2θ is not greater than 74°, so as to ensure that the speed-increasing opening chamber 13 of the valve body 1 with the annular magnet groove 17 has sufficient strength.

[0072] In a preferred embodiment, the valve core 2 of the springless check valve 300 has a blocking state and an overflow state;

[0073] When the valve core 2 is in the blocking state, the blocking body 21 of the valve core 2 fits against the conical sealing ring surface 141 of the valve core blocking chamber 14 to form a ring-shaped rigid static seal. In the radial direction of the valve body 1, let the shortest distance between the conical sealing ring surface 141 and the axis of the valve body 1 be H, the shortest distance between the annular magnet groove 17 and the axis of the valve body 1 be H1, and the shortest distance between the cylindrical magnet groove 18 and the axis of the valve body 1 be H2. Then H > H1 and H > H2.

[0074] When the valve core 2 is in the flow-through state, the maximum distance between the valve core 2 and the conical sealing ring surface 141 is equal to the maximum distance that the end face of the support foot 22 of the valve core 2 can be away from the contact surface of the second snap ring 4, denoted as L. When the valve core 2 is in the blocking state, let the diameter of the contact circle between the valve core 2 and the conical sealing ring surface 141 be d2. Then 4(Ltgθ)^2+4d2*tgθ≥d1^2, so as to ensure sufficient flow-through area and thus reduce flow resistance.

[0075] For any parts not mentioned in this invention, existing technologies can be used or referenced.

[0076] The various embodiments in this specification are described in a progressive manner. The same or similar parts between the various embodiments can be referred to each other. Each embodiment focuses on describing the differences from other embodiments.

[0077] The above description is merely an embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principle of the present invention should be included within the scope of the claims of the present invention.

Claims

1. A type of arterial manifold with unidirectional oil supply, characterized in that, It includes a main pipeline and multiple branch pipelines branched from the main pipeline. The branch pipelines include a first branch, a second branch, a third branch, ... and an nth branch. A springless check valve is provided at the end of each branch pipeline. The opening direction of the springless check valve is from the main pipeline to a control valve provided at the rear of the springless check valve. The springless one-way valve includes a valve body and a valve core. The valve body has an oil inlet channel, a magnetic snap ring groove, a speed-increasing opening chamber, a valve core sealing chamber, a flow-through snap ring groove, and an oil outlet channel sequentially opened in its axial direction. A first snap ring is provided in the magnetic snap ring groove, and a second snap ring is provided in the flow-through snap ring groove. The valve body also has a magnetic groove located outside the speed-increasing opening chamber. The valve core is disposed in the valve core sealing chamber and can slide in the valve core sealing chamber along the axial direction of the valve body. The valve core includes a sealing body and a plurality of support feet evenly arranged on the side of the sealing body along the circumferential direction of the sealing body. An oil passage is formed between two adjacent support feet. The diameter of the sealing body is larger than the diameter of the speed-increasing opening chamber. The control valve is connected to a control system. When the control valve is open, the oil between the springless check valve and the control valve flows to the working device. The valve core of the springless check valve moves towards the oil outlet channel under the impact of the pulsating fluid flow in the main pipeline. In the gap after the pulsating fluid flow impact, it is impacted by the backflow of the flow retainer groove and has a tendency to move towards the oil inlet channel to close. When the control valve is closed, the valve core of the springless check valve is closed by the rigid action of the oil column between the springless check valve and the control valve. A first step is formed between the valve core sealing chamber and the speed-up opening chamber of the springless one-way valve. The valve core sealing chamber is provided with a conical sealing ring surface. The speed-up opening chamber can be shortened to the first step. Let the diameter of the speed-up opening chamber be d1, and the diameter of the through hole opened at the small end of the conical sealing ring surface be d1. The diameter of the through hole opened at the large end of the conical sealing ring surface is the same as the diameter of the oil outlet channel. The diameter of the flow-through snap ring groove is larger than the diameter of the oil outlet channel, and the diameter of the speed-up opening chamber is smaller than the diameter of the oil outlet channel. The magnet slot of the springless one-way valve is an annular magnet slot or multiple cylindrical magnet slots arranged in a ring. When the magnet slot is an annular magnet slot, the annular magnet slot is filled with an annular magnetic element; or when the magnet slot is a cylindrical magnet slot, the cylindrical magnet slot is filled with a cylindrical magnetic element, the magnetic placement direction of the cylindrical magnetic element is consistent with the axial direction of the valve body, and the magnetic placement direction of the cylindrical magnetic elements is consistent with each other. When the magnet groove is an annular magnet groove, both the first retaining ring and the second retaining ring are made of magnetic materials, and the magnetic directions of the first retaining ring and the second retaining ring are opposite to the magnetic directions of the annular magnetic element in the annular magnet groove, so as to form a mutually exclusive fit. When the sealing surface where the valve body and valve core mate is conical, the included angle of the conical sealing surface is set to 2θ, and 2θ is not greater than 74°. The valve core of the springless check valve has a blocking state and an overflow state; When the valve core is in a blocked state, the blocking body of the valve core fits against the conical sealing ring surface of the valve core blocking chamber to form a ring-shaped rigid static seal. In the radial direction of the valve body, let the shortest distance between the conical sealing ring surface and the axis of the valve body be H, and the shortest distance between the annular magnet groove and the axis of the valve body be H1, then H > H1. When the valve core is in the overflow state, the maximum distance between the valve core and the conical sealing ring surface, which is equal to the maximum distance that the end face of the valve core's support foot can be away from the contact surface of the second snap ring, is denoted as L. When the valve core is in the blocking state, let the diameter of the contact circle between the valve core and the conical sealing ring surface be d2, then 4(Ltgθ)^2+4d2 tgθ≥d1^2, to ensure sufficient flow area, thereby reducing flow resistance.

2. The arterial-like manifold with unidirectional oil supply according to claim 1, characterized in that, The main pipeline adopts a pipeline with a gradually decreasing inner diameter, and its end coincides with the nth branch. The spatial angle between any of the branch pipes and the axis of the main pipe is no greater than 90°, and except for the nth branch pipe, the spatial angle between the other branch pipes and the axis of the main pipe is no less than 10°; The branch pipes are arranged symmetrically about the axis of the main pipe, and / or sequentially along the contraction direction of the main pipe.

3. The arterial-like manifold with unidirectional oil supply according to claim 2, characterized in that, The end of the main pipeline coincides with the nth branch pipeline. Let the diameter of the branch pipeline be D_branch, the diameter of the main pipeline at the front end of the branch pipeline be D_main, and the diameter of the nth branch pipeline be D_n_branch. Then, D_main > D_branch and D_main ≥ D_n_branch.

4. The arterial-like manifold with unidirectional oil supply according to claim 1, characterized in that, When an annular magnet groove is provided in the valve body, the maximum diameter of the annular magnet groove is not greater than the diameter of the oil inlet channel, the minimum diameter of the annular magnet groove is not less than (d1+3mm), and the groove depth of the annular magnet groove is not greater than 2mm. When a cylindrical magnet groove is provided in the valve body, the distance between the cylindrical magnet groove and the oil inlet channel in the radial direction of the valve body is not less than 0.1 mm, the distance between the cylindrical magnet groove and the speed-up chamber is not less than 3 mm, and the groove depth of the cylindrical magnet groove is not greater than 2 mm.

5. The arterial-like manifold with unidirectional oil supply according to claim 1, characterized in that, The sealing body is bowl-shaped or cone-shaped, and the number of supporting feet is odd and not less than 3.

6. The arterial-like manifold with unidirectional oil supply according to claim 4, characterized in that, The valve core of the springless one-way valve is formed by extrusion technology with tube end forming to ensure that the side wall of the valve core has a conical or spherical sealing surface that matches the inner wall of the valve core sealing chamber.

Images