Double-channel linkage hydraulic distribution valve, brake linkage system and two-wheeled vehicle

Abstract

The utility model relates to a double-channel linkage hydraulic distribution valve, a brake linkage system and a two-wheeled vehicle, which comprises a shell, a first oil cavity, a second oil cavity and an oil cavity channel communicated with the first end of the first oil cavity and the first end of the second oil cavity, the side wall, close to the first end of the first oil cavity, of the first oil cavity is connected with a first connector and a second connector which are formed in the shell in the radial direction in a penetrating mode, and the side wall, close to the second end of the second oil cavity, of the second oil cavity is connected with a third connector and a fourth connector which are formed in the shell in the radial direction in a penetrating mode. The combined piston piece is movably arranged in the first oil cavity; the single piston piece is movably arranged in the second oil cavity; the combined piston piece and the single piston piece automatically distribute brake oil liquid output to the second connector and the fourth connector according to changes of brake oil pressure input by the first connector so as to balance brake.

Description

Technical Field

[0001] The utility model relates to the technical field of bicycle accessories, in particular to a dual-channel linkage hydraulic distribution valve, a brake linkage system and a two-wheeled vehicle. Background Art

[0002] Most existing bicycles adopt independent braking systems for the front and rear wheels. During braking, in order to obtain a reasonable deceleration, the rider needs to reasonably distribute the operating forces of both hands so that the front and rear tires make full use of the adhesion coefficient of the road surface. However, in actual riding, it is very difficult for the rider to do so. And because the rear wheel of a vehicle during normal riding or acceleration bears most of the weight of the vehicle, the obtained frictional force is greater than that of the front wheel. But during braking, due to inertia, the center of gravity of the vehicle will shift to the front wheel.

[0003] When emergency braking is required during high-speed riding, if the front wheel is braked alone, the center of gravity of the vehicle is unstable and there may be a risk of tail whipping. For this reason, we propose a dual-channel linkage hydraulic distribution valve, a brake linkage system and a two-wheeled vehicle. Summary of the Utility Model

[0004] This application provides a dual-channel linkage hydraulic distribution valve, a brake linkage system and a two-wheeled vehicle to at least solve the problem that when the front wheel is braked alone in the prior art, the center of gravity of the vehicle is unstable and there may be a risk of tail whipping.

[0005] In a first aspect, this application provides a dual-channel linkage hydraulic distribution valve, which is used in conjunction with a vehicle frame and includes:

[0006] A housing having a first oil chamber, a second oil chamber and an oil chamber passage communicating a first end of the first oil chamber with a first end of the second oil chamber formed in a middle portion thereof. A first interface and a second interface radially opened on the housing are through-connected to a side wall of the first oil chamber near its first end, and a third interface and a fourth interface radially opened on the housing are through-connected to a side wall of the second oil chamber near its second end;

[0007] A combined piston member movably disposed in the first oil chamber;

[0008] A single piston member movably disposed in the second oil chamber;

[0009] Wherein, the combined piston member and the single piston member automatically distribute the brake oil output to the second interface and the fourth interface according to the change of the brake oil pressure input at the first interface to balance braking.

[0010] Optionally, the combined piston member includes:

[0011] An annular step integrally formed at a position in the first oil chamber corresponding to the second interface, separating the inner end of the second interface into a first branch and a second branch. Both sides of the inner wall of the annular step are recessed inward to form a first slope surface and a second slope surface;

[0012] A first piston movably arranged on one side of the first oil chamber close to the first slope surface. A first table surface matching the first slope surface is formed at its first end, so as to leave the first slope surface and open the second branch when the oil pressure reaches the third preset oil pressure threshold;

[0013] A first elastic member arranged in the first oil chamber and located between the second end of the first piston and the second end of the first oil chamber, to elastically maintain the first table surface in contact with the first slope surface and close the second branch;

[0014] A second piston movably arranged on one side of the first oil chamber close to the second slope surface. An oil passage hole communicating with the first interface is provided in the middle of its axis, and a second table surface matching the second slope surface is formed at its second end, so as to contact the second slope surface and close the first branch when the oil pressure reaches the second preset oil pressure threshold;

[0015] A second elastic member arranged in the first oil chamber and located between the first end of the first piston and the second end of the second piston, to elastically maintain the second table surface away from the first slope surface and open the second branch.

[0016] Optionally, the first end of the first oil chamber is an open structure and is threadedly fitted with a first screw cap, and the inner end of the first screw cap abuts against the first end of the second piston.

[0017] Optionally, the first screw cap includes:

[0018] A screw cap body threadedly fitted with the first end of the first oil chamber;

[0019] A positioning boss integrally formed at the inner end of the screw cap body and abutting against the first end of the second piston. Its diameter is smaller than the inner diameter of the first oil chamber, and an annular oil groove communicating the first interface and the oil chamber passage is formed between it and the inner wall of the first oil chamber;

[0020] A communicating oil groove radially opened on one side of the positioning boss close to the second piston to communicate the annular oil groove and the oil passage hole.

[0021] Optionally, the single piston member includes:

[0022] A stepped portion is formed in the second oil chamber and divides the second oil chamber into a front chamber communicating with the oil chamber passage and a rear chamber communicating with the third interface and the fourth interface. The inner diameter of the front chamber is smaller than that of the rear chamber.

[0023] A third piston, the first section of which is movably assembled in the front chamber and the second section of which is movably assembled in the rear chamber. When the oil pressure reaches the first preset oil pressure threshold, the third piston displaces towards the rear chamber.

[0024] A third elastic member is arranged in the rear chamber and abuts against the free end of the second section of the third piston and the second end of the second oil chamber respectively to elastically maintain the third piston limited at the stepped portion.

[0025] A piston sleeve is fixedly sleeved on the annular side wall of the second section of the third piston.

[0026] Optionally, sealing rings are assembled on the movable contact surfaces between the combined piston member and the first oil chamber and between the single piston member and the second oil chamber.

[0027] Optionally, a plurality of assembly holes for fixed installation with the vehicle frame by screws are formed in the housing.

[0028] Optionally, the second ends of the first oil chamber and the second oil chamber are both of open structures and are threadedly assembled with second screw caps.

[0029] In a second aspect, the present application provides a brake linkage system, including the dual-channel linkage hydraulic distribution valve described in the first aspect above, and

[0030] A first upper pump, which is connected to the first interface through a first oil pipe;

[0031] A front-wheel lower pump, which is connected to the second interface through a second oil pipe;

[0032] A second upper pump, which is connected to the third interface through a third oil pipe;

[0033] A rear-wheel lower pump, which is connected to the fourth interface through a fourth oil pipe;

[0034] Wherein, when the first upper pump brakes, the dual-channel linkage hydraulic distribution valve automatically distributes the oil fluid input from the first interface to the front-wheel lower pump and the rear-wheel lower pump according to the oil pressure change to balance the braking; when the second upper pump brakes, the dual-channel linkage hydraulic distribution valve distributes the oil fluid input from the third interface to the rear-wheel lower pump to brake.

[0035] In a third aspect, the present application provides a brake linkage system, including the brake linkage system described in the second aspect above.

[0036] Compared with the related art, the dual-channel linkage hydraulic distribution valve, brake linkage system and two-wheeled vehicle provided by the present application have at least the following technical effects:

[0037] When braking, operating the first master cylinder alone, the front-wheel slave cylinder works initially, slightly braking the front wheel first to shift the center of gravity backward, and then controlling the front-wheel slave cylinder and the rear-wheel slave cylinder to work simultaneously to maintain braking balance. Finally, continuously increasing the braking force, at this time, the braking force is automatically distributed to the front-wheel slave cylinder and the rear-wheel slave cylinder according to the preset pressure threshold ratio, realizing the reasonable combined braking of the front and rear brakes of the bicycle by a single master cylinder. Compared with the braking force distribution of manual braking, it is more convenient, efficient and accurate, and the braking distance can be significantly shortened, reducing the risk of the bicycle skidding; at the same time, the synchronous linkage braking of the front and rear wheels is realized on the premise of not changing the overall braking structure of the bicycle and maximizing cost reduction.

[0038] Details of one or more embodiments of the present application are set forth in the following drawings and description to make other features, objects, and advantages of the present application more comprehensible. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] In order to more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the following will briefly introduce the drawings required for use in the description of the specific embodiments or the prior art. Obviously, the following drawings are some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0040] Figure 1 is a perspective view of a dual-channel linkage hydraulic distribution valve shown according to an exemplary embodiment.

[0041] Figure 2 is a front view of a dual-channel linkage hydraulic distribution valve shown according to an exemplary embodiment.

[0042] Figure 3 is a plan sectional view of a dual-channel linkage hydraulic distribution valve shown according to an exemplary embodiment.

[0043] Figure 4 is a perspective sectional view of a housing shown according to an exemplary embodiment.

[0044] Figure 5 is a perspective view of a combined structure of a combined piston member and a single piston member shown according to an exemplary embodiment.

[0045] Figure 6 is an exploded view of a combined structure of a combined piston member and a single piston member shown according to an exemplary embodiment.

[0046] Description of the reference numerals: Housing 10: First interface 101, Second interface 102, First branch 1021, Second branch 1022, Third interface 103, Fourth interface 104, First oil chamber 105, Second oil chamber 106, Oil chamber passage 107, Assembly hole 108;

[0047] First screw cap 20: Screw cap body 201, Positioning boss 202, Annular oil groove 203, Communicating oil groove 204;

[0048] Second screw cap 30; Sealing ring 40;

[0049] Combined piston member 50: Annular step 501, First sloped surface portion 5021, Second sloped surface portion 5022, First piston 503, First elastic member 504, First stepped surface portion 505, Second elastic member 506, Second piston 507, Second stepped surface portion 508, Oil passage hole 509;

[0050] Single piston member 60: Third piston 601, Step portion 602, Piston sleeve 603, Third elastic member 604. Detailed implementation

[0051] Next, the technical solution of the present invention will be clearly and completely described in conjunction with the drawings. Obviously, the described embodiments are part of the embodiments of the present invention, rather than all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative work fall within the protection scope of the present invention.

[0052] In the description of the present invention, it should be noted that the orientation or positional relationship indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation of the present invention. In addition, the terms "first", "second", "third" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance.

[0053] In the description of the present invention, it should be noted that unless otherwise clearly specified and defined, the terms "installed", "connected", "connected" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific situations.

[0054] In the related art, most existing bicycles adopt an independent braking system for the front and rear wheels. During braking, in order to obtain a reasonable deceleration, the rider needs to reasonably distribute the operating force of both hands so that the front and rear tires make full use of the adhesion coefficient of the road surface. However, in actual riding, it is very difficult for the rider to achieve this. Moreover, since the rear wheel of a vehicle during normal riding or acceleration bears most of the weight of the vehicle, the frictional force obtained is greater than that of the front wheel. However, during braking, due to inertia, the center of gravity of the vehicle will shift to the front wheel. When emergency braking is required during high-speed riding, if the front wheel is braked alone, the center of gravity of the vehicle is unstable and there may be a risk of tail whipping.

[0055] Based on the above situation, the embodiments of the present invention provide a dual-channel linkage hydraulic distribution valve, a brake linkage system and a two-wheeled vehicle, which will be elaborated in detail below in conjunction with specific embodiments and drawings.

[0056] Embodiment 1

[0057] The embodiments of the present invention provide a dual-channel linkage hydraulic distribution valve. Figure 1 It is a three-dimensional view of the dual-channel linkage hydraulic distribution valve shown according to an exemplary embodiment. Figure 2 It is a front view of the dual-channel linkage hydraulic distribution valve shown according to an exemplary embodiment. Figure 3 It is a plane sectional view of the dual-channel linkage hydraulic distribution valve shown according to an exemplary embodiment. As Figure 1 -3 shows, the dual-channel linkage hydraulic distribution valve is used in cooperation with a vehicle frame. Specifically, a plurality of assembly holes 108 for fixing and installing with the vehicle frame by screws are opened on the housing 10, and the dual-channel linkage hydraulic distribution valve is fixedly assembled on the vehicle frame through screws passing through the assembly holes 108;

[0058] Figure 4 It is an axial sectional view of the housing shown according to an exemplary embodiment. Referring to the attached Figure 1 -4, the dual-channel linkage hydraulic distribution valve includes:

[0059] A housing 10, in the middle of which a first oil chamber 105, a second oil chamber 106, and an oil chamber passage 107 connecting the first end of the first oil chamber 105 and the first end of the second oil chamber 106 are opened. A first interface 101 and a second interface 102 radially opened on the housing 10 are connected through the side wall near the first end of the first oil chamber 105. A third interface 103 and a fourth interface 104 radially opened on the housing 10 are connected through the side wall near the second end of the second oil chamber 106; Continuing to refer to the attached Figure 1-4. In some embodiments, the first end of the first oil chamber 105 is an open structure and is threadedly fitted with a first screw cap 20, and the inner end of the first screw cap 20 abuts against the first end of the second piston 507; the second ends of both the first oil chamber 105 and the second oil chamber 106 are open structures and are threadedly fitted with second screw caps 30.

[0060] A combined piston member 50, which is movably arranged in the first oil chamber 105;

[0061] Figure 5 is a three-dimensional view of the combined structure of the combined piston member and the single piston member shown according to an exemplary embodiment. Figure 6 is an exploded view of the combined structure of the combined piston member and the single piston member shown according to an exemplary embodiment. Refer to the attached Figure 5 -6. In some embodiments, the combined piston member 50 includes: an annular step 501, which is integrally formed at a position in the first oil chamber 105 corresponding to the second interface 102 and separates the inner end of the second interface 102 into a first branch 1021 and a second branch 1022. Both sides of the inner wall of the annular step 501 are recessed inward to form a first slope surface portion 5021 and a second slope surface portion 5022;

[0062] A first piston 503, which is movably arranged on one side of the first oil chamber 105 close to the first slope surface portion 5021, and a first stepped surface portion 505 matching the first slope surface portion 5021 is formed at its first end, so as to leave the first slope surface portion 5021 and open the second branch 1022 when the oil pressure reaches the third preset oil pressure threshold; a sealing ring 40 is assembled on the annular side wall of the first piston 503;

[0063] A first elastic member 504, which is arranged in the first oil chamber 105 and is located between the second end of the first piston 503 and the second end of the first oil chamber 105, so as to elastically maintain the first stepped surface portion 505 against the first slope surface portion 5021 and close the second branch 1022; in this embodiment, the first elastic member 504 is a compression spring. Further, continue to refer to the attached Figure 3 , spring cavities are opened at the second end of the first piston 503 and the inner end of the second screw cap 30 to partially accommodate the first elastic member 504 and maintain the first elastic member 504 from deforming when axially deformed;

[0064] A second piston 507, which is movably arranged on one side of the first oil chamber 105 close to the second slope surface portion 5022. An oil passage hole 509 communicating with the first interface 101 is opened in the middle of its axis, and a second stepped surface portion 508 matching the second slope surface portion 5022 is formed at its second end, so as to abut against the second slope surface portion 5022 and close the first branch 1021 when the oil pressure reaches the first preset oil pressure threshold; a sealing ring 40 is also assembled on the annular side wall of the second piston 507;

[0065] A second elastic member 506 is disposed within the first oil chamber 105 and between the first end of the first piston 503 and the second end of the second piston 507 to resiliently maintain the second table surface 508 away from the first slope surface 5021 and open the second branch 1022. In this embodiment, the second elastic member 506 is a compression spring. Further, with continued reference to the appendix Figure 3 , spring chambers are formed at the first end of the first piston 503 and the second end of the second piston 507 to partially accommodate the second elastic member 506 and maintain the second elastic member 506 from deforming during axial deformation.

[0066] A single piston member 60 is movably disposed within the second oil chamber 106.

[0067] With continued reference to the appendix Figure 5 -6, in some embodiments, the single piston member 60 includes: a stepped portion 605 formed within the second oil chamber 106 that divides the second oil chamber 106 into a front chamber 1061 communicating with the oil chamber passage 107 and a rear chamber 1062 communicating with the third interface 103 and the fourth interface 104, the inner diameter of the front chamber 1061 being smaller than the inner diameter of the rear chamber 1062.

[0068] A third piston 601, the first section of which is movably assembled within the front chamber 1061 and the second section of which is movably assembled within the rear chamber 1062. The third piston 601 displaces rearward into the rear chamber 1062 when the oil pressure reaches the second preset oil pressure threshold. A sealing ring 40 is also assembled on the annular side wall of the first section of the third piston 601.

[0069] A third elastic member 604 is disposed within the rear chamber 1062 and abuts against the free end of the second section of the third piston 601 and the second end of the second oil chamber 106 to resiliently maintain the third piston 601 positioned at the stepped portion 605. In this embodiment, the third elastic member 604 is a compression spring. Further, with continued reference to the appendix Figure 3 , spring chambers are formed at the second end of the third piston 601 and the inner end of the second screw cap 30 to partially accommodate the third elastic member 604 and maintain the third elastic member 604 from deforming during axial deformation.

[0070] A piston sleeve 603 is fixedly sleeved on the annular side wall of the second section of the third piston 601.

[0071] Among them, with continued reference to the appendix Figure 2 , the combined piston member 50 and the single piston member 60 automatically distribute the brake oil inputted according to the change of the brake oil pressure at the first interface 101 and output it to the second interface 102 and the fourth interface 104 to balance the braking.

[0072] In the technical solution of the above embodiment, in a scenario where the assembly environment is kept clean, the first piston 503 and the first elastic member 504 are inserted into the second end of the first oil chamber 105, the piston sleeve 603 is assembled onto the third piston 601, and the third piston 601 and the third elastic member 604 are inserted into the second end of the second oil chamber 106. Then, the second screw cap 30 is threadedly locked at the second ends of the first oil chamber 105 and the second oil chamber 106 respectively. The second elastic member 506 and the second piston 507 are inserted into the first end of the second oil chamber 106, and the first screw cap 20 is threadedly locked at the first end of the second oil chamber 106, thus completing the rapid assembly of the dual-channel linkage hydraulic distribution valve in this embodiment.

[0073] Subsequently, oil pipes are successively connected to the first interface 101, the second interface 102, the third interface 103, and the fourth interface 104, and the other ends of the oil pipes are successively connected to the first upper pump (left handbrake), the front wheel lower pump, the second upper pump (right handbrake), and the rear wheel lower pump. Brake oil is injected into both the first oil chamber 105 and the second oil chamber 106. It can be understood that currently in most countries in China and the world, the rear wheel lower pump corresponding to the rear wheel brake is controlled by the right handbrake, and the front wheel lower pump corresponding to the front wheel brake is controlled by the left handbrake. When the dual-channel linkage hydraulic distribution valve in this embodiment is connected, when the first upper pump (left handbrake) is pinched for braking, according to the input oil pressure, the combined piston member 50 and the single piston member 60 automatically distribute the brake oil input to the front wheel lower pump and the rear wheel lower pump to balance the braking.

[0074] Continue to refer to the appendix Figure 6 , in some of these embodiments, the first screw cap 20 includes:

[0075] A screw cap body 201, which is threadedly assembled with the first end of the first oil chamber 105;

[0076] A positioning boss 202, which is integrally formed at the inner end of the screw cap body 201 and abuts against the first end of the second piston 507. Its diameter is smaller than the inner diameter of the first oil chamber 105, and an annular oil groove 203 communicating the first interface 101 and the oil chamber passage 107 is formed between it and the inner wall of the first oil chamber 105;

[0077] A communicating oil groove 204, which is radially opened on the side of the positioning boss 202 close to the second piston 507 to communicate the annular oil groove 203 and the oil passage hole 509.

[0078] In the technical solution of the above embodiment, during braking, continue to refer to the appendix Figure 3, the opening force of the first elastic member 504 is F1; the closing force of the second elastic member 506 is F2; the opening force of the third elastic member 604 is F3; the first upper pump input pressure corresponding to the first interface 101 is P, the front wheel output pressure corresponding to the second interface 102 is P1, and the rear wheel output pressure corresponding to the fourth interface 104 is P2; the second upper pump input pressure corresponding to the third interface is P3; the area of the first end of the first piston 503 is SA1; the area of the first end of the second piston 507 is SB1, and the area of the second end is SB2; the area of the first end of the third piston 601 is SC1, and the area of the second end is SC2;

[0079] Refer to the appendix Figure 3 , under normal conditions, the oil circuit in the first oil chamber 105 is in a state where the first interface 101 and the second interface 102 are connected, that is, the oil circuit between the first upper pump and the front wheel lower pump is connected; the third interface 103 and the fourth interface 104 are connected to the rear chamber 1062; the first oil chamber 105 and the front chamber 1061 are connected through the annular oil groove 203 and the oil chamber passage 107, that is, the movement of the third piston 601 allows the oil in the rear chamber 1062 to enter the fourth interface 104 and be output to the rear wheel lower pump for braking;

[0080] When driving the second upper pump for braking, the oil injected through the third interface 103 reaches the fourth interface 104 through the rear chamber 1062 and is output to the rear wheel lower pump, driving the rear wheels of the vehicle to brake;

[0081] When driving the first upper pump for braking:

[0082] S1. When the first upper pump input pressure P is at its initial oil pressure Pa during the first braking, the first path of oil reaches the front chamber 1061 through the annular oil groove 203 - oil chamber passage 107, but the oil pressure of the first path of oil fails to overcome the opening force F3 of the third elastic member 604, and the oil circuit is not connected; the second path of oil reaches the first branch 1021 through the annular oil groove 203 - connecting oil groove 204 - oil hole 50 and is output to the front wheel lower pump through the second interface 102, driving the front wheels of the bicycle to brake slightly, but the oil pressure of the second path of oil fails to overcome the opening force F1 of the first elastic member 504 and the closing force F2 of the second elastic member 506;

[0083] S2. When the first upper pump input pressure P reaches the first preset oil pressure threshold Pb, at this time, the first path of oil overcomes the opening force F3 of the third elastic member 604, but the second path of oil still fails to overcome the opening force F1 of the first elastic member 504 and the closing force F2 of the second elastic member 506. At this time, the first path of oil pushes the third piston 601 to move from the front chamber 1061 to the rear chamber 1062, closing the third interface 103 while pressing the oil in the rear chamber 1062 into the fourth interface 104 and outputting it to the rear wheel lower pump; and the second path of oil continues to be output to the front wheel lower pump through the first branch 1021 - second interface 102. At this time, the front wheels and rear wheels of the bicycle are braked synchronously;

[0084] S3. The input pressure P of the first upper pump continues to increase to the second preset oil pressure threshold value Pc. At this time, the oil in the second path overcomes the closing force F2 of the second elastic member 506 but does not overcome the opening force F1 of the first elastic member 504. The oil pushes the second face portion 508 of the second piston 507 to abut against the second slope face portion 5022 and closes the first branch 1021, that is, closes the second oil path, maintaining the braking force of the front wheel of the bicycle; the oil in the first path still enters the front chamber 1061 and increases the pushing force on the third piston 601. The oil in the rear chamber 1062 continues to be output from the fourth interface 60 to the rear wheel lower pump, driving the increase of the braking force of the rear wheel of the bicycle;

[0085] S4. When the input pressure P of the first upper pump reaches the third preset oil pressure threshold value Pd, the oil in the first path still enters the front chamber 1061 and increases the pushing force on the third piston 601. The oil in the rear chamber 1062 continues to be output from the fourth interface 60 to the rear wheel lower pump, and the oil in the first path drives the continuous increase of the braking force of the rear wheel of the bicycle; at the same time, the oil in the second path overcomes the closing force F2 of the second elastic member 506 and the opening force F1 of the first elastic member 504. The first slope face portion 5021 leaves the first face portion 505 and opens the second branch 1022, that is, the oil in the second path passes through the annular oil groove 203 - the communicating oil groove 204 - the oil passage hole 50 to reach the second branch 1022 and is output to the front wheel lower pump through the second interface 102, driving the increase of the braking force of the front wheel of the bicycle, realizing the automatic distribution of the braking force to the front wheel lower pump and the rear wheel lower pump according to the preset pressure ratio, and finally achieving the reasonable distribution of the front and rear braking forces (in this embodiment, P1:P2 = 6:4 ， Specifically, P1:P2 is the ratio of the braking forces of the front and rear wheels and is the ratio of the large and small end areas of the first piston 601. In this example, the large end diameter of the first piston 601 is 12 mm and the small end diameter is 10 mm. Therefore, the ratio of the braking forces of the front and rear wheels is 36 / 25 = 1.44, that is, the distribution of the braking forces of the front and rear wheels is approximately 6:4), the braking distance can be significantly shortened, and the risk of the bicycle skidding can be reduced;

[0086] Further, when the second upper pump brakes, its braking forward pressure is only the output pressure P2 of the rear wheel:

[0087] P2 = P3 × Se

[0088] In the formula, P2 is the output pressure of the rear wheel, P3 is the input pressure of the second upper pump, and Se is the piston area of the rear wheel lower pump corresponding to the fourth interface 104, which is not shown in the figure;

[0089] When the first upper pump brakes:

[0090] When reaching the first preset oil pressure threshold value Pb, its braking forward pressure is the output pressure P1 of the front wheel + the output pressure P2 of the rear wheel:

[0091] P1 = P × Se

[0092] P2 = P × Se × (SC1 / SC2)

[0093] Wherein, Se is the piston area of the rear wheel slave cylinder corresponding to the fourth interface 104, which is not shown in the figure, SC1 is the area of the first end of the third piston 601, and SC2 is the area of the second end of the third piston 601;

[0094] When the second preset oil pressure threshold Pc is reached, its braking forward pressure is the front wheel output pressure P1 + the rear wheel output pressure P2:

[0095] P1 = P × Se

[0096] P2 = P × Se × (SC1 / SC2)

[0097] Wherein, the piston area of the rear wheel slave cylinder corresponding to the fourth interface 104 is not shown in the figure, SC1 is the area of the first end of the third piston 601, and SC2 is the area of the second end of the third piston 601; At this time, the front wheel output pressure P1 remains unchanged and the rear wheel output pressure P2 increases;

[0098] When the third preset oil pressure threshold Pc is reached, its braking forward pressure is the front wheel output pressure P1 + the rear wheel output pressure P2:

[0099] P1 = P × Se

[0100] P2 = P × Se × (SC1 / SC2)

[0101] Wherein, Se is the piston area of the rear wheel slave cylinder corresponding to the fourth interface 104, which is not shown in the figure, SC1 is the area of the first end of the third piston 601, and SC2 is the area of the second end of the third piston 601; At this time, the front wheel output pressure P1 increases and the rear wheel output pressure P2 increases;

[0102] In this embodiment, the first elastic member 504, the second elastic member 506, and the third elastic member 604 are all compression springs, and the opening force F1 of the first elastic member 504; the closing force F2 of the second elastic member 506; the opening force F3 of the third elastic member 604 can all select appropriate springs through the method of calculating the oil pressure output in advance;

[0103] P = 4F / πd 2

[0104] Wherein, P is the piston opening pressure, F is the elastic force of the elastic member, d is the diameter value of the compressed end face of the first piston 503, and the diameter difference between the two compressed end faces of the second piston 507 / the third piston 601.

[0105] In summary, for the dual-channel linked hydraulic distribution valve provided by the embodiments of the present utility model, when an input is applied to the first interface 101, the initial output is at the second interface 102, and the front-wheel lower pump operates to slightly brake the front wheels first, shifting the center of gravity backward; secondly, the second interface 102 and the fourth interface 104 output simultaneously to control the simultaneous operation of the front-wheel lower pump and the rear-wheel lower pump to maintain braking balance; then, the braking force is increased, and the rear-wheel lower pump increases the braking force on the rear wheels to shorten the braking distance; until finally, the braking force is automatically distributed to the front-wheel lower pump and the rear-wheel lower pump according to a preset pressure threshold ratio, achieving the reasonable coordinated braking of the front and rear brakes of the bicycle by a single upper pump. Compared with the braking force distribution of manual braking, it is more convenient, efficient, and accurate, and the braking distance can be significantly shortened, reducing the risk of the bicycle skidding; at the same time, when an input is applied to the third interface 103, it directly outputs simultaneously through the fourth interface 104 to brake the rear wheels first. And without changing the overall braking structure of the bicycle and maximizing cost reduction, the present application realizes the synchronous linked braking of the front and rear wheels.

[0106] Embodiment 2

[0107] Embodiment 2 of the present application provides a braking linkage system, including the dual-channel linked hydraulic distribution valve of Embodiment 1 above, and

[0108] a first upper pump, which is connected to the first interface 101 through a first oil pipe;

[0109] a front-wheel lower pump, which is connected to the second interface 102 through a second oil pipe;

[0110] a second upper pump, which is connected to the third interface 103 through a third oil pipe;

[0111] a rear-wheel lower pump, which is connected to the fourth interface 104 through a fourth oil pipe;

[0112] wherein, when the first upper pump brakes, the dual-channel linked hydraulic distribution valve automatically distributes the oil fluid input through the first interface 101 to the front-wheel lower pump and the rear-wheel lower pump according to the change in the oil pressure to balance the braking; when the second upper pump brakes, the dual-channel linked hydraulic distribution valve distributes the oil fluid input through the third interface 103 to the rear-wheel lower pump to brake.

[0113] For other structures not described, refer to Embodiment 1.

[0114] In summary, the dual-channel linkage hydraulic distribution valve and the brake linkage system provided by the embodiments of the present utility model achieve the following: when braking, the first upper pump is operated independently. Initially, the front-wheel lower pump works to slightly brake the front wheels, shifting the center of gravity backward. Secondly, the front-wheel lower pump and the rear-wheel lower pump are controlled to work simultaneously to maintain braking balance. Thirdly, the braking force is increased, and the rear-wheel lower pump increases the braking force on the rear wheels to shorten the braking distance. Finally, the braking force is automatically distributed to the front-wheel lower pump and the rear-wheel lower pump according to the preset pressure threshold ratio, realizing the reasonable coordinated braking of the front and rear brakes of the bicycle by a single upper pump. Compared with the braking force distribution of manual brakes, it is more convenient, efficient, and accurate, and the braking distance can be significantly shortened, reducing the risk of the bicycle skidding. At the same time, the synchronous linkage braking of the front and rear wheels is achieved without changing the overall braking structure of the bicycle and maximizing cost reduction.

[0115] Embodiment 3

[0116] Embodiment 3 of the present application provides a two-wheeled vehicle including the brake linkage system of the second aspect above. The two-wheeled vehicle in this embodiment is not limited to bicycles or electric bicycles, and can also be extended to vehicles with two-way braking systems such as motorcycles.

[0117] For other un-described structures, refer to Embodiment 1.

[0118] In summary, the dual-channel linkage hydraulic distribution valve, the brake linkage system, and the two-wheeled vehicle provided by the embodiments of the present utility model achieve the following: when braking, the first upper pump is operated independently. Initially, the front-wheel lower pump works to slightly brake the front wheels, shifting the center of gravity backward. Secondly, the front-wheel lower pump and the rear-wheel lower pump are controlled to work simultaneously to maintain braking balance. Thirdly, the braking force is increased, and the rear-wheel lower pump increases the braking force on the rear wheels to shorten the braking distance. Finally, the braking force is automatically distributed to the front-wheel lower pump and the rear-wheel lower pump according to the preset pressure threshold ratio, realizing the reasonable coordinated braking of the front and rear brakes of the bicycle by a single upper pump. Compared with the braking force distribution of manual brakes, it is more convenient, efficient, and accurate, and the braking distance can be significantly shortened, reducing the risk of the bicycle skidding. At the same time, the synchronous linkage braking of the front and rear wheels is achieved without changing the overall braking structure of the bicycle and maximizing cost reduction.

[0119] The technical features of the above embodiments can be combined arbitrarily. For the sake of brevity of description, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, it should be considered as the scope recorded in this specification.

[0120] The above embodiments only represent several implementation manners of the present application. The description is relatively specific and detailed, but it should not be construed as a limitation on the scope of the utility model patent. It should be noted that for those of ordinary skill in the art, without departing from the concept of the present application, several modifications and improvements can still be made, and these all belong to the protection scope of the present application. Therefore, the protection scope of the patent of the present application shall be subject to the appended claims.

Claims

1. A dual-channel linked hydraulic distribution valve, which is used in conjunction with a vehicle frame, is characterized in that, Comprising: A housing, in the middle of which there are provided a first oil chamber, a second oil chamber, and an oil chamber passage connecting the first end of the first oil chamber and the first end of the second oil chamber. On the side wall of the first oil chamber near its first end, there are through-connected a first interface and a second interface radially opened on the housing. On the side wall of the second oil chamber near its second end, there are through-connected a third interface and a fourth interface radially opened on the housing; A combined piston member, which is movably arranged in the first oil chamber; A single piston member, which is movably arranged in the second oil chamber; Wherein, the combined piston member and the single piston member automatically distribute the brake oil input from the first interface according to the change of the brake oil pressure and output it to the second interface and the fourth interface to balance the braking.

2. The dual-channel linkage hydraulic distribution valve according to claim 1, characterized in that: The combined piston member includes: An annular step, which is integrally formed at a position in the first oil chamber corresponding to the second interface and divides the inner end of the second interface into a first branch and a second branch. Both sides of the inner wall of the annular step are recessed inward to form a first slope surface and a second slope surface; A first piston, which is movably arranged on one side of the first oil chamber near the first slope surface, and a first stepped surface matching the first slope surface is formed at its first end, so as to leave the first slope surface and open the second branch when the oil pressure reaches the third preset oil pressure threshold; A first elastic member, which is arranged in the first oil chamber and is located between the second end of the first piston and the second end of the first oil chamber, so as to elastically maintain the first stepped surface in contact with the first slope surface and close the second branch; A second piston, which is movably arranged on one side of the first oil chamber near the second slope surface. An oil passage hole communicating with the first interface is provided in the middle of its axis, and a second stepped surface matching the second slope surface is formed at its second end, so as to contact the second slope surface and close the first branch when the oil pressure reaches the second preset oil pressure threshold; A second elastic member, which is arranged in the first oil chamber and is located between the first end of the first piston and the second end of the second piston, so as to elastically maintain the second stepped surface away from the first slope surface and open the second branch.

3. The dual-channel linkage hydraulic distribution valve according to claim 2, wherein: The first end of the first oil chamber is of an open structure and is threadedly assembled with a first screw cap, and the inner end of the first screw cap abuts against the first end of the second piston.

4. The dual-channel linkage hydraulic distribution valve according to claim 3, characterized in that: The first screw cap includes: A screw cap body, which is threadedly assembled with the first end of the first oil chamber; A positioning boss, which is integrally formed at the inner end of the screw cap body and abuts against the first end of the second piston. Its diameter is smaller than the inner diameter of the first oil chamber, and an annular oil groove communicating the first interface and the oil chamber passage is formed between it and the inner wall of the first oil chamber; A communicating oil groove, which is radially opened on the side of the positioning boss near the second piston to communicate the annular oil groove and the oil passage hole.

5. The dual-channel linkage hydraulic distribution valve according to claim 1, characterized in that: The single piston member includes: A stepped portion, which is formed in the second oil chamber and divides the second oil chamber into a front chamber communicating with the oil chamber passage and a rear chamber communicating with the third interface and the fourth interface. The inner diameter of the front chamber is smaller than that of the rear chamber; A third piston, the first section of which is movably assembled in the front cavity, and the second section of which is movably assembled in the rear cavity. When the oil pressure reaches a first preset oil pressure threshold, the third piston displaces towards the rear cavity; A third elastic member, which is arranged in the rear cavity and abuts against the free end of the second section of the third piston and the second end of the second oil cavity respectively, to elastically maintain the third piston limited at the step portion; A piston sleeve, which is fixedly sleeved on the annular side wall of the second section of the third piston.

6. The dual-channel linkage hydraulic distribution valve according to claim 1, characterized in that: Sealing rings are assembled on the active contact surfaces of the combined piston member with the first oil cavity and the active contact surfaces of the single piston member with the second oil cavity.

7. The dual-channel linkage hydraulic distribution valve according to claim 1, characterized in that: A plurality of assembly holes for fixedly installing with the vehicle frame by screws are formed in the housing.

8. The dual-channel linked hydraulic distribution valve according to claim 1, wherein: The second ends of the first oil cavity and the second oil cavity are both of open structures and are threadedly assembled with second screw caps.

9. A brake linkage system, characterized in that, It includes the dual-channel linkage hydraulic distribution valve according to any one of claims 1-8 above, and A first upper pump, which is connected to the first interface through a first oil pipe; A front-wheel lower pump, which is connected to the second interface through a second oil pipe; A second upper pump, which is connected to the third interface through a third oil pipe; A rear-wheel lower pump, which is connected to the fourth interface through a fourth oil pipe; Wherein, when the first upper pump brakes, the dual-channel linkage hydraulic distribution valve automatically distributes the oil fluid input from the first interface to the front-wheel lower pump and the rear-wheel lower pump according to the oil pressure change to balance the braking; when the second upper pump brakes, the dual-channel linkage hydraulic distribution valve distributes the oil fluid input from the third interface to the rear-wheel lower pump to brake.

10. A two-wheeled vehicle, characterized in that, It includes the brake linkage system according to claim 9 above.

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