Interlinked hydraulic distribution valve, brake interlinked system and two-wheeled vehicle

Abstract

An interlinked hydraulic distribution valve, a brake interlinked system and a two-wheeled vehicle. The interlinked hydraulic distribution valve comprises: a housing (10), the middle of which is provided with a first oil cavity (105), a second oil cavity (106), and an oil cavity channel (107) connecting a first end of the first oil cavity (105) to a first end of the second oil cavity (106), wherein a first connection port (101) and a second connection port (102), which are radially formed in the housing (10), are connected in a penetrating manner to the side wall of the first oil cavity (105) close to the first end thereof, and a third connection port (103) radially formed in the housing (10) is connected in a penetrating manner to the side wall of the second oil cavity (106) close to a second end thereof; a combined piston member (50), which is movably arranged in the first oil cavity (105); and a single piston member (60), which is movably arranged in the second oil cavity (106), wherein the combined piston member (50) and the single piston member (60) automatically distribute and output a brake fluid, which is inputted through the first connection port (101), to the second connection port (102) and the third connection port (103), so as to balance braking. The structure realizes the rational coordinated braking of front and rear brakes of a bicycle by means of a single master cylinder, thereby significantly shortening the braking distance, and reducing the risk of rear-wheel skid of a bicycle.

Description

A hydraulic distribution valve, a brake linkage system, and a two-wheeled vehicle Technical Field

[0001] This invention relates to the field of bicycle parts technology, specifically to a linkage hydraulic distribution valve, a brake linkage system, and a two-wheeled vehicle. Background Technology

[0002] Most bicycles currently use independent braking systems for the front and rear wheels. During braking, to achieve reasonable deceleration, the rider needs to properly distribute the force applied by both hands, allowing the front and rear tires to fully utilize the road surface's coefficient of friction. However, in actual riding, this is difficult for riders to do. Because the rear wheel bears most of the vehicle's weight during normal riding or acceleration, it experiences greater friction than the front wheel. But during braking, due to inertia, the vehicle's center of gravity shifts to the front wheel.

[0003] When braking suddenly at high speeds, braking only the front wheel can cause instability in the vehicle's center of gravity, potentially leading to a fishtailing risk. To address this, we propose a linked hydraulic distribution valve, a brake linkage system, and a two-wheeled vehicle. Summary of the Invention

[0004] This application provides a linked hydraulic distribution valve, a brake linkage system, and a two-wheeled vehicle to at least solve the problem in the prior art where braking only the front wheels causes instability in the vehicle's center of gravity, potentially leading to a fishtailing risk.

[0005] Firstly, this application provides a linkage hydraulic distribution valve, which is used in conjunction with a vehicle frame, comprising:

[0006] The housing has a first oil cavity, a second oil cavity, and an oil cavity channel connecting the first end of the first oil cavity and the first end of the second oil cavity in its middle part. The first oil cavity has a first interface and a second interface that are radially opened on the housing through the side wall near its first end. The second oil cavity has a third interface and a third interface that are radially opened on the housing through the side wall near its second end.

[0007] A combined piston assembly is movably disposed within the first oil chamber;

[0008] A single piston component is movably disposed within the second oil chamber;

[0009] The combined piston assembly and the single piston assembly automatically distribute the brake fluid input from the first interface to the second and third interfaces to balance braking.

[0010] Optionally, the combined piston assembly includes:

[0011] An annular step is integrally formed in the first oil cavity at the position corresponding to the second interface and divides the inner end of the second interface into a first branch and a second branch. The inner walls of the annular step are recessed inward on both sides and form a first slope and a second slope.

[0012] The first piston is movably disposed in the first oil chamber on one side near the first slope surface, and its first end is formed with a first facet surface that cooperates with the first slope surface, so that when the oil pressure reaches the third preset oil pressure threshold, it leaves the first slope surface and opens the second branch.

[0013] A first elastic element is disposed in the first oil cavity and located between the second end of the first piston and the second end of the first oil cavity, so as to elastically maintain the first platform surface abutting the first slope surface and close the second branch.

[0014] The second piston is movably disposed in the first oil chamber on one side near the second slope surface. It has an oil passage hole in its axial middle part that connects to the first interface, and its second end is formed with a second platform surface that cooperates with the second slope surface so that it abuts against the second slope surface and closes the first branch when the oil pressure reaches the second preset oil pressure threshold.

[0015] The second elastic element is disposed in the first oil cavity and located between the first end of the first piston and the second end of the second piston to elastically maintain the second platform 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 threaded with a first screw cap, the inner end of the first screw cap abutting the first end of the second piston;

[0017] The first screw cap includes:

[0018] A screw cap body, which is threadedly assembled with the first end of the first oil cavity;

[0019] The positioning boss is integrally formed on the inner end of the screw cap and abuts against the first end of the second piston. Its diameter is smaller than the inner diameter of the first oil cavity and an annular oil groove is formed between the inner wall of the first oil cavity and the first interface and the oil cavity channel.

[0020] A connecting oil hole is provided on the side of the positioning boss near the second piston, and its two ends are respectively connected to the first interface and the annular oil groove.

[0021] Optionally, the single piston component includes:

[0022] A stepped portion is formed within the second oil cavity and divides the second oil cavity into a front cavity that connects to the oil cavity channel, and a rear cavity that connects to the third interface, wherein the inner diameter of the front cavity is smaller than the inner diameter of the rear cavity;

[0023] The third piston has its first section movably assembled in the front cavity and its second section movably assembled in the rear cavity. When the oil pressure reaches the first preset oil pressure threshold, the third piston moves towards the rear cavity.

[0024] A third elastic element is disposed 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, so as to elastically maintain the third piston in the stepped portion.

[0025] The piston sleeve is fixedly fitted onto the annular sidewall of the second section of the third piston.

[0026] Optionally, sealing rings are fitted on the movable contact surfaces of the combined piston component and the first oil chamber, and on the movable contact surfaces of the individual piston component and the second oil chamber.

[0027] Optionally, it also includes:

[0028] An oil sump cavity is formed in the middle of the housing, and the oil sump cavity is connected to the second oil cavity through an oil replenishment channel;

[0029] An oil replenishing piston is movably disposed within the oil sump cavity;

[0030] The oil replenishing piston replenishes brake fluid into the second oil chamber during braking to balance the brake fluid pressure.

[0031] Optionally, the oil replenishing piston component includes:

[0032] A limiting step is integrally formed inside the oil sump cavity at the position corresponding to the oil replenishment channel;

[0033] A piston body is movably assembled within the oil sump cavity and moves within the oil sump cavity in accordance with the movement of the oil, so as to adaptively adjust the capacity of the oil sump cavity.

[0034] An oil tank cover is fitted to the first end of the oil tank cavity, and the oil tank cover has a pressure balance hole that connects to the external atmospheric pressure.

[0035] Optionally, an assembly step is provided on the inner wall of the first end of the oil tank cavity, and a cotter pin is provided on the side of the oil tank cover away from the oil tank cavity. The cotter pin is engaged with the opening at the second end of the oil tank cavity to cooperate with the assembly step to position the axial position of the oil tank cover.

[0036] Optionally, a fourth interface radially formed on the housing is also connected through the side wall of the rear cavity.

[0037] Secondly, this application provides a brake linkage system, including the linkage hydraulic distribution valve described in the first aspect, and

[0038] The first upper pump is connected to the first interface via a first oil pipe;

[0039] The front wheel lower pump is connected to the second interface via a second oil pipe;

[0040] The rear wheel pump is connected to the third interface via a third oil pipe.

[0041] When the first upper pump brakes, the linkage hydraulic distribution valve automatically distributes the oil output to the front wheel lower pump and the rear wheel lower pump according to the oil pressure change of the oil input at the first interface to balance the braking.

[0042] Thirdly, this application provides a braking linkage system, including the braking linkage system described in the second aspect above.

[0043] Compared with related technologies, the linkage hydraulic distribution valve, brake linkage system, and two-wheeled vehicle provided in this application have at least the following technical advantages:

[0044] During braking, the first upper pump is operated independently. Initially, the front wheel lower pump works, slightly braking the front wheel to shift the center of gravity backward. Then, the front and rear wheel lower pumps are controlled to work simultaneously to maintain braking balance. Finally, the braking force is continuously increased. At this time, the braking force is automatically distributed to the front and rear wheel lower pumps according to the preset pressure threshold ratio. This achieves reasonable coordination of braking between the front and rear brakes by a single upper pump. Compared with manual braking, the braking force distribution is simpler, more efficient and precise, and the braking distance can be significantly shortened, reducing the risk of the bicycle skidding. At the same time, it achieves synchronous linkage braking of the front and rear wheels without changing the overall braking structure of the bicycle and minimizing costs.

[0045] Details of one or more embodiments of this application are set forth in the following drawings and description to make other features, objects and advantages of this application more readily apparent. Attached Figure Description

[0046] To more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0047] Figure 1 is a perspective view of a linkage hydraulic distribution valve according to an exemplary embodiment.

[0048] Figure 2 is a front view of a linkage hydraulic distribution valve according to an exemplary embodiment.

[0049] Figure 3 is a plan view of a hydraulic distribution valve according to an exemplary embodiment.

[0050] Figure 4 is a axial cross-sectional view of the housing according to an exemplary embodiment.

[0051] Figure 5 is a perspective view of the combined structure of the combined piston and the single piston according to an exemplary embodiment.

[0052] Figure 6 is an exploded view of the combined structure of the combined piston and the single piston according to an exemplary embodiment.

[0053] Figure 7 shows a perspective view of a first screw cap according to an alternative embodiment.

[0054] Figure 8 is one of the perspective views of a hydraulic pressure balance linkage valve according to another exemplary embodiment.

[0055] Figure 9 is a second perspective view of a hydraulic pressure balance linkage valve according to another exemplary embodiment.

[0056] Figure 10 is a top view of a hydraulic pressure balance linkage valve according to another exemplary embodiment.

[0057] Figure 11 is a cross-sectional view of the AA structure in Figure 10.

[0058] Figure 12 is a cross-sectional view of the BB structure in Figure 10.

[0059] Figure 13 is a cross-sectional view of the shell based on the AA structure in Figure 10.

[0060] Figure 14 is a cross-sectional view of the shell based on the BB structure in Figure 10.

[0061] Figure 15 is a perspective view of an oil replenishing piston according to another exemplary embodiment.

[0062] Explanation of reference numerals in the attached drawings: Housing 10: First interface 101, Second interface 102, First branch 1021, Second branch 1022, Third interface 103, Fourth interface 104, First oil cavity 105, Second oil cavity 106, Oil cavity channel 107, Assembly hole 108, Oil replenishment channel 109, Oil sump cavity 100;

[0063] First screw cap 20: screw cap body 201, positioning boss 202, annular oil groove 203, connecting oil groove 204;

[0064] Second screw cap 30; sealing ring 40;

[0065] Combined piston component 50: annular step 501, first slope surface 5021, second slope surface 5022, first piston 503, first elastic element 504, first platform surface 505, second elastic element 506, second piston 507, second platform surface 508, oil passage hole 509.

[0066] Single piston component 60: third piston 601, stepped portion 602, piston sleeve 603, third elastic component 604;

[0067] Oil replenishment piston component 70: limiting step 701, piston body 702, oil sump cover 703, cotter pin 704. Detailed Implementation

[0068] The technical solution of the present invention will now be clearly and completely described with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0069] In the description of this invention, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing the invention and for 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 the invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0070] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0071] In related technologies, most existing bicycles use independent braking systems for the front and rear wheels. During braking, to achieve reasonable deceleration, the rider needs to properly distribute the force applied by both hands, allowing the front and rear tires to fully utilize the road surface's coefficient of friction. However, in actual riding, this is difficult for riders to achieve. Because the rear wheel bears most of the vehicle's weight during normal riding or acceleration, it experiences greater friction than the front wheel. But during braking, due to inertia, the vehicle's center of gravity shifts to the front wheel. In high-speed riding requiring emergency braking, braking only the front wheel can cause instability in the vehicle's center of gravity, potentially leading to a fishtailing risk.

[0072] Based on the above, embodiments of the present invention provide a linkage hydraulic distribution valve, a brake linkage system, and a two-wheeled vehicle, which will be described in detail below with reference to specific embodiments and accompanying drawings.

[0073] Example 1

[0074] This invention provides a linkage hydraulic distribution valve. Figure 1 is a perspective view of the linkage hydraulic distribution valve according to an exemplary embodiment. Figure 2 is a front view of the linkage hydraulic distribution valve according to an exemplary embodiment. Figure 3 is a planar sectional view of the linkage hydraulic distribution valve according to an exemplary embodiment. As shown in Figures 1-3, the linkage hydraulic distribution valve is used with a vehicle frame. Specifically, the housing 10 has a plurality of mounting holes 108 for fixing the valve to the vehicle frame with screws. The linkage hydraulic distribution valve is fixedly mounted on the vehicle frame by screws passing through the mounting holes 108.

[0075] Figure 4 is a axial sectional view of the housing according to an exemplary embodiment. Referring to Figures 1-4, the linked hydraulic distribution valve includes:

[0076] The housing 10 has a first oil cavity 105, a second oil cavity 106, and an oil cavity channel 107 connecting the first end of the first oil cavity 105 and the first end of the second oil cavity 106. The first oil cavity 105 has a first interface 101 and a second interface 102 radially opened on the side wall near its first end. The second oil cavity 106 has a third interface 103 radially opened on the side wall near its second end. Referring to Figures 1-4, in some embodiments, the first end of the first oil cavity 105 is an open structure and is threaded with a first screw cap 20. The inner end of the first screw cap 20 abuts against the first end of the second piston 507. The second ends of the first oil cavity 105 and the second oil cavity 106 are both open structures and are threaded with a second screw cap 30.

[0077] The combined piston component 50 is movably disposed within the first oil chamber 105;

[0078] Figure 5 is a perspective view of the combined structure of the combined piston and the single piston according to an exemplary embodiment. Figure 6 is an exploded view of the combined structure of the combined piston and the single piston according to an exemplary embodiment. Referring to Figures 5-6, in some embodiments, the combined piston 50 includes: an annular step 501, which is integrally formed in the first oil cavity 105 at a position corresponding to the second interface 102 and divides the inner end of the second interface 102 into a first branch 1021 and a second branch 1022. The inner walls of the annular step 501 are recessed inward on both sides and form a first slope surface 5021 and a second slope surface 5022.

[0079] The first piston 503 is movably disposed in the first oil chamber 105 on one side near the first slope surface 5021, and its first end is formed with a first face surface 505 that cooperates with the first slope surface 5021, so that when the oil pressure reaches the third preset oil pressure threshold, it leaves the first slope surface 5021 and opens the second branch 1022; a sealing ring 40 is fitted on the annular sidewall of the first piston 503.

[0080] The first elastic element 504 is disposed in the first oil cavity 105 and located between the second end of the first piston 503 and the second end of the first oil cavity 105, so as to elastically maintain the first platform surface 505 abutting against the first slope surface 5021 and close the second branch 1022; in this embodiment, the first elastic element 504 is a compression spring. Further, referring to Figure 3, the second end of the first piston 503 and the inner end of the second screw cap 30 are both provided with spring cavities to partially accommodate the first elastic element 504 and maintain the first elastic element 504 from deformation when it undergoes axial deformation;

[0081] The second piston 507 is movably disposed in the first oil chamber 105 on one side near the second slope surface 5022. It has an oil passage hole 509 in its axial middle part that connects to the first interface 101, and its second end is formed with a second surface 508 that cooperates with the second slope surface 5022 so that it abuts against the second slope surface 5022 and closes the first branch 1021 when the oil pressure reaches the first preset oil pressure threshold. A sealing ring 40 is also fitted on the annular sidewall of the second piston 507.

[0082] The second elastic element 506 is disposed in the first oil cavity 105 and located between the first end of the first piston 503 and the second end of the second piston 507, so as to elastically maintain the second platform surface 508 away from the first slope surface 5021 and open the second branch 1022; in this embodiment, the second elastic element 506 is a compression spring. Further, referring to Figure 3, the first end of the first piston 503 and the second end of the second piston 507 are both provided with spring cavities to partially accommodate the second elastic element 506 and maintain the second elastic element 506 from deformation when it undergoes axial deformation.

[0083] The single piston component 60 is movably disposed within the second oil chamber 106;

[0084] Referring again to Figures 5-6, in some embodiments, the single piston member 60 includes: a stepped portion 605, which is formed in the second oil cavity 106 and divides the second oil cavity 106 into a front cavity 1061 that communicates with the oil cavity channel 107, and a rear cavity 1062 that communicates with the third interface 103, wherein the inner diameter of the front cavity 1061 is smaller than the inner diameter of the rear cavity 1062.

[0085] The third piston 601 has its first section movably assembled in the front cavity 1061 and its second section movably assembled in the rear cavity 1062. When the oil pressure reaches the second preset oil pressure threshold, the third piston 601 moves to the rear cavity 1062. A sealing ring 40 is also assembled on the annular side wall of the first section of the third piston 601.

[0086] The third elastic element 604 is disposed in the rear cavity 1062 and abuts against the free end of the second section of the third piston 601 and the second end of the second oil cavity 106, respectively, so as to elastically maintain the third piston 601 in the step portion 605. In this embodiment, the third elastic element 604 is a compression spring. Further, referring to Figure 3, the second end of the third piston 601 and the inner end of the second screw cap 30 are provided with spring cavities to partially accommodate the third elastic element 604 and maintain the third elastic element 604 from deformation when it undergoes axial deformation.

[0087] Piston sleeve 603 is fixedly sleeved on the annular sidewall of the second section of the third piston 601.

[0088] Referring to Figure 2, the combined piston 50 and the single piston 60 automatically distribute the brake fluid input from the first interface 101 to the second interface 102 and the third interface 103 to balance the braking.

[0089] In the above embodiment, under the scenario of ensuring a clean assembly environment, the first piston 503 and the first elastic element 504 are installed from 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 element 604 are installed from the second end of the second oil chamber 106. The second screw cap 30 is then threaded and locked at the second ends of the first oil chamber 105 and the second oil chamber 106, respectively. The second elastic element 506 and the second piston 507 are installed from the first end of the second oil chamber 106, and the first screw cap 20 is threaded and locked at the first end of the second oil chamber 106, thus completing the rapid assembly of the linkage hydraulic distribution valve in this embodiment.

[0090] Subsequently, the oil pipes are connected sequentially to the first interface 101, the second interface 102, and the third interface 103, and the other end of the oil pipes is sequentially connected to the first upper pump (left handbrake), the front wheel lower pump, and the rear wheel lower pump. Braking fluid is injected into both the first oil chamber 105 and the second oil chamber 106. It is understood that currently, in my country and most countries in the world, the rear wheel lower pump is controlled by the right handbrake, corresponding to the rear wheel brake, and the front wheel lower pump is controlled by the left handbrake, corresponding to the front wheel brake. When the first upper pump (left handbrake) is squeezed, the combined piston 50 and the single piston 60 automatically distribute the braking fluid input to the front wheel lower pump and the rear wheel lower pump according to the change in braking oil pressure to balance the braking.

[0091] Referring again to Figure 6, in some embodiments, the first screw cap 20 includes:

[0092] The screw cap body 201 is threadedly assembled with the first end of the first oil cavity 105;

[0093] The positioning boss 202 is integrally formed on 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 cavity 105 and an annular oil groove 203 is formed between the inner wall of the first oil cavity 105 and the first interface 101 and the oil cavity channel 107.

[0094] The connecting oil hole 204 is opened on the side of the positioning boss 202 near the second piston 507, and its two ends are respectively connected to the first interface 101 and the annular oil groove 203. In this embodiment, the connecting oil hole 204 is L-shaped and opened in the positioning boss 202, and its first end is set on the side of the positioning boss 202 near the second piston 507, and its second end is connected to the annular oil groove 203 to pass through the oil passage.

[0095] In one alternative embodiment, FIG7 shows a perspective view of the first screw cap according to an alternative embodiment. Referring to FIG7, the connecting oil hole 204 can also be configured as a connecting oil groove, which is radially opened on the side of the positioning boss 202 near the second piston 507 to connect the annular oil groove 203 and the oil passage hole 509; it is understood that the configuration of the connecting oil groove or the connecting oil hole 204 does not affect the implementation of the embodiment of this application, and is only provided as an example of an alternative solution.

[0096] In the above embodiment, during braking, referring to Figure 3, the opening force of the first elastic element 504 is F1; the closing force of the second elastic element 506 is F2; ​​the opening force of the third elastic element 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; the rear wheel output pressure corresponding to the third interface 103 is P2; 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.

[0097] Referring to Figure 3, under normal conditions, the oil passage in the first oil chamber 105 is connected to the first interface 101 and the second interface 102, that is, the oil passage between the first upper pump and the front wheel lower pump is connected; the third interface 103 is 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 channel 107, that is, the movement of the third piston 601 can drive the oil in the rear chamber 1062 to enter the third interface 103 and output to the rear wheel lower pump for braking;

[0098] When the first upper pump is driven for braking:

[0099] S1. The initial oil pressure Pa of the first upper pump input pressure P when braking first, the first oil flows through the annular oil groove 203-oil chamber channel 107 to the front chamber 1061, but the oil pressure of the first oil cannot overcome the opening force F3 of the third elastic element 604, so the oil circuit is not connected; the second oil flows through the annular oil groove 203-connecting oil groove 204-oil passage hole 50 to the first branch 1021 and is output to the front wheel lower pump through the second interface 102, driving the front wheel of the bicycle to brake slightly, but the oil pressure of the second oil cannot overcome the opening force F1 of the first elastic element 504 and the closing force F2 of the second elastic element 506;

[0100] S2. When the input pressure P of the first upper pump reaches the first preset oil pressure threshold Pb, the first oil path overcomes the opening force F3 of the third elastic element 604, but the second oil path is temporarily unable to overcome the opening force F1 of the first elastic element 504 and the closing force F2 of the second elastic element 506. At this time, the first oil path pushes the third piston 601 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 third interface 103 and outputting it to the rear wheel lower pump; while the second oil path continues to be output to the front wheel lower pump through the first branch 1021-second interface 102. At this time, the front wheel and rear wheel of the bicycle are braked synchronously.

[0101] S3. The input pressure P of the first upper pump continues to increase to the second preset oil pressure threshold Pc. At this time, the second oil overcomes the closing force F2 of the second elastic element 506 but does not overcome the opening force F1 of the first elastic element 504. The oil pushes the second face 508 of the second piston 507 to abut against the second slope face 5022 and closes the first branch 1021, that is, closes the second oil circuit, maintaining the braking force of the bicycle's front wheel. The first path still enters the front chamber 1061 and increases the push on the third piston 601. The oil in the rear chamber 1062 continues to be output from the third interface 103 to the rear wheel lower pump, driving the rear wheel braking force of the bicycle to increase.

[0102] S4. When the input pressure P of the first upper pump reaches the third preset oil pressure threshold Pd, the first oil path still enters the front chamber 1061 and increases the push on the third piston 601. The oil in the rear chamber 1062 continues to be output from the third interface 103 to the rear wheel lower pump. The first oil path drives the rear wheel braking force of the bicycle to continuously increase. At the same time, the second oil path overcomes the closing force F2 of the second elastic element 506 and the opening force F1 of the first elastic element 504. The first slope surface 5021 leaves the first platform surface 505 and opens the second branch 1022. That is, the second oil path reaches the second branch 1022 through the annular oil groove 203-connecting oil groove 204-oil passage hole 50 and is output to the front wheel lower pump through the second interface 102, driving the front wheel of the bicycle to increase the braking force. This realizes the automatic distribution of braking force to the front wheel lower pump and the rear wheel lower pump according to the preset pressure ratio, and ultimately achieves a reasonable distribution of the front and rear braking forces (in this embodiment, P1:P2 = Specifically, P1:P2 is the ratio of the braking force between the front and rear wheels, which is the ratio of the area of ​​the large and small ends of the first piston 601. In this example, the diameter of the large end of the first piston 601 is 12mm and the diameter of the small end is 10mm, so the braking force ratio between the front and rear wheels is 36 / 25=1.44, that is, the braking force distribution between the front and rear wheels is approximately 6:4. The braking distance can be significantly shortened, reducing the risk of the bicycle skidding.

[0103] Furthermore, when the first upper pump applies the brakes:

[0104] When the first preset oil pressure threshold Pb is reached, the positive braking pressure is the sum of the front wheel output pressure P1 and the rear wheel output pressure P2.

[0105] P1=P×Se

[0106] P2 = P × Se × (SC1 / SC2)

[0107] In the formula, Se is the piston area of ​​the rear wheel lower pump corresponding to the third interface 103 (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.

[0108] When the second preset oil pressure threshold Pc is reached, the positive braking pressure is the sum of the front wheel output pressure P1 and the rear wheel output pressure P2.

[0109] P1=P×Se

[0110] P2 = P × Se × (SC1 / SC2)

[0111] In the formula, the piston area of ​​the rear wheel pump corresponding to the third interface 103 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.

[0112] When the third preset oil pressure threshold Pc is reached, the positive braking pressure is the sum of the front wheel output pressure P1 and the rear wheel output pressure P2.

[0113] P1=P×Se

[0114] P2 = P × Se × (SC1 / SC2)

[0115] In the formula, Se is the piston area of ​​the rear wheel pump corresponding to the third interface 103 (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.

[0116] In this embodiment, the first elastic element 504, the second elastic element 506, and the third elastic element 604 are all compression springs, and the opening force F1 of the first elastic element 504, the closing force F2 of the second elastic element 506, and the opening force F3 of the third elastic element 604 can all be pre-selected by calculating the hydraulic output.

[0117] P=4F / πd 2

[0118] In the formula, P is the piston opening pressure, F is the elastic force of the elastic element, d is the diameter of the pressure end face of the first piston 503, and the diameter difference between the pressure end faces of the second piston 507 and the third piston 601.

[0119] In summary, the linkage hydraulic distribution valve provided in this embodiment of the invention achieves the following: when the first interface 101 is input, the second interface 102 initially outputs, and the front wheel lower pump operates, firstly applying slight braking to the front wheel to shift the center of gravity backward; secondly, the second interface 102 and the third interface 103 simultaneously output, controlling the front wheel lower pump and the rear wheel lower pump to operate simultaneously, maintaining braking balance; then, the braking force is increased, and the rear wheel lower pump increases the braking force on the rear wheel 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 a preset pressure threshold ratio, realizing reasonable coordination 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 simpler, more efficient and more accurate, and the braking distance can be significantly shortened, reducing the risk of bicycle tail-swing. Moreover, this application achieves synchronous linkage braking of the front and rear wheels without changing the overall braking structure of the bicycle and maximizing cost reduction.

[0120] In an optional embodiment, a fourth interface 104 radially opened on the housing 10 is also connected through the side wall of the rear cavity 1062. When oil is input into the fourth interface 104, it can be directly output through the third interface 103 to brake the rear wheel separately.

[0121] Example 2

[0122] Embodiment 2 of this application provides a linkage hydraulic distribution valve, which differs from the linkage hydraulic distribution valve of Embodiment 1 above in that FIG8 is a perspective view of a hydraulic pressure balancing linkage valve according to another exemplary embodiment. FIG9 is a second perspective view of a hydraulic pressure balancing linkage valve according to another exemplary embodiment. FIG10 is a top view of a hydraulic pressure balancing linkage valve according to another exemplary embodiment. FIG11 is a cross-sectional view of structure AA in FIG10. FIG12 is a cross-sectional view of structure BB in FIG10. FIG13 is a cross-sectional view of the housing according to structure AA in FIG10. FIG14 is a cross-sectional view of the housing according to structure BB in FIG10. Referring to FIG8-FIG14, the linkage hydraulic distribution valve further includes:

[0123] An oil sump cavity 100 is formed in the middle of the housing 10, and the oil sump cavity 100 is connected to the second oil cavity 106 through an oil replenishment channel 109;

[0124] The oil replenishing piston 70 is movably disposed within the oil sump cavity 100; wherein, the oil replenishing piston 70 replenishes brake fluid into the second oil cavity 106 during braking action to balance the brake fluid pressure.

[0125] Referring again to Figures 4-7, in this embodiment, the oil replenishing piston component 70 includes:

[0126] The limiting step 701 is integrally formed in the oil tank cavity 100 at the position corresponding to the oil replenishment channel 109;

[0127] The piston body 702 is movably assembled in the oil sump cavity 100 and moves within the oil sump cavity 100 with the movement of the oil to adaptively adjust the capacity of the oil sump cavity 100.

[0128] The oil tank cover 703 is positioned at the first end of the oil tank cavity 100, and the oil tank cover 703 is provided with a pressure balance hole that connects to the external atmospheric pressure.

[0129] More specifically, Figure 15 is a perspective view of the oil replenishing piston according to another exemplary embodiment. Referring to Figures 11-15, an assembly step is also provided on the inner wall of the first end of the oil sump cavity 100, and a cotter pin 704 is provided on the side of the oil sump cover 703 away from the oil sump cavity 100. The cotter pin 704 is engaged with the opening at the second end of the oil sump cavity 100 to cooperate with the assembly step to position the axial position of the oil sump cover 703; the oil replenishing piston 70 replenishes brake fluid into the second oil chamber 106 during braking action to balance the brake fluid pressure.

[0130] Other undescribed structures are described in Example 1.

[0131] In the above embodiment, referring to Figures 7-15, in the initial state, the piston body 702 is in the oil sump cavity 100 near the opening end of the oil sump cavity 100 and its stroke is limited by the oil sump cover 703. As the brake pads wear, during the braking process, the brake fluid in the oil sump cavity 100 is automatically replenished to the second oil chamber 106 with reduced pressure through the replenishment channel 109. The piston body 702 moves in the direction of brake fluid output, thereby maintaining sufficient oil in the braking system for braking.

[0132] In summary, this application, through the assembly of the oil replenishing piston 70 and the oil sump chamber 100 on the linkage valve, enables the oil pressure balancing linkage valve to automatically replenish the brake fluid in the oil sump chamber 100 to the cylinder chamber 101 with reduced pressure during braking as the brake pads wear. The piston body 702 moves in the direction of brake fluid output, thereby maintaining sufficient oil in the braking system for braking. Furthermore, this application achieves synchronous linkage braking of the front and rear wheels and maintains stable vehicle braking performance without altering the overall braking structure of the bicycle and maximizing cost reduction.

[0133] Example 3

[0134] Embodiment 3 of this application provides a brake linkage system, including the linkage hydraulic distribution valve of Embodiment 1 described above, and

[0135] The first upper pump is connected to the first interface 101 via the first oil pipe;

[0136] The front wheel lower pump is connected to the second interface 102 via a second oil pipe;

[0137] The rear wheel lower pump is connected to the third interface 103 via a third oil pipe;

[0138] When the first upper pump brakes, the linkage hydraulic distribution valve automatically distributes the oil output to the front wheel lower pump and the rear wheel lower pump according to the oil pressure change of the oil input through the first interface 101 to balance the braking; when the second upper pump brakes, the linkage hydraulic distribution valve distributes the oil input through the third interface 103 to the rear wheel lower pump for braking.

[0139] Other undescribed structures are described in Example 1.

[0140] In summary, the linkage hydraulic distribution valve and brake linkage system provided in this embodiment of the invention enables the independent operation of the first upper pump during braking. Initially, the front wheel lower pump operates, slightly braking the front wheel to shift the center of gravity backward. Next, the front wheel lower pump and the rear wheel lower pump are controlled to operate simultaneously to maintain braking balance. Then, the braking force is increased, with the rear wheel lower pump increasing the braking force on the rear wheel 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 a preset pressure threshold ratio. This achieves reasonable coordination of braking between the front and rear brakes by a single upper pump. Compared with manual braking, the braking force distribution is simpler, more efficient, and more precise, and the braking distance can be significantly shortened, reducing the risk of bicycle skidding. At the same time, it achieves synchronous linkage braking of the front and rear wheels without changing the overall braking structure of the bicycle and maximizing cost reduction.

[0141] Example 4

[0142] Embodiment 4 of this application provides a brake linkage system, including the linkage hydraulic distribution valve of Embodiment 2 described above, and

[0143] The first upper pump is connected to the first interface 101 via the first oil pipe;

[0144] The front wheel lower pump is connected to the second interface 102 via a second oil pipe;

[0145] The rear wheel lower pump is connected to the third interface 103 via a third oil pipe;

[0146] The second upper pump is connected to the fourth interface 104 via the fourth oil pipe;

[0147] When the first upper pump brakes, the linkage hydraulic distribution valve automatically distributes the oil output to the front wheel lower pump and the rear wheel lower pump according to the oil pressure change of the oil input through the first interface 101 to balance the braking; when the second upper pump brakes, the linkage hydraulic distribution valve distributes the oil input through the third interface 103 to the rear wheel lower pump for braking; when the second upper pump brakes, the linkage hydraulic distribution valve distributes the oil input through the fourth interface 104 to the rear wheel lower pump for braking.

[0148] Other undescribed structures are described in Example 2.

[0149] In this embodiment, when the second upper pump is driven to brake, the oil input from the fourth interface 104 reaches the third interface 103 through the rear chamber 1062 and is output to the rear wheel lower pump to drive the rear wheel brakes independently. The input pressure of the second upper pump corresponding to the fourth interface 104 is P3; when the second upper pump brakes, its positive braking pressure is only the rear wheel output pressure P2.

[0150] P2 = P3 × Se

[0151] In the formula, P2 is the rear wheel output pressure, P3 is the second upper pump input pressure, and Se is the piston area of ​​the rear wheel lower pump corresponding to the third interface 103, which is not shown in the figure;

[0152] In summary, the linkage hydraulic distribution valve and brake linkage system provided in this embodiment of the invention realizes that the second upper pump can be operated independently during braking. The oil input from the fourth interface 104 reaches the third interface 103 through the rear chamber 1062 and is output to the rear wheel lower pump. It can drive the rear wheel brake of the vehicle independently. Under the premise of not changing the overall braking structure of the bicycle and minimizing costs, the front and rear wheels can be braked synchronously and the vehicle's braking performance can be maintained stably.

[0153] Example 5

[0154] Embodiment 5 of this application provides a two-wheeled vehicle including the braking linkage system of Embodiment 3 or 4 described above. The two-wheeled vehicle in this embodiment is not limited to bicycles or electric bicycles, but can also be extended to vehicles with dual-path braking systems, such as motorcycles.

[0155] Other undescribed structures are described in Example 1.

[0156] In summary, the linkage hydraulic distribution valve, brake linkage system, and two-wheeled vehicle provided by the embodiments of the present invention enable the independent operation of the first upper pump during braking. Initially, the front wheel lower pump operates, slightly braking the front wheel to shift the center of gravity backward. Next, the front wheel lower pump and the rear wheel lower pump are controlled to operate simultaneously to maintain braking balance. Then, the braking force is increased, with the rear wheel lower pump increasing the braking force on the rear wheel 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 a preset pressure threshold ratio. This achieves reasonable coordination of braking between the front and rear brakes by a single upper pump. Compared with manual braking, the braking force distribution is simpler, more efficient, and more precise, and the braking distance can be significantly shortened, reducing the risk of bicycle skidding. At the same time, it achieves synchronous linkage braking of the front and rear wheels without changing the overall braking structure of the bicycle and maximizing cost reduction.

[0157] The technical features of the above embodiments can be combined in any way. For the sake of brevity, 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, they should be considered to be within the scope of this specification.

[0158] The above embodiments merely illustrate several implementation methods of this application, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the invention patent. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this application, and these all fall within the protection scope of this application. Therefore, the protection scope of this patent application should be determined by the appended claims.

Claims

1. A linked hydraulic distribution valve for use with a vehicle frame, characterized by, include: The housing has a first oil cavity, a second oil cavity, and an oil cavity channel connecting the first end of the first oil cavity and the first end of the second oil cavity in its middle part. The first oil cavity has a first interface and a second interface that are radially opened on the housing through the side wall near its first end. The second oil cavity has a third interface that is radially opened on the housing through the side wall near its second end. A combined piston assembly is movably disposed within the first oil chamber; A single piston component is movably disposed within the second oil chamber; The combined piston assembly and the single piston assembly automatically distribute the brake fluid input from the first interface to the second and third interfaces to balance braking.

2. The linked hydraulic pressure distribution valve according to claim 1, wherein: The combined piston assembly includes: An annular step is integrally formed in the first oil cavity at the position corresponding to the second interface and divides the inner end of the second interface into a first branch and a second branch. The inner walls of the annular step are recessed inward on both sides and form a first slope and a second slope. The first piston is movably disposed in the first oil chamber on one side near the first slope surface, and its first end is formed with a first facet surface that cooperates with the first slope surface, so that when the oil pressure reaches the third preset oil pressure threshold, it leaves the first slope surface and opens the second branch. A first elastic element is disposed in the first oil cavity and located between the second end of the first piston and the second end of the first oil cavity, so as to elastically maintain the first platform surface abutting the first slope surface and close the second branch. The second piston is movably disposed in the first oil chamber on one side near the second slope surface. It has an oil passage hole in its axial middle part that connects to the first interface, and its second end is formed with a second platform surface that cooperates with the second slope surface so that it abuts against the second slope surface and closes the first branch when the oil pressure reaches the second preset oil pressure threshold. The second elastic element is disposed in the first oil cavity and located between the first end of the first piston and the second end of the second piston to elastically maintain the second platform surface away from the first slope surface and open the second branch.

3. The linked hydraulic pressure distribution valve according to claim 2, wherein: The first end of the first oil chamber is an open structure and is threaded with a first screw cap, the inner end of the first screw cap abutting the first end of the second piston; The first screw cap includes: A screw cap body, which is threadedly assembled with the first end of the first oil cavity; The positioning boss is integrally formed on the inner end of the screw cap and abuts against the first end of the second piston. Its diameter is smaller than the inner diameter of the first oil cavity and an annular oil groove is formed between the inner wall of the first oil cavity and the first interface and the oil cavity channel. A connecting oil hole is provided on the side of the positioning boss near the second piston, and its two ends are respectively connected to the first interface and the annular oil groove.

4. The linked hydraulic pressure distribution valve according to claim 1, wherein: The single piston component includes: A stepped portion is formed within the second oil cavity and divides the second oil cavity into a front cavity that connects to the oil cavity channel, and a rear cavity that connects to the third interface, wherein the inner diameter of the front cavity is smaller than the inner diameter of the rear cavity; A third piston, a first section of which is movably arranged in the front cavity, and a second section of which is movably arranged in the rear cavity, the third piston being displaced to the rear cavity when the oil pressure reaches a first preset oil pressure threshold; A third elastic member arranged in the rear cavity and abutting against a free end of the second section of the third piston and a second end of the second oil cavity respectively, to elastically maintain the third piston limited at the step portion; A piston sleeve fixedly sleeved on an annular side wall of the second section of the third piston.

5. The linked hydraulic pressure distribution valve according to claim 1, wherein: A sealing ring is arranged on the active contact surface of the first oil cavity and the active contact surface of the second oil cavity.

6. The linked hydraulic pressure distribution valve according to claim 1, wherein: Further comprising: An oil pool cavity opened in the middle of the housing, and the oil pool cavity being communicated with the second oil cavity through an oil supplement channel; An oil supplement piston movably arranged in the oil pool cavity; The oil supplement piston supplements brake oil into the second oil cavity to balance the brake oil pressure when the brake is operated.

7. The linked hydraulic pressure distribution valve according to claim 6, wherein: The oil supplement piston comprises: A limiting step integrally formed in the oil pool cavity at a position corresponding to the oil supplement channel; A piston body movably arranged in the oil pool cavity and moving in the oil pool cavity along with the movement of the oil, to adaptively adjust the capacity of the oil pool cavity; An oil pool cover limitingly arranged at a first end of the oil pool cavity, and the oil pool cover being provided with an air pressure balance hole communicated with the external atmospheric pressure.

8. The linked hydraulic pressure distribution valve according to claim 7, wherein: An assembly step is further opened in an inner wall of the first end of the oil pool cavity, and the oil pool cover is provided with an open pin on a side away from the oil pool cavity, the open pin being clamped at an opening of the second end of the oil pool cavity to position the axial position of the oil pool cover in cooperation with the assembly step.

9. The linked hydraulic pressure distribution valve according to claim 4, wherein: A fourth interface radially opened on the housing is further connected through the side wall of the rear cavity.

10. A brake linkage system characterized by, The linkage hydraulic distribution valve comprises the linkage hydraulic distribution valve according to any one of claims 1-9, and A first upper pump communicated with the first interface through a first oil pipe; A front wheel lower pump communicated with the second interface through a second oil pipe; A rear wheel lower pump communicated with the third interface through a third oil pipe; When the first upper pump is braked, the linkage hydraulic distribution valve automatically distributes the oil output to the front wheel lower pump and the rear wheel lower pump according to the change of the oil pressure of the oil input into the first interface to balance the brake.

11. A two-wheeled vehicle characterized by The brake linkage system comprises the brake linkage system according to claim 10.

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