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

Abstract

This invention relates to a linked hydraulic distribution valve, a brake linkage system, and a two-wheeled vehicle. The system includes: a housing with a first oil chamber, a second oil chamber, and an oil chamber channel connecting a first end of the first oil chamber and a first end of the second oil chamber; a first interface and a second interface radially formed on the housing are connected through the side wall of the first oil chamber near its first end; a third interface radially formed on the housing is connected through the side wall of the second oil chamber near its second end; a combined piston assembly movably disposed within the first oil chamber; and a single piston assembly movably disposed within the second oil chamber. The combined piston assembly and the single piston assembly automatically distribute brake fluid input through the first interface to the second and third interfaces to balance braking. This invention achieves efficient coordination of the front and rear brakes of a bicycle using a single upper pump, significantly shortening the braking distance and reducing the risk of bicycle skidding.

Description

[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. [Previous Technology]

[0002] 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 of their hands to ensure that the front and rear tires fully utilize the road surface's coefficient of friction. However, in actual riding, this is difficult for riders to do. Furthermore, 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 speed, if only the front wheel is braked, the vehicle's center of gravity becomes unstable, 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.

[0004] In view of this, we, the inventors, devoted ourselves to further research and development and improvement, hoping to solve the above problems with a better invention. After continuous experimentation and modification, this invention came into being. [Summary of the Invention]

[0005] The present invention provides a linkage hydraulic distribution valve, a brake linkage system and a two-wheeled vehicle, so as to at least solve the problem that in the prior art, when only the front wheels are braked, the center of gravity of the vehicle is unstable and there may be a risk of fishtailing.

[0006] In a first aspect, the present invention provides a linkage hydraulic distribution valve, which is used in conjunction with a vehicle frame, comprising:

[0007] A housing, wherein a first oil cavity and a second oil cavity are provided in the middle, and an oil cavity channel is provided to connect the first end of the first oil cavity and the first end of the second oil cavity. A first interface and a second interface are radially opened on the housing and are connected through the side wall of the first oil cavity near its first end. A third interface and a third interface are radially opened on the housing and are connected through the side wall of the second oil cavity near its second end.

[0008] A combined piston assembly, which is movably disposed within the first oil chamber;

[0009] A single piston component, which is movably disposed within the second oil chamber;

[0010] Wherein, the combined piston assembly and the single piston assembly automatically distribute the brake fluid input from the first interface to the second interface and the third interface to balance braking.

[0011] Optionally, the combined piston assembly includes:

[0012] An annular step, integrally formed in the first oil cavity at the position corresponding to the second interface and dividing the inner end of the second interface into a first branch and a second branch, wherein both sides of the inner wall of the annular step are recessed inward and form a first slope and a second slope.

[0013] A 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 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.

[0014] A first elastic member 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.

[0015] 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 the middle of its axial direction 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 when the oil pressure reaches the second preset oil pressure threshold, it abuts against the second slope surface and closes the first branch.

[0016] A 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.

[0017] 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;

[0018] Wherein, the first screw cap includes:

[0019] A screw cap body, which is threadedly assembled with the first end of the first oil cavity;

[0020] The positioning boss is integrally formed on 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 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.

[0021] 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.

[0022] Optionally, the single piston component includes:

[0023] A stepped portion, which is formed in 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;

[0024] 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.

[0025] A third elastic member 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;

[0026] A piston sleeve, which is fixedly sleeved on the annular sidewall of the second section of the third piston.

[0027] Optionally, a sealing ring is fitted on the movable contact surface between the combined piston and the first oil chamber, and on the movable contact surface between the single piston and the second oil chamber.

[0028] Optionally, it also includes:

[0029] 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;

[0030] An oil replenishing piston component, which is movably disposed within the oil sump cavity;

[0031] Wherein, the oil replenishing piston replenishes brake fluid into the second oil chamber during braking action to balance the brake fluid pressure.

[0032] Optionally, the oil replenishing piston component includes:

[0033] A limiting step, integrally formed in the oil tank cavity at the position corresponding to the oil replenishment channel;

[0034] A piston body is movably assembled in the oil sump cavity and moves in the oil sump cavity with the movement of the oil to adaptively adjust the capacity of the oil sump cavity;

[0035] An oil tank cover, which is limited and fitted at the first end of the oil tank cavity, and the oil tank cover is provided with a pressure balance hole that connects to the external atmospheric pressure.

[0036] 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.

[0037] Optionally, a fourth interface radially opened on the housing is also connected through the side wall of the rear cavity.

[0038] In a second aspect, the present invention provides a brake linkage system, comprising the linkage hydraulic distribution valve described in the first aspect, and

[0039] A first upper pump is connected to the first interface via a first oil pipe;

[0040] The front wheel lower pump is connected to the second interface via a second oil pipe;

[0041] The rear wheel under-pump is connected to the third interface via a third oil pipe;

[0042] Wherein, 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.

[0043] In a third aspect, the present invention provides a braking linkage system, including the braking linkage system described in the second aspect above.

[0044] Compared with related technologies, the linkage hydraulic distribution valve, brake linkage system and two-wheeled vehicle provided by the present invention have at least the following technical effects:

[0045] When braking, the first upper pump is operated independently. Initially, the front wheel lower pump works, first applying slight braking to the front wheel to shift the center of gravity backward. Then, the front wheel lower pump and the rear wheel lower pump 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 wheel lower pump and the rear wheel lower pump according to the preset pressure threshold ratio. This achieves 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. 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.

[0046] Details of one or more embodiments of the present invention are set forth in the following figures and description to make other features, objects and advantages of the invention more readily apparent.

Implementation Method

[0048] Regarding the technical means of us inventors, several preferred embodiments are described in detail below with reference to the drawings, so that you may understand and agree with the present invention.

[0049] The technical solution of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without making any progressive efforts are within the scope of protection of the present invention.

[0050] 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 drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention. In addition, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0051] 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. For those skilled in the art, the specific meaning of the above terms in this invention can be understood according to the specific circumstances.

[0052] 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 do. Furthermore, because the rear wheel bears most of the vehicle's weight during normal riding or acceleration, it experiences greater friction than the front wheel. However, during braking, due to inertia, the vehicle's center of gravity shifts to the front wheel. In high-speed riding requiring emergency braking, if only the front wheel is braked, the vehicle's center of gravity becomes unstable, potentially leading to a fishtailing risk.

[0053] Based on the above, the present invention provides 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 figures.

[0054] Example 1

[0055] This embodiment of the 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 cross-sectional view of the linkage hydraulic distribution valve according to an exemplary embodiment. As shown in Figures 1 to 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 and mounting 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.

[0056] FIG4 is a axial sectional view of the housing according to an exemplary embodiment. Referring to FIGS. 1-4, the linked hydraulic distribution valve includes:

[0057] 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 to 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.

[0058] A combined piston component 50 is movably disposed within the first oil chamber 105;

[0059] FIG5 is a perspective view of the combined structure of the combined piston and the single piston according to an exemplary embodiment. FIG6 is an exploded view of the combined structure of the combined piston and the single piston according to an exemplary embodiment. Referring to FIG5-FIG6, in some embodiments, the combined piston 50 includes: an annular step 501, which is integrally formed in the first oil cavity 105 at the 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;

[0060] 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 assembled on the annular sidewall of the first piston 503.

[0061] 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 FIG3, 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;

[0062] The second piston 507 is movably disposed in the first oil chamber 105 on one side near the second slope surface 5022. An oil passage hole 509 communicating with the first interface 101 is opened in the middle of its axial direction, and a second surface 508 is formed at its second end to cooperate with the second slope surface 5022, so as to abut against the second slope surface 5022 and close the first branch 1021 when the oil pressure reaches the first preset oil pressure threshold. A sealing ring 40 is also installed on the annular side wall of the second piston 507.

[0063] The second elastic member 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 member 506 is a compression spring. Further, referring to FIG3, 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 member 506 and maintain the second elastic member 506 from deformation when it undergoes axial deformation;

[0064] A single piston component 60 is movably disposed within the second oil chamber 106;

[0065] Continuing to refer 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;

[0066] 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 sidewall of the first section of the third piston 601.

[0067] The third elastic member 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 member 604 is a compression spring. Further, referring to FIG3, 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 member 604 and maintain the third elastic member 604 from deformation when it undergoes axial deformation;

[0068] Piston sleeve 603, which is fixedly sleeved on the annular sidewall of the second section of the third piston 601.

[0069] 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.

[0070] In the above embodiment, under the scenario of ensuring a clean assembly environment, the first piston 503 and the first elastic member 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 member 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 end of the first oil chamber 105 and the second oil chamber 106, respectively. The second elastic member 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. This completes the rapid assembly of the linkage hydraulic distribution valve in this embodiment.

[0071] 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 connected sequentially 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 to correspond to the rear wheel brake, and the front wheel lower pump is controlled by the left handbrake to correspond to the front wheel brake. When the first upper pump (left handbrake) is squeezed to brake, 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 of braking oil pressure to balance the braking.

[0072] Referring again to FIG6, in some embodiments, the first screw cap 20 includes:

[0073] Screw cap body 201, which is threadedly assembled with the first end of the first oil cavity 105;

[0074] 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 connecting the first interface 101 and the oil cavity channel 107 is formed between the inner wall of the first oil cavity 105.

[0075] 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.

[0076] In an optional embodiment, FIG7 shows a perspective view of the first screw cap according to an optional 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 the present invention, and is only provided as an optional alternative for illustrative purposes.

[0077] In the technical solution of the above embodiment, during braking, referring to FIG3, 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; 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.

[0078] 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;

[0079] When the first upper pump is driven for braking:

[0080] S1, When the first upper pump input pressure P is first braked, its initial oil pressure Pa, 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, and 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;

[0081] 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, and at the same time closes the third interface 103, it presses the oil in the rear chamber 1062 into the third interface 103 and outputs 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.

[0082] 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, and maintains 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, which drives the rear wheel braking force of the bicycle to increase.

[0083] S4. When the input pressure P of the first upper pump reaches the third preset oil pressure threshold Pd, the first oil 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 drives the rear wheel braking force of the bicycle to continue to increase. At the same time, the second oil 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 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. The braking force is automatically distributed to the front wheel lower pump and the rear wheel lower pump according to the preset pressure ratio, so as to achieve 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.

[0084] Furthermore, when the first upper pump applies the brakes:

[0085] When the first preset oil pressure threshold Pb is reached, its positive braking pressure is the front wheel output pressure P1 + the rear wheel output pressure P2:

[0086] P1=P×Se [Equation 1]

[0087] P2=P×Se×(SC1 / SC2) [Equation 2]

[0088] In

Equation 1

Equation 2

[0089] When the second preset oil pressure threshold Pc is reached, its positive braking pressure is the front wheel output pressure P1 + the rear wheel output pressure P2:

[0090] P1=P×Se [Equation 3]

[0091] P2=P×Se×(SC1 / SC2) [Equation 4]

[0092] In

Equation 3

Equation 4

[0093] When the third preset oil pressure threshold Pc is reached, its positive braking pressure is the front wheel output pressure P1 + the rear wheel output pressure P2:

[0094] P1=P×Se [Equation 5]

[0095] P2=P×Se×(SC1 / SC2) [Equation 6]

[0096] In Equations 5 and 6, Se is the piston area of ​​the rear wheel pump corresponding to the third interface 103, 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.

[0097] 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.

[0098] P=4F / πd2 [Equation 7]

[0099] [Equation 7] In this equation, 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.

[0100] In summary, the linkage hydraulic distribution valve provided in this embodiment of the invention realizes that when the first interface 101 is input, the second interface 102 is initially output, and the front wheel lower pump works, first slightly braking the front wheel and shifting the center of gravity backward; then the second interface 102 and the third interface 103 output simultaneously, controlling the front wheel lower pump and the rear wheel lower pump to work simultaneously to maintain braking balance; then the braking force is increased again, and the rear wheel lower pump increases the braking force on the rear wheel 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 the 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 invention achieves synchronous linkage braking of the front and rear wheels without changing the overall braking structure of the bicycle and maximizing cost reduction.

[0101] 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.

[0102] Example 2

[0103] Embodiment 2 of the present invention 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 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 FIG8-14, the linkage hydraulic distribution valve further includes:

[0104] 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;

[0105] A replenishing piston 70 is movably disposed within the oil sump cavity 100; wherein, the replenishing piston 70 replenishes brake fluid into the second oil cavity 106 during braking action to balance the brake fluid pressure.

[0106] Continuing to refer to Figures 4-7, in this embodiment, the oil replenishing piston component 70 includes:

[0107] Limiting step 701, which is integrally formed in the oil tank cavity 100 at the position corresponding to the oil replenishment channel 109;

[0108] The piston body 702 is movably assembled in the oil sump cavity 100 and moves in the oil sump cavity 100 with the movement of the oil to adaptively adjust the capacity of the oil sump cavity 100.

[0109] The oil tank cover 703 is limited and assembled at the first end of the oil tank cavity 100, and the oil tank cover 703 is provided with an air pressure balance hole that connects to the external atmospheric pressure.

[0110] More specifically, FIG15 is a perspective view of the oil replenishing piston according to another exemplary embodiment. Referring to FIG11-FIG15, 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.

[0111] For other undescribed structures, refer to Example 1.

[0112] In the above embodiment, referring to Figures 7 to 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.

[0113] In summary, by assembling the oil replenishing piston 70 and the oil sump 100 on the linkage valve, the oil pressure balancing linkage valve automatically replenishes the brake fluid in the oil sump 100 to the cylinder 101 with reduced pressure during braking as the brake pads wear. The piston 702 moves in the direction of brake fluid output, thereby maintaining sufficient oil in the braking system for braking. Furthermore, the present invention 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.

[0114] Example 3

[0115] Embodiment 3 of the present invention provides a brake linkage system, including the linkage hydraulic distribution valve of Embodiment 1 above, and

[0116] The first upper pump is connected to the first interface 101 via the first oil pipe;

[0117] The front wheel lower pump is connected to the second interface 102 via the second oil pipe;

[0118] The rear wheel lower pump is connected to the third interface 103 via the third oil pipe;

[0119] 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 101 to balance the braking; when the second upper pump brakes, the linkage hydraulic distribution valve distributes the oil input at the third interface 103 to the rear wheel lower pump to brake.

[0120] Other undescribed structures refer to Example 1.

[0121] In summary, the linkage hydraulic distribution valve and brake linkage system provided in this embodiment of the invention realizes that the first upper pump can be operated independently during braking. Initially, the front wheel lower pump works to slightly brake the front wheel and shift the center of gravity backward. Then, the front wheel lower pump and the rear wheel lower pump are controlled to work simultaneously to maintain braking balance. Next, 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 the preset pressure threshold ratio. This realizes 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. At the same time, it realizes synchronous linkage braking of the front and rear wheels without changing the overall braking structure of the bicycle and maximizing cost reduction.

[0122] Example 4

[0123] Embodiment 4 of the present invention provides a brake linkage system, including the linkage hydraulic distribution valve of Embodiment 2 above, and

[0124] The first upper pump is connected to the first interface 101 via the first oil pipe;

[0125] The front wheel lower pump is connected to the second interface 102 via a second oil pipe;

[0126] The rear wheel lower pump is connected to the third interface 103 via the third oil pipe;

[0127] The second upper pump is connected to the fourth interface 104 via the fourth oil pipe;

[0128] 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 101 to balance the braking; when the second upper pump brakes, the linkage hydraulic distribution valve distributes the oil input at 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 at the fourth interface 104 to the rear wheel lower pump for braking.

[0129] Other undescribed structures refer to Example 2.

[0130] 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 brake of the vehicle 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.

[0131] P2=P3×Se [Equation 8]

[0132] [Equation 8] In this equation, 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;

[0133] In summary, the linkage hydraulic distribution valve and brake linkage system provided in the embodiments of the present 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 braking performance can be maintained stably.

[0134] Example 5

[0135] Embodiment 5 of the present invention 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 braking systems such as motorcycles.

[0136] Other undescribed structures refer to Example 1.

[0137] In summary, the linkage hydraulic distribution valve, brake linkage system, and two-wheeled vehicle provided in this embodiment of the invention realize the independent operation of the first upper pump during braking. Initially, the front wheel lower pump works to slightly brake the front wheel and shift the center of gravity backward. Then, the front wheel lower pump and the rear wheel lower pump are controlled to work simultaneously to maintain braking balance. Next, 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 the preset pressure threshold ratio. This realizes 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. At the same time, it realizes synchronous linkage braking of the front and rear wheels without changing the overall braking structure of the bicycle and maximizing cost reduction.

[0138] In summary, the technical means disclosed in this invention can effectively solve the problems of the prior art and achieve the expected purpose and effect. Moreover, it has not been published or publicly used before the application and has long-term progressiveness. It is indeed an invention as defined by the Patent Law. Therefore, this application is filed in accordance with the law. I earnestly request Your Excellency to give a detailed review and grant me an invention patent. I am deeply grateful for Your Excellency's kindness.

[0139] However, the above description is only a few preferred embodiments of the present invention and should not be construed as limiting the scope of the present invention. All equivalent changes and modifications made in accordance with the scope of the patent application and the contents of the specification of the present invention should still fall within the scope of the patent of the present invention. [Simplified Explanation of the Diagram]

[0047] In order to more clearly illustrate the technical solutions in the specific embodiments of the present invention or 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 who are skilled in the art, other drawings can be obtained from these drawings without making any progress. [Fig. 1] is a perspective view of a linkage hydraulic distribution valve according to an exemplary embodiment; [Fig. 2] is a front view of a linkage hydraulic distribution valve according to an exemplary embodiment; [Fig. 3] is a planar sectional view of a linkage hydraulic distribution valve according to an exemplary embodiment; [Fig. 4] is an axial sectional view of a housing according to an exemplary embodiment; [Fig. 5] is a perspective view of a combined structure of a combined piston and a single piston according to an exemplary embodiment; [Fig. 6] is an exploded view of a combined structure of a combined piston and a single piston according to an exemplary embodiment; [Fig. 7] is a perspective view of a first screw cap according to an alternative embodiment; [Fig. 8] is one of the perspective views of a hydraulic pressure balancing linkage valve according to another exemplary embodiment; [Fig. 9] is another perspective view of a hydraulic pressure balancing linkage valve according to another exemplary embodiment; [Fig. 10] is a top view of a hydraulic pressure balancing linkage valve according to another exemplary embodiment; [Fig. 11] is a sectional view of structure AA in Fig. 10; [Fig. 12] is a sectional view of structure BB in Fig. 10; [Fig. 13] is a sectional view of the housing according to structure AA in Fig. 10; [Fig. 14] is a cross-sectional view of the housing according to the BB structure in Fig. 10; [Fig. 15] is a perspective view of the oil replenishing piston according to another exemplary embodiment.

Claims

1. A linkage hydraulic distribution valve, used in conjunction with a vehicle frame, characterized in that it comprises: The housing includes a first oil chamber, a second oil chamber, and an oil chamber channel connecting the first end of the first oil chamber and the first end of the second oil chamber. The first oil chamber has a first interface and a second interface radially formed on the housing, which are connected through the side wall near its first end. The second oil chamber has a third interface radially formed on the housing, which is connected through the side wall near its second end. A combined piston assembly is movably disposed within the first oil chamber. A single piston assembly is movably disposed within the second oil chamber. The combined piston assembly and the single piston assembly automatically distribute and output brake fluid input from the first interface to the second interface and the third interface to balance braking. The housing also includes: an oil sump located in the middle of the housing, which is connected to the second oil chamber via a replenishment channel; and a replenishment piston assembly movably disposed within the oil sump. The replenishment piston assembly replenishes brake fluid to the second oil chamber during braking to balance the brake fluid pressure.

2. The linkage hydraulic distribution valve as described in claim 1, characterized in that: the combined piston assembly comprises: An annular step, integrally formed within the first oil cavity at the position corresponding to the second interface, 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, forming a first slope and a second slope. A first piston, movably disposed within the first oil cavity near the first slope, has a first facet formed at its first end that mates with the first slope, so that it disengages from the first slope and opens the second branch when the oil pressure reaches a third preset oil pressure threshold. A first elastic member, disposed within the first oil cavity and located between the second end of the first piston and the second end of the first oil cavity, elastically maintains the first facet against the first slope and closes the second branch. The second piston is movably disposed within the first oil chamber on one side near the second slope surface. It has an oil passage hole in its axial center that connects to the first interface, and its second end is formed with a second facet that mates with the second slope surface. When the oil pressure reaches a second preset oil pressure threshold, it abuts against the second slope surface and closes the first branch. The second elastic member is disposed within the first oil chamber and located between the first end of the first piston and the second end of the second piston. It elastically maintains the second facet away from the first slope surface and opens the second branch.

3. The linkage hydraulic distribution valve as described in claim 2, characterized in that: the first end of the first oil chamber is an open structure and is threadedly fitted with a first screw cap, the inner end of the first screw cap abutting against the first end of the second piston; wherein, The first screw cap includes: a screw cap body, which is threadedly assembled with the first end of the first oil cavity; a positioning boss, which is integrally formed on the inner end of the screw cap body and abuts against the first end of the second piston, the diameter of which is smaller than the inner diameter of the first oil cavity and forms an annular oil groove between the boss and the inner wall of the first oil cavity, connecting the first interface and the oil cavity channel; and a communicating oil hole, which is opened 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 linkage hydraulic distribution valve as described in claim 1, characterized in that: the individual piston component comprises: A stepped portion, formed within the second oil cavity, divides the second oil cavity into a front cavity communicating with the oil cavity channel and a rear cavity communicating with the third interface, wherein the inner diameter of the front cavity is smaller than the inner diameter of the rear cavity; a third piston, the first section of which is movably assembled within the front cavity and the second section of which is movably assembled within the rear cavity, wherein the third piston displaces into the rear cavity when the oil pressure reaches a first preset oil pressure threshold; a third elastic member, disposed within the rear cavity and abutting against the free end of the second section of the third piston and the second end of the second oil cavity respectively, thereby elastically maintaining the third piston at the stepped portion; and a piston sleeve, fixedly sleeved on the annular sidewall of the second section of the third piston.

5. The linkage hydraulic distribution valve as described in claim 1, characterized in that: sealing rings are fitted on the movable contact surface between the combined piston member and the first oil chamber, and on the movable contact surface between the single piston member and the second oil chamber.

6. The linkage hydraulic distribution valve as described in claim 1, characterized in that: the oil replenishing piston comprises: A limiting step is integrally formed inside the oil sump cavity at the position corresponding to the oil replenishment channel; A piston body is movably assembled within the oil sump cavity and moves within the oil sump cavity with the movement of the oil to adaptively adjust the capacity of the oil sump cavity; an oil sump cover is limited and assembled at the first end of the oil sump cavity, and the oil sump cover has a pressure balance hole that connects to the external atmospheric pressure.

7. The linkage hydraulic distribution valve as described in claim 6, characterized in that: an assembly step is further provided on the inner wall of the first end of the oil sump cavity, and a cotter pin is provided on the side of the oil sump cover away from the oil sump cavity, the cotter pin being engaged with the opening at the second end of the oil sump cavity to cooperate with the assembly step in positioning the axial position of the oil sump cover.

8. The linkage hydraulic distribution valve as described in claim 4, characterized in that: a fourth interface radially opened on the housing is further connected through the side wall of the rear cavity.

9. A braking linkage system, characterized in that it comprises a linkage hydraulic distribution valve as described in any one of claims 1 to 8, a first upper pump connected to the first interface via a first oil pipe; a front wheel lower pump connected to the second interface via a second oil pipe; and a rear wheel lower pump connected to the third interface via a third oil pipe; wherein, 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.

10. A two-wheeled vehicle, characterized in that it includes a braking linkage system as described in claim 9.

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