TW202035200A - Proportion controllable combined braking system - Google Patents

Abstract

A proportion controllable combined braking system is disclosed and includes a linkage lever, a force inputting assembly, a first force outputting assembly, a second force outputting assembly and a proportion control mechanism. The linkage lever has a first end and a second end, which are opposed to each other. The force inputting assembly is pin-connected between the first end and the second end of the linkage lever. When an input force is provided through the force inputting assembly, the linkage lever is moved in a direction of the input force. The first force outputting assembly is connected with the first end of the linkage lever. The first force outputting assembly generates a first output force in response to the input force from the force inputting assembly. The second force outputting assembly is connected with the modulation mechanism. The proportion control mechanism is movably contacted with the second force outputting assembly or the second end of the linkage lever to generate a modulation force according to a control unit thereof. The second force outputting assembly generates a suitable second output force in response to the input force, the first output force and the modulation force.

Description

Proportionable brake linkage system

This case is about a brake system, especially a brake linkage system that can actively control the ratio.

The brake system is a braking system that slows down or stops the vehicle from moving forward, and stops by slowing the rotation of the vehicle's wheels. Traditional two-wheeled vehicles are limited by the movement of the two wheels. Once inadvertent inadvertent movement occurs during braking, in addition to greatly extending the braking distance, it may also cause the tires to completely lock up and side-slip, thereby causing the body to lose The accident of dumping due to balance seriously endangers the safety of the vehicle.

In order to enhance the safety of vehicle driving and prevent vehicle users from improperly operating the front and rear wheel brake systems, the current market has a brake system that integrates the front wheel brake force and the rear wheel brake force. The brake device of the front and rear wheels is activated at the same time through the action of a single handle. The front wheel braking force and the rear wheel braking force act on the front wheels and the rear wheels respectively in a fixed ratio.

However, since the effect of vehicle inertia forward will become more and more obvious as the braking force of the overall vehicle increases, if the fixed-ratio brake linkage system is not properly designed, it will not be able to stop the moving vehicle smoothly. For example, the initial braking force of the front wheels is too strong and locks up before the rear wheels, causing the vehicle to tip over during braking, or the braking force of the rear wheels is too strong, causing the tail to flick and the braking distance is too long.

In view of this, it is really necessary to provide a controllable proportional brake linkage system with a proportional control mechanism that can dynamically control the ratio of the front wheel brake force to the rear wheel brake force, and effectively integrate the front wheel brake force and the rear wheel brake force to match The vehicle's inertial forward movement effect provides front-wheel braking force and rear-wheel braking force with non-linear proportional changes, solving the problems faced by conventional technologies.

The purpose of this case is to provide a controllable proportional brake linkage system, which can generate sufficient braking force through a single handle operation to meet the deceleration of the regulations. Use proportional control mechanism to provide modulating force, dynamically control front wheel brake force and rear wheel brake force, ensure the correct distribution of front and rear wheel brake force, so that the proportional change of rear wheel brake force and front wheel brake force is in a non-linear relationship, and it is in braking In the program, keep the slip rate of the rear wheels greater than the slip rate of the front wheels in order to obtain comfortable performance, maximum deceleration and stability when the vehicle is braking.

Another purpose of this case is to provide a controllable proportional brake linkage system, which controls the front and rear wheel brake force ratio by pressing a single handle operation and a proportional control mechanism, so that the rear wheel brake mechanism brakes first. During emergency braking or braking on slippery roads, the rear wheels will lock up before the front wheels. If the rear wheel brake mechanism fails, such as disconnected or stuck, the proportional control mechanism can control the front wheels not to generate braking force. If the front wheel brake mechanism fails, the rear wheel can maintain sufficient braking force. Effectively integrate the front wheel braking force and the rear wheel braking force to match the vehicle inertia forward effect, providing a non-linear proportional change of the front wheel braking force and the rear wheel braking force

To achieve the foregoing objective, the present application provides a controllable proportional brake linkage system, which structure includes a connecting rod, an input component, a first output component, a second output component, and a proportional control mechanism. The connecting rod has a first end and a second end, and the first end and the second end are opposite to each other. The input force component is connected between the first end and the second end of the connecting rod, and is assembled to provide an input force, so that the connecting rod is displaced in the direction of the input force. The first output component is connected to the first end of the connecting rod and generates a first output force corresponding to the input force of the input component. A second output component is connected to the second end of the connecting rod. The proportional control mechanism is connected to the second end of the second output element or the connecting rod and provides a modulating force so that the second output element responds to the input force of the input element, the first output force of the first output element and the proportional control mechanism The modulating force produces a second output force.

In one embodiment, the ratio of the second output force to the first output force is non-linear, and at an early stage of braking or when the input force input by the user through the input force component is less than a specific value, it is ensured that the second output force is less than The first output force.

In one embodiment, the first output component and the second output component provide the first output force and the second output force to a first runner and a second runner, respectively, to perform a braking procedure, wherein the proportional control mechanism is more Connected to a controller, the controller is connected to a first wheel speed detector and a second wheel speed detector, the first wheel speed detector is configured to detect the first rotating speed of the first wheel, The two-wheel speed detector is configured to detect the second rotation speed of the second runner, wherein the controller calculates the first slip rate of the first runner according to the first rotation speed of the first runner and the second rotation speed of the second runner And the second slip rate of the second runner, and in response to the change relationship between the second slip rate of the second runner and the first slip rate of the first runner, the control command of the proportional control mechanism is controlled so that the proportional control mechanism provides adjustment Variable force.

In one embodiment, the proportional control mechanism keeps the first slip rate greater than the second slip rate during the braking procedure.

In one embodiment, the proportional controllable brake linkage system further includes a housing with an accommodating space, and the proportional control mechanism is disposed on the housing.

In an embodiment, the second output component has a force receiving part configured to receive the modulating force, wherein the proportional control mechanism includes a force rod, a power source, and a controller. The force rod is arranged in the shell and accommodated in the accommodating space to provide a modulating force and act on the force receiving portion of the second output component. The power source is arranged on the shell, and is slidably connected to the power rod to generate the modulating force with the power rod. The controller is electrically connected to the power source to control the power source, and the power rod generates the modulating force.

In one embodiment, the force rod has a first arm, a second arm, and a pivotal portion. The pivotal portion is pivotally connected to the housing, and the first arm and the second arm are located on both sides of the pivotal portion. One arm is slidably connected to the force receiving part of the second output component, and the second arm is slidably connected to the power source, wherein the power source abuts against the second arm of the force rod, and the force rod rotates around the pivotal part to drive the first arm Press against the force receiving part of the second output component.

In one embodiment, the power source includes a transmission member and a force application part, the transmission member is connected to the force application part, and the force application part is slidably connected to the second arm of the power rod.

In one embodiment, the first output component and the second output component are selected from one of the group consisting of a drum brake mechanism and a disc brake mechanism.

In one embodiment, the first output component and the second output component are a rear wheel brake mechanism and a front wheel brake mechanism, respectively.

Some typical embodiments embodying the features and advantages of this case will be described in detail in the following description. It should be understood that this case can have various changes in different aspects, all of which do not depart from the scope of the case, and the descriptions and drawings therein are essentially for illustrative purposes, not for limiting the case.

Figure 1 is a schematic diagram showing the force action of the brake linkage system of the first preferred embodiment of the present invention. Figure 2 is a diagram showing the relationship between the first output force and the second output force in the brake linkage system of the first preferred embodiment of the present invention. In this embodiment, the proportional controllable brake linkage system 1 includes a connecting rod 10, an input component 20, a first output component 30, a second output component 40, and a proportional control mechanism 50. The input component 20 is, for example, a left hand brake handle component for the user to operate and actuate the brake linkage system 1. The first output component 30 and the second output component 40 may be, for example, a rear wheel brake mechanism and a front wheel brake mechanism, respectively. In one embodiment, the first output component 30 and the second output component 40 are, for example, a rear-wheel drum brake mechanism and a front-wheel disc brake mechanism. Of course, this case is not limited to this. It should be noted that the output force of the first output component 30 and the second output component 40 can be applied to a drum type, a disc type or other types of brake mechanisms, which will not be repeated here. In this embodiment, the connecting rod 10 has a first end 11 and a second end 12, and the first end 11 and the second end 12 are opposite to each other. The input component 20 is pin-connected between the first end 11 and the second end 12 of the connecting rod 10, and is assembled to provide an input force F1, so that the connecting rod 10 is displaced in the direction of the input force F1. The first output component 30 is pin-connected to the first end 11 of the connecting rod 10 and generates a first output force F2 corresponding to the input force F1 of the input component 20. The second output component 40 is pin-connected to the second end 12 of the connecting rod 10. The proportional control mechanism 50 is connected to the second output component 40 and provides a modulating force F3 so that the second output component 40 responds to the input force F1 of the input component 20, the first output force F2 of the first output component 30, and the proportional control The modulating force F3 of the mechanism 50 generates a second output force F4. The ratio of the second output force F4 to the first output force F2 is non-linear, and at an early stage of braking or when the input force F1 input by the user through the input force component 20 is less than a specific value, it is ensured that the second output force F4 is less than The first output force F2. It should be noted that as the input force F1 of the input component 20 increases, the displacement generated by the connecting rod 10 increases, and the proportional control mechanism 50 can respond to a braking procedure with a non-constant value of the modulating force F3, which changes non-linearly. Figure 2 shows the solid line part.

式(1)

式(2)Figure 3 is a schematic diagram showing the application of the brake linkage system of the first preferred embodiment of the present invention. In this example, the first output component 30 and the second output component 40 of the brake linkage system 1 respectively provide a first output force F2 and a second output force F4 to a first runner 81 such as a rear wheel and a It is the second runner 82 of the front wheel to perform the aforementioned braking procedure. The proportional control mechanism 50 is further connected to a controller 53, and the controller 53 is connected to, for example, a first wheel speed detector 71 adjacent to the second runner 81 and a first wheel speed detector 71 adjacent to the second runner 82. A second wheel speed detector 72. The controller 53 receives the rotational speed signals of a first wheel speed detector 71 and a second wheel speed detector 72 and calculates the first slip rate λ _{1 of the} first runner 81 and the second runner 82 A second slip rate λ ₂ . The controller 53 further determines the control of the modulating force F3 command of the proportional control mechanism 50 according to the change relationship between the second sliding rate λ ₂ and the first sliding rate λ ₁ . In one embodiment, the first wheel speed detector 71 and the second wheel speed detector 72 can detect the rotation speed of the first wheel 81 and the second wheel 82, and the controller 53 calculates the first wheel The first sliding rate λ _{1 of} 81 and the second sliding rate λ _{2 of the} second runner 82. Taking the traveling speed V _{H of the} vehicle as an example, in the braking procedure, the first wheel speed detector 71 can measure the first rotation speed ω _{1 of the} first wheel 81; and the second wheel speed detector 72 can measure The second rotation speed ω _{2 of the} second runner 82. When the first runner 81 and the second runner 82 both have the same runner radius R, the first slip rate λ ₁ and the second slip rate λ ₂ can be expressed as the following equations (1) and (2), respectively ).

Formula 1)

Formula (2)

式(3)In this embodiment, the proportional control mechanism 50 can, for example, keep the first slip rate λ ₁ greater than the second slip rate λ ₂ in the aforementioned braking procedure. In other words, the modulating force F3 provided by the proportional control mechanism 50 can be, for example, a function of the second slip rate λ ₂ and the first slip rate λ ₁ , in response to the change of the second slip rate λ _{2 and} the change of the first slip rate λ ₁ The relationship provides the modulation power F3. Among them, the modulation force F3 can be expressed as the following formula (3)

Formula (3)

Figure 4 is a three-dimensional structural view of the brake linkage system of the first preferred embodiment of the present invention. Figure 5 is an exploded view showing the structure of the brake linkage system of the first preferred embodiment of the present invention. Fig. 6 is a three-dimensional structural diagram of some components of the brake linkage system of the first preferred embodiment of the present invention. Figure 7 is a schematic diagram showing the initial state of the brake linkage system of the first preferred embodiment of the present invention. Figure 8 is a schematic diagram showing the actuation state of the brake linkage system of the first preferred embodiment of the present invention. In this embodiment, the brake linkage system 1 further includes a housing 60 with an accommodating space 61, and the proportional control mechanism 50 is disposed on the housing 60. In this embodiment, the modulating force F3 of the proportional control mechanism 50 can directly act on the second output component 40, for example. The second output component 40 has a force receiving portion 41, for example, a cylindrical structure, fixed on the force application line in the second output component 40, so as to be configured to receive the modulating force F3 provided by the proportional control mechanism 50. In this embodiment, the proportional control mechanism 50 includes a powerful rod 51, a power source 52 and a controller 53. The force rod 51 is disposed in the housing 60 and is accommodated in the accommodating space 61 to provide the modulating force F3 and act on the force receiving portion 41 of the second output component 40. The lever 51 has a first arm 511 and a second arm 512 opposite to each other, and a pivot portion 513. The pivot portion 513 is pivotally connected to the housing 60, and the first arm 511 and the second arm 512 are located on both sides of the pivot portion 513. The first arm 511 of the force rod 51 is slidably connected to the force receiving portion 41 of the second output component 40, and the second arm 512 of the force rod 51 is slidably connected to the power source 52. In this embodiment, the power source 52 presses against the second arm 512 of the force rod 51, and the force rod 51 rotates around the pivot portion 513, driving the first arm 511 against the force receiving portion 41 of the second output component 40 . In addition, the power source 52 is disposed in the housing 60 and is slidably connected to the force rod 51 to drive the power rod 51 to generate the modulating force F3. The controller 53 is electrically connected to the power source 52 to control the power source 52 and further drive the power rod 51 to generate the modulating force F3. In this embodiment, the power source 52 may be, for example, a motor to provide power. The power source 52 further includes a transmission member 521 and a force applying portion 522. The transmission member 521 may be, for example, but not limited to, a rotating screw, and the force applying portion 522 is connected with the transmission member 521. When the power source 51 actuates the transmission member 521, the transmission member 521, for example, rotates a thread on a screw to drive the force applying portion 522 to generate displacement. The position of the controller 53 is not limited, and can be adjusted according to actual application requirements, and will not be repeated here. In this embodiment, the housing 60 further includes a guide groove 62, which is spatially arranged relative to the force applying portion 522 to guide the direction of movement of the force applying portion 522, so that the force applying portion 522 can make the The force rod 51 of the proportional control mechanism 50 is applied to the second output component 40 with a modulating force F3. In this embodiment, the first arm 511 may, for example, have an arc surface, and is spatially opposed to the force receiving portion 41 of the second output component 40 to be slidably connected with the force receiving portion 41 of the second output component 40. In one embodiment, the force application line in the second force output component 40 may penetrate through an opening on the first arm 511, for example, but it is not a necessary technical feature limiting the present case, and will not be repeated here. Similarly, the second arm 512 may also have, for example, an arc surface, which is spatially opposed to the urging portion 522 to be slidably connected to the urging portion 522 of the power source 52. The transmission member 521 can penetrate through an opening on the second arm 512, but it is not a necessary technical feature of the present case, and will not be described again.

之變化逐漸增加作用於例如後輪的第一轉輪81。於剎車初期或當使用者透過入力組件輸入之輸入力小於一特定值時，即小入力剎車時，確保第二輸出力小於第一輸出力。另一方面，第二出力組件40除了受到連桿10的拉動外，第二出力組件40上的受力部41同時受比例控制機構50施加調變力F3，第二出力組件40之第二輸出力F4可例如是以

之關係變化。由於調變力F3非一定值，呈非線性變化，故第二出力組件40之第二輸出力F4亦呈非線性變化，如第2圖所示實線部分。In this embodiment, the input component 20 can be, for example, a left-hand handle, and the connecting rod 10 is connected to the input component 20. When the user pulls the left-hand handle, the input component 20 inputs an input force F1. Of course, the manner in which the first output component 30 and the second output component 40 are connected to the connecting rod 10 is not limited to the necessary technical features of the present case. In this embodiment, the connection position of the first output component 30 at the first end 11 of the connecting rod 10 and the connection position of the second output component 40 at the second end 12 of the connecting rod 10 are opposite to each other, and can be, for example, respectively It is located on both sides of the access position of the input component 20, and has the same distance from the access position of the input component, but this case is not limited to this. It should be emphasized that, in this embodiment, as the user gradually increases the input force F1 with the input component 20 of the left hand, for example, the first output force F2 of the first output component 30 can be

The change gradually increases to act on, for example, the first runner 81 of the rear wheel. In the early stage of braking or when the input force input by the user through the input force component is less than a specific value, that is, when braking with a small input force, it is ensured that the second output force is less than the first output force. On the other hand, in addition to being pulled by the connecting rod 10, the second output assembly 40 is also pulled by the force receiving portion 41 on the second output assembly 40 by the proportional control mechanism 50 to apply the modulating force F3. The second output of the second output assembly 40 The force F4 can be for example

The relationship changes. Since the modulating force F3 is not a fixed value and changes nonlinearly, the second output force F4 of the second output component 40 also changes nonlinearly, as shown in the solid line part in FIG.

之間。於一實施例中，於剎車初期，比例控制機構50提供之調變力F3可以控制第二出力組件40之第二輸出力F4保持為零，即不對第二轉輪82作用。藉此，剎車連動系統1可延後例如前輪剎車機構之第二出力組件40之作用時間，使其晚於例如後輪剎車機構之第一出力組件30，而第一出力組件30先制動進行例如後輪之第一轉輪81進行剎車，可確保後輪會比前輪先停止轉動。It is worth noting that the value of the modulating force F3 is determined by the controller 53 of the proportional control mechanism 50 according to the relationship between the second slip rate λ ₂ and the first slip rate λ ₁ , and its range can be between 0 and

between. In one embodiment, at the initial stage of braking, the modulating force F3 provided by the proportional control mechanism 50 can control the second output force F4 of the second output component 40 to remain zero, that is, it does not act on the second runner 82. Thereby, the brake linkage system 1 can delay the action time of the second output component 40 of, for example, the front wheel brake mechanism, making it later than the first output component 30 of, for example, the rear wheel brake mechanism, and the first output component 30 first brakes for example The first wheel 81 of the rear wheel brakes to ensure that the rear wheel stops rotating before the front wheel.

As shown in Figure 2, in this embodiment, the modulating force F3 of the proportional control mechanism 50 can control the second output force F4 to be generated later than the first output force F2, because the modulating force F3 can respond to the second output force F3. The relationship between the slip rate λ ₂ and the first slip rate λ ₁ changes. The controller can adjust the appropriate value of F3 in accordance with the increase in the braking force of the vehicle, so that the second output force F4 follows the subsequent input force F1 and the first output The increase of the force F2 shows a non-linear relationship, so the ratio of the second output force F4 to the first output force F2 is a non-linear relationship. The goal is to make the ratio of the front and rear brake forces change in response to the change of the mass forward effect. , So that the relationship between the front and rear braking force changes along the ideal braking force curve, effectively improving the braking efficiency of the vehicle. As a result, the brake linkage system 1 of this case has the best braking performance. When braking in an emergency or on a slippery road, the rear wheels will stop rotating before the front wheels. If the rear wheel brake mechanism fails, such as disconnected or stuck, the proportional control mechanism 50 can control the front wheels not to generate braking force. In addition, if the front wheel brake mechanism fails, the rear wheel brake mechanism can still generate sufficient braking force.

On the other hand, it needs to be explained that, in this implementation, the brake linkage system 1 integrates the braking force of the front wheels and the braking force of the rear wheels through the aforementioned actuation mechanism, which is more robust. Taking the first output component 30 as a drum type rear wheel brake mechanism as an example for illustration, the variation conditions of the drum type brake mechanism are many and complicated. When the brake shoes in the rear wheel brake mechanism are worn out or the brake wire is not adjusted after the brake line is tired, the free clearance of the brake handle (or handlebar clearance) will increase and cause, for example, the first output component 30 of the rear brake mechanism. One output force F2 drops. However, when the brake linkage system 1 in this case integrates the front wheel brake force and the rear wheel brake force through the aforementioned actuation mechanism, even if the handlebar clearance exceeds the range without returning to the factory for adjustment, it can still ensure the first output component 30 of the rear wheel brake mechanism. For example, the second output component 40 of the front wheel brake mechanism is actuated first, and at the same time, the second output force F4 and the first output force F2 that change in a non-linear relationship and have a correct ratio are provided. As shown in the solid line in Figure 2, the relationship between the first output force F2 and the second output force F4 is the design curve of the brake linkage system 1 in this case. Compared with the theoretically locking front and rear wheels, the maximum reduction can be achieved. The ideal curve of speed (the dotted line). The ratio of the second output force F4 to the first output force F2 of the brake linkage system 1 in this case increases the safety margin S. Therefore, the brake linkage system 1 in this case integrates the front wheel brakes through the aforementioned actuation mechanism The design of power and rear wheel braking force is sufficiently robust to ensure that the braking force distribution of the front and rear wheels is not significantly degraded due to these factors.

Figure 9 is a schematic diagram showing the installation of the brake linkage system of the first preferred embodiment of the present invention. As shown in the figure, the brake linkage system 1 of the present application can be applied to, for example, a two-wheeled vehicle. The first output component 30 and the second output component 40 can be, for example, a rear wheel drum brake mechanism and a front wheel disc brake mechanism, respectively. The proportional control mechanism 50 is structured on the housing 60 (see Figure 4). The connecting rod 10 and the housing 60 are adjacent to the input component 20 of the left hand handle, for example, so that the input component 20 can efficiently provide the input force F1 to Connecting rod 10. Of course, the setting positions of the connecting rod 10 and the proportional control mechanism 50 can be adjusted according to actual application requirements, and this case is not limited to this. Similarly, the way in which the input component 20, the first output component 30, and the second output component 40 are connected to the connecting rod 10 is not limited, nor is it limited to the necessary technical content of the case, and can be adjusted according to actual application requirements. In this example, the user controls the input component 20 by, for example, the left hand handle, and controls the first output component 30 and the second output component 40 of the brake linkage system 1, and the modulating force F3 provided by the proportional control mechanism 50, The brake linkage system 1 can provide the second output force F4 and the first output force F2 (as shown in the solid line in Figure 2) that are in a non-linear relationship and have a correct ratio to complete the brake linkage of the front and rear wheels for the vehicle You can get comfort performance, maximum deceleration and stability when braking.

Figure 10 is a schematic diagram of the force action of the brake linkage system in the second preferred embodiment of the present invention. Figure 11 is a schematic diagram showing the application of the brake linkage system of the second preferred embodiment of the present invention. In this embodiment, the brake interlocking system 1a is similar to the brake interlocking system 1 shown in FIGS. 1-9, and the same component numbers represent the same components, structures and functions, and will not be repeated here. Different from the brake linkage system 1 shown in FIGS. 1-9, in this embodiment, the proportional control mechanism 50a can be connected to the second end 12 of the connecting rod 10 and provide a modulating force F3. Since the input force F1 of the input component 20, the first output force F2 of the first output component 30, and the modulating force F3 of the proportional control mechanism 50a act on the connecting rod 10, the second output component 40 connected to the connecting rod 10 can also be A second output force F4 is generated in response to the input force F1 of the input force component 20, the first output force F2 of the first output component 30, and the modulating force F3 of the proportional control mechanism 50a. Therefore, when the input force F1 input by the user through the input element 20 increases, the displacement generated by the connecting rod 10 increases, and the first output force F2 of the first output element 30 and the second output force F4 of the second output element 40 can be input relative to each other The force F1 increases. In this embodiment, the modulating force F3 generated by the proportional control mechanism 50a in response to the braking procedure is not a fixed value, but changes nonlinearly, as shown in the solid line part in FIG.

In this example, the first output component 30 and the second output component 40 of the brake linkage system 1a provide a first output force F2 and a second output force F4 respectively to a first runner 81 such as a rear wheel and a It is the second runner 82 of the front wheel to perform the aforementioned braking procedure. Similarly, the controller 53 connected to the proportional control mechanism 50a is further connected to, for example, a first wheel speed detector 71 adjacent to the second runner 81 and a second wheel speed detector 71 adjacent to the second runner 82.测器72. The first wheel speed detector 71 and the second wheel speed detector 72 can detect the rotation speed of the first wheel 81 and the second wheel 82 and send it to the controller 53 so that the controller 53 can calculate the first wheel respectively The first sliding rate λ _{1 of} 81 and the second sliding rate λ _{2 of the} second runner 82 are not described here. In this embodiment, the controller 53 connected to the proportional control mechanism 50a controls the proportional control mechanism 50a to provide the modulating force F3 in response to changes in the second slip rate λ ₂ and the first slip rate λ ₁ in the braking procedure, such as maintaining the first The slip rate λ _{1 is} greater than the second slip rate λ ₂ . Since the modulating force F3 provided by the proportional control mechanism 50a and the second output force F4 of the second output component 40 act on the second end 12 of the connecting rod 10 at the same time, it is more conducive for the brake linkage system 1a to provide a non-linear relationship change and configuration. The correct ratio of the second output force F4 to the first output force F2 (as shown in the solid line part in Figure 2), effectively integrates the front wheel braking force and the rear wheel braking force, and cooperates with the vehicle inertia forward effect to complete the braking linkage of the front and rear wheels , In order to obtain comfort performance, maximum deceleration and stability when the vehicle is braking.

To sum up, this case provides sufficient braking force through a single handle operation and deceleration in compliance with regulations. Use proportional control mechanism to provide modulating force, dynamically control front wheel brake force and rear wheel brake force, ensure the correct distribution of front and rear wheel brake force, so that the proportional change of rear wheel brake force and front wheel brake force is in a non-linear relationship, and it is in braking In the program, keep the slip rate of the rear wheels greater than the slip rate of the front wheels in order to obtain comfortable performance, maximum deceleration and stability when the vehicle is braking. In addition, its structure is simplified, its cost is reasonable, and its installation is easy. By pressing the single handle operation and the proportional control mechanism, the front and rear wheel brake force ratio is controlled, so that the rear wheel brake mechanism will brake first. During emergency braking or braking on slippery roads, the rear wheels will lock up before the front wheels. If the rear wheel brake mechanism fails, such as disconnected or stuck, the proportional control mechanism can control the front wheels not to generate braking force. If the front wheel brake mechanism fails, the rear wheel can maintain sufficient braking force. Effectively integrate the front wheel braking force and the rear wheel braking force to match the vehicle inertia forward effect, providing a non-linear proportional change of the front wheel braking force and the rear wheel braking force.

This case can be modified in many ways by those who are familiar with this technology, but it is not deviated from the protection of the patent application.

1. 1a: brake linkage system 10: connecting rod 11: first end 12: second end 20: input component 30: first output component 40: second output component 41: force receiving part 50, 50a: proportional control mechanism 51 : Force rod 511: First arm 512: Second arm 513: Pivot part 52: Power source 53: Controller 521: Transmission part 522: Force application part 60: Housing 61: Housing space 62: Guide groove 71: First wheel speed detector 72: Second wheel speed detector 81: First wheel 82: Second wheel F1: Input force F2: First output force F3: Modulation force F4: Second output force V _H : Travel speed of the vehicle R: Wheel radius S: Safety margin ω ₁ : First rotation speed ω ₂ : Second rotation speed λ ₁ : First slip rate λ ₂ : Second slip rate

Figure 1 is a schematic diagram showing the force action of the brake linkage system of the first preferred embodiment of the present invention. Figure 2 is a diagram showing the relationship between the first output force and the second output force in the brake linkage system of the first preferred embodiment of the present invention. Figure 3 is a schematic diagram showing the application of the brake linkage system of the first preferred embodiment of the present invention. Figure 4 is a three-dimensional structural view of the brake linkage system of the first preferred embodiment of the present invention. Figure 5 is an exploded view showing the structure of the brake linkage system of the first preferred embodiment of the present invention. Fig. 6 is a three-dimensional structural diagram of some components of the brake linkage system of the first preferred embodiment of the present invention. Figure 7 is a schematic diagram showing the initial state of the brake linkage system of the first preferred embodiment of the present invention. Figure 8 is a schematic diagram showing the actuation state of the brake linkage system of the first preferred embodiment of the present invention. Figure 9 is a schematic diagram showing the installation of the brake linkage system of the first preferred embodiment of the present invention. Figure 10 is a schematic diagram of the force action of the brake linkage system in the second preferred embodiment of the present invention. Figure 11 is a schematic diagram showing the application of the brake linkage system of the second preferred embodiment of the present invention.

1: Brake linkage system

10: connecting rod

11: first end

12: second end

20: Input components

30: The first output component

40: The second output component

41: Forced part

50: Proportional control mechanism

51: Force rod

53: Controller

71: The first wheel speed detector

72: Second wheel speed detector

81: The first runner

82: second runner

V _H : The traveling speed of the vehicle

R: Runner radius

ω ₁ : first speed

ω ₂ : second speed

λ ₁ : first slip rate

λ ₂ : second slip rate

Claims (10)

A brake linkage system capable of controlling the ratio of braking force, comprising: a connecting rod having a first end and a second end, the first end and the second end are opposite to each other; an input component, a pin connected to the connecting rod Between the first end and the second end of the connecting rod, it is assembled to provide an input force so that the connecting rod is displaced in the direction of the input force; a first output component, the pin is connected to the first connecting rod End, corresponding to the input force of the input component to generate a first output force; a second output component, the pin is connected to the second end of the connecting rod; and a proportional control mechanism, connected to the second output component or the The second end of the connecting rod provides a modulating force so that the second output component responds to the input force of the input component, the first output force of the first output component, and the adjustment of the proportional control mechanism The variable force produces a second output force. The brake linkage system capable of controlling the ratio of braking force according to claim 1, wherein the ratio of the second output force to the first output force changes in a non-linear manner, and at an early stage of braking or the input force is less than a specific value When, the second output force is less than the first output force. The brake linkage system capable of controlling the ratio of braking force according to claim 1, wherein the first output component and the second output component provide the first output force and the second output force to a first runner and a The second wheel is used to perform a braking procedure, wherein the proportional control mechanism is further connected to a controller which is connected to a first wheel speed detector and a second wheel speed detector. The first wheel The speed detector is configured to detect a first rotation speed of the first wheel, the second wheel speed detector is configured to detect a second rotation speed of the second wheel, and the controller is configured to detect a first rotation speed of the second rotation wheel. Calculate a first slip rate of the first runner and a second slip rate of the second runner based on the rotation speed and the second rotation speed, and correspond to the second slip rate of the second runner and the first runner The change relationship of the first sliding rate controls the proportional control mechanism to provide the modulating force. The brake linkage system capable of controlling the proportion of braking force as described in claim 3, wherein the proportional control mechanism maintains the first slip rate greater than the second slip rate during the braking procedure. The brake linkage system capable of controlling the ratio of braking force as described in claim 1, further includes a housing with an accommodating space, and the proportional control mechanism is arranged on the housing. The brake linkage system capable of controlling the proportion of braking force as described in claim 5, wherein the second output component has a force receiving part configured to receive the modulating force, wherein the proportional control mechanism includes: a force rod arranged at The housing is accommodated in the accommodating space to provide the modulating force and act on the force receiving portion of the second output component; a power source is provided in the housing and is slidably connected to the force rod to Driving the force rod to generate the modulating force; and a controller electrically connected to the power source to control the power source to drive the force rod to generate the modulating force. The brake linkage system capable of controlling the ratio of braking force according to claim 6, wherein the force rod has a first arm, a second arm, and a pivotal portion, the pivotal portion is pivotally connected to the housing, the The first arm and the second arm are located on both sides of the pivotal portion, wherein the first arm is slidably connected to the force receiving portion of the second output component, and the second arm is slidably connected to the power source, wherein the The power source presses against the second arm of the force rod, and the force rod rotates around the pivotal portion as a center to drive the first arm against the force receiving portion of the second output component. The brake interlocking system capable of controlling the ratio of braking force according to claim 7, wherein the power source includes a transmission member and a force application part, the transmission part is connected to the force application part, and the force application part is slidably connected to the power rod The second arm. The brake linkage system capable of controlling the ratio of braking force according to claim 1, wherein the first output component and the second output component are selected from the group consisting of a drum brake mechanism and a disc brake mechanism One. The brake linkage system capable of controlling the ratio of braking force according to claim 1, wherein the first output component and the second output component are a rear wheel brake mechanism and a front wheel brake mechanism, respectively.

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