Floor type brake-by-wire pedal and vehicle

Abstract

The utility model provides a floor type brake-by-wire pedal and a vehicle, and belongs to the technical field of vehicle brake pedals, the floor type brake-by-wire pedal comprises a pedal seat, the pedal seat is provided with a fixing part used for being fixedly connected with a vehicle floor, and the pedal seat can be fixedly connected with the vehicle floor through the fixing part to form a floor type structure; the pedal mechanism comprises a pedal arm, a connecting rod arm and a swing arm, the pedal arm is hinged to the pedal seat, the swing arm is hinged to the pedal seat, and the two ends of the connecting rod arm are hinged to the pedal arm and the swing arm respectively; the elastic piece is connected with the swinging arm; the floor type brake-by-wire pedal has the advantages that the floor type brake-by-wire pedal can provide non-linear pedal force, the brake pedal is arranged to be of a floor type structure, the lever ratio of the brake pedal is gradually reduced along with increase of the pedal stroke, and therefore the non-linear pedal force is provided.

Description

Technical Field

[0001] This utility model belongs to the field of vehicle brake pedal technology, and relates to a floor-mounted brake-by-wire pedal and a vehicle. Background Technology

[0002] Brake-by-wire pedals can be categorized into two main types based on their installation method and location: floor-mounted brake-by-wire pedals and suspended brake-by-wire pedals. Floor-mounted brake-by-wire pedals are directly mounted on the vehicle floor, with the pedal axle located near the bottom of the floor. This design provides more robust structural support and delivers more direct and precise braking feedback to the driver.

[0003] When the driver presses the floor-mounted brake-by-wire pedal, sensors detect the rotation angle of the pedal shaft and convert it into an electrical signal. Simultaneously, a pedal force simulation structure provides feedback force to the pedal arm, allowing the driver to instantly perceive the braking system's status and precisely control vehicle deceleration. The pedal force required for this system varies non-linearly: as the pedal travel increases, the increase in pedal force also increases. Traditional spring structures cannot achieve this non-linear pedal force characteristic.

[0004] Currently, there are some structures that can provide nonlinear or variable pedal force. For example, a utility model patent with application number CN201820860086.9, entitled "Pedal Assembly and Vehicle Having the Same", describes a pedal assembly with a crank-slider mechanism. When the pedal arm is pressed, the slider of the crank-slider mechanism moves, thereby changing the lever arm and thus changing the lever ratio.

[0005] The pedal assembly described above relies on the crank-slider mechanism to change the leverage ratio. However, in the crank-slider mechanism, the slider is prone to jamming or wear. Furthermore, this type of pedal assembly is a suspended structure. Therefore, there is currently no floor-mounted brake-by-wire pedal that can provide non-linear pedal force. Utility Model Content

[0006] The purpose of this invention is to address the aforementioned problems in the existing technology by proposing a floor-mounted brake-by-wire pedal and a vehicle.

[0007] The objective of this utility model can be achieved through the following technical solution: a floor-mounted brake-by-wire pedal, comprising:

[0008] A pedal seat having a fixing part for fixedly connecting to the vehicle floor, the pedal seat being able to be fixedly connected to the vehicle floor via the fixing part to form a floor-type structure;

[0009] A pedal mechanism, comprising a pedal arm, a connecting arm, and a swing arm, wherein the pedal arm is hinged to the pedal seat, the swing arm is hinged to the pedal seat, and the two ends of the connecting arm are respectively hinged to the pedal arm and the swing arm;

[0010] An elastic element, which is connected to the swing arm;

[0011] The pedal stroke determines the pedal arm's rotation angle, the pedal arm's rotation angle determines the position of the linkage arm, and the linkage arm's position determines the lever ratio of the pedal mechanism. When the pedal stroke increases, the lever ratio of the pedal mechanism decreases, causing the pedal force transmitted from the elastic element to the pedal arm via the swing arm and the linkage arm to increase non-linearly.

[0012] Preferably, it also includes a hysteresis block, which includes a force-receiving part and a hysteresis part. The hysteresis block is oscillatingly connected to the pedal seat. The force-receiving part and the hysteresis part are respectively located on both sides of the swing center of the hysteresis block and form a lever structure. One end of the elastic element is in contact with the force-receiving part and the other end is in contact with the swing arm. The hysteresis part is in contact with the swing arm.

[0013] When the pedal arm rotates, the hysteresis part of the hysteresis block applies a hysteresis force to the swing arm; the pedal stroke determines the pressure value applied by the elastic element to the force-receiving part, and the pressure value received by the force-receiving part determines the hysteresis force value applied by the hysteresis part to the swing arm.

[0014] Preferably, one of the hysteresis block's swing center position and the pedal seat is provided with a support shaft and the other is provided with a support groove, the support shaft being disposed in the support groove so that the hysteresis block can be oscillatingly connected to the pedal seat.

[0015] Preferably, the swing arm is provided with an arc surface, the arc surface is arranged with the hinge axis between the swing arm and the pedal seat as the center, and the hysteresis part is in contact with the arc surface; when the swing arm swings, a hysteresis force is generated between the hysteresis part and the arc surface.

[0016] Preferably, the stepping part of the pedal arm is set as point A, the hinge point between the pedal arm and the pedal seat is set as point B, the hinge point between the pedal arm and the connecting rod arm is set as point C, the hinge point between the swing arm and the connecting rod arm is set as point D, the hinge point between the swing arm and the pedal seat is set as point E, and the straight line passing through points C and D is set as straight line CD.

[0017] When the pedal stroke increases, the vertical distance between point B and line CD increases, and the vertical distance between point E and line CD decreases, resulting in a decrease in the lever ratio of the pedal mechanism.

[0018] Preferably, the contact point between the elastic element and the force-bearing part is set as point F, and the contact point between the elastic element and the swing arm is set as point H; when the pedal stroke of the pedal arm increases, the swing arm swings and forces the elastic element to compress, the distance between point F and point H decreases, the pressure value acting on the force-bearing part increases, and thus the hysteresis force applied by the hysteresis part to the swing arm increases.

[0019] Preferably, the pedal mechanism is configured as a four-bar linkage; when point A of the pedal arm is subjected to pressure, point A and point C of the pedal arm rotate together around point B, and point D and point H of the swing arm rotate together around point E, and the rotation direction of the pedal arm is opposite to the rotation direction of the swing arm.

[0020] Preferably, points A, B, and C of the pedal arm form a triangular structure, with points A, B, and C being the three vertices of the triangular structure, and points D, H, and E of the swing arm form another triangular structure, with points D, H, and E being the three vertices of the other triangular structure.

[0021] A vehicle includes the floor-mounted brake-by-wire pedal and a vehicle body, wherein the pedal seat of the floor-mounted brake-by-wire pedal is fixedly connected to the floor plate of the vehicle body via a fixing part.

[0022] Compared with the prior art, the beneficial effects of this utility model are as follows:

[0023] 1. A floor-mounted brake pedal capable of providing non-linear pedal force is provided. The brake pedal is configured as a floor-mounted structure, which gradually reduces the lever ratio as the pedal travel increases, thereby providing non-linear pedal force.

[0024] 2. When the pedal arm of the control pedal is pressed, it can provide not only pedal force but also hysteresis force. Since the hysteresis block forms a lever structure, when one side sinks, the other side rises. That is, the pressure on the force-bearing part can be transmitted to the hysteresis part. Under this pressure, the hysteresis part resists the rotating swing arm, thereby producing a hysteresis effect.

[0025] 3. When the driver applies force at point A, the pedal arm rotates around point B, causing the linkage arm to move. The linkage arm pushes the swing arm to rotate around point E, forcing the elastic element to gradually compress. As the pedal travel increases, the movement of the swing arm causes point H to move closer to point F, that is, the distance between point F and point H gradually decreases. As the degree of compression increases, the elastic force provided by the elastic element also increases accordingly, thereby increasing the pedal force and the hysteresis force. Attached Figure Description

[0026] Figure 1 This is a half-sectional view of the floor-mounted brake-by-wire pedal of this utility model.

[0027] Figure 2 This is a schematic diagram of the pedal mechanism of this utility model.

[0028] Figure 3 This is an axonometric view of the pedal mechanism of this utility model.

[0029] Figure 4 This is an axonometric view of the floor-mounted brake-by-wire pedal of this utility model.

[0030] Figure 5 This is a schematic diagram showing the positions of various points of the floor-mounted brake-by-wire pedal of this utility model in its initial state.

[0031] Figure 6 This is a schematic diagram showing the positions of various points of the floor-mounted brake-by-wire pedal at its travel limit.

[0032] Figure 7 This is a schematic diagram illustrating the simulation relationship between the pedal arm travel and the pedal force of this utility model.

[0033] In the figure, 100 is the pedal seat; 110 is the fixing part; 120 is the support groove; 200 is the pedal arm; 300 is the connecting rod arm; 400 is the swing arm; 410 is the arc surface; 500 is the elastic element; 600 is the hysteresis block; 610 is the force-bearing part; 620 is the hysteresis part; and 630 is the support shaft. Detailed Implementation

[0034] The following are specific embodiments of the present invention, which are described in conjunction with the accompanying drawings. However, the present invention is not limited to these embodiments.

[0035] like Figures 1 to 7As shown, a floor-mounted brake-by-wire pedal includes: a pedal seat 100, which has a fixing part 110 for fixed connection with the vehicle floor, the pedal seat 100 being able to be fixedly connected to the vehicle floor via the fixing part 110 to form a floor-mounted structure; and a pedal mechanism, the pedal mechanism including a pedal arm 200, a connecting arm 300, and a swing arm 400, the pedal arm 200 being hinged to the pedal seat 100, the swing arm 400 being hinged to the pedal seat 100, and the two ends of the connecting arm 300 being respectively connected to the pedal arm 200. The pedal arm 400 is hinged; the elastic element 500 is connected to the swing arm 400; the pedal stroke of the pedal arm 200 determines the rotation angle of the pedal arm 200, the rotation angle of the pedal arm 200 determines the position of the linkage arm 300, and the position of the linkage arm 300 determines the leverage ratio of the pedal mechanism; when the pedal stroke of the pedal arm 200 increases, the leverage ratio of the pedal mechanism decreases, causing the pedal force transmitted from the elastic element 500 to the pedal arm 200 through the swing arm 400 and the linkage arm 300 to increase non-linearly.

[0036] Brake pedal force refers to the reaction force felt by the driver when pressing the brake pedal. It is a crucial component of the interaction between the driver and the vehicle's braking system. For brake-by-wire pedals, since there is no hydraulic system or mechanical linkage to feedback the pedal force, an elastic element (500) is used to simulate the pedal force. The ideal pedal force is not a simple linear relationship; that is, as the pedal travel increases, the required pedal force gradually increases, but the increase is not constant. This non-linear characteristic makes it easy to obtain slight braking force when lightly pressing the pedal in the initial stage, while requiring greater force to further increase braking force near the maximum travel, thus allowing for more precise and smooth braking control.

[0037] To achieve the desired nonlinear pedal force characteristics, traditional spring structures often fall short because they typically only provide an approximately linear force-displacement relationship. However, in this linear brake pedal, the pedal mechanism is designed as a four-bar linkage. As the pedal travel increases, the lever ratio of the four-bar linkage gradually decreases. Therefore, the originally linear spring force can generate nonlinear pedal force feedback through this gradually changing lever ratio.

[0038] In this line-controlled brake pedal, the pedal seat 100 serves as the foundation and fixing point of the entire pedal mechanism. The pedal seat 100 is characterized by its floor-mounted structure, and the fixing part 110 is responsible for firmly fixing the entire pedal device to the vehicle floor. The pedal mechanism is actually a specially designed four-bar linkage. Its key feature is that it can change its leverage ratio with the pedal travel. The pedal mechanism consists of a pedal arm 200, a connecting arm 300, and a swing arm 400. The pedal arm 200 is hinged to the pedal seat 100. The pedal part (point A) of the pedal arm 200 is the part directly operated by the driver. The connecting arm 300 is hinged at both ends to the pedal arm 200 and the swing arm 400, respectively, acting as a lever and transmitting motion. The swing arm 400 is hinged to the pedal seat 100 and connected to the elastic element 500. When the swing arm 400 rotates, it compresses the elastic element 500. The elastic force generated when the elastic element 500 is compressed acts on the swing arm 400 and is amplified by the connecting arm 300 before being transmitted to the pedal arm 200, thus forming the pedal force. This pedal force not only provides feedback during pedaling but also serves as a return mechanism. It is worth noting that the elastic element 500 can be set as a single spring or as a spring group consisting of two or more springs.

[0039] The working logic and principle of the pedal mechanism in changing the leverage ratio are as follows: When the pedal arm 200 is pressed (point A), the pedal arm 200 rotates around its hinge point with the pedal seat 100 (point B), driving the connecting rod arm 300, which is hinged thereto, to move. Simultaneously, the pedal arm 200, through the connecting rod arm 300, drives the swing arm 400 to rotate around its hinge point with the pedal seat 100 (point E). During this process, the position of the connecting rod arm 300 changes, causing changes in the lever arm between the pedal arm 200 and the connecting rod arm 300, and also between the swing arm 400 and the connecting rod arm 300, thus altering the leverage ratio of the entire system. The pedal force is determined by both the elastic force of the elastic element 500 and the leverage ratio. Although the elastic force of the elastic element 500 changes linearly with the travel of the pedal arm 200, the leverage ratio also changes with the travel of the pedal arm 200. Therefore, the final pedal force changes non-linearly with the travel of the pedal arm 200.

[0040] The four-bar linkage design makes the entire pedal mechanism both compact and efficient, reducing unnecessary complexity. The components are connected via hinges, ensuring smooth and stable movement and reducing the risk of malfunction. Furthermore, this design is less prone to jamming or wear, offering high reliability and durability.

[0041] like Figures 1 to 3As shown, based on the above embodiment, a hysteresis block 600 is also included. The hysteresis block 600 includes a force-receiving part 610 and a hysteresis part 620. The hysteresis block 600 is oscillatingly connected to the pedal seat 100. The force-receiving part 610 and the hysteresis part 620 are located on both sides of the swing center of the hysteresis block 600 and form a lever structure. One end of the elastic member 500 is in contact with the force-receiving part 610 and the other end is in contact with the swing arm 400. The hysteresis part 620 is in contact with the swing arm 400. When the pedal arm 200 rotates, the hysteresis part 620 of the hysteresis block 600 applies a hysteresis force to the swing arm 400. The pedal stroke of the pedal arm 200 determines the pressure value applied by the elastic member 500 to the force-receiving part 610, and the pressure value received by the force-receiving part 610 determines the hysteresis force value applied by the hysteresis part 620 to the swing arm 400.

[0042] When the pedal arm 200 of this brake pedal is depressed, it provides not only pedal force but also hysteresis force. Hysteresis force refers to the asymmetry or difference between the pedal force and pedal travel during braking, when the driver depresses and releases the brake pedal. In this embodiment, the hysteresis force is generated by the friction between the hysteresis portion 620 and the swing arm 400, and the magnitude of the hysteresis force is directly proportional to the pressure exerted by the hysteresis portion 620 against the swing arm 400.

[0043] The elastic element 500 is not installed between the pedal seat 100 and the swing arm 400, but is located between the force-receiving part 610 of the hysteresis block 600 and point H of the swing arm 400. The hysteresis block 600 forms a swingable lever structure within the pedal seat 100; the force-receiving part 610 is located on one side of the lever and is in direct contact with the elastic element 500 (such as a spring), responsible for receiving pressure from the elastic element 500; the hysteresis part 620 is located on the other side of the hysteresis block 600 and is in contact with the swing arm 400, used to apply a hysteresis force; since the hysteresis block 600 forms a lever structure, when one side sinks, the other side tilts up, that is, the pressure on the force-receiving part 610 can be transmitted to the hysteresis part 620, and the hysteresis part 620 resists the rotating swing arm 400 under this pressure, thereby producing a hysteresis effect.

[0044] Based on the above embodiments, a support shaft 630 is provided at one of the swing center position of the hysteresis block 600 and the pedal seat 100, and a support groove 120 is provided at the other. The support shaft 630 is disposed in the support groove 120 so that the hysteresis block 600 can be oscillatingly connected to the pedal seat 100.

[0045] To enable the hysteresis block 600 to be oscillatingly connected to the pedal seat 100, this embodiment employs a cooperation mechanism of support shaft 630 and support groove 120. The support shaft 630 is designed as a strip-shaped protrusion structure with an arc-shaped curved surface. The support groove 120 is designed as an arc-shaped groove, and the shapes of the support shaft 630 and the support groove 120 are adapted to each other. The support shaft 630 is set in the support groove 120 to form a hinge structure. The support shaft 630 serves as the swing center of the hysteresis block 600, enabling the hysteresis block 600 to swing, thereby transmitting the pressure received by the force-bearing part 610 to the hysteresis part 620.

[0046] Based on the above embodiments, the swing arm 400 is provided with an arc surface 410, the arc surface 410 is set with the hinge axis between the swing arm 400 and the pedal seat 100 as the center, and the hysteresis part 620 is in contact with the arc surface 410; when the swing arm 400 swings, a hysteresis force is generated between the hysteresis part 620 and the arc surface 410.

[0047] In the example, one end of the swing arm 400 is hinged to the pedal seat 100, and the outer peripheral surface of one end of the swing arm 400 is set as an arc surface 410. With point E as the center, when the swing arm 400 rotates around point E, the relative motion between the hysteresis part 620 and the arc surface 410 will generate friction, thereby forming a hysteresis force.

[0048] When the pedal arm 200 of the control pedal is pressed, the pedal arm 200 rotates around point B, which in turn drives the swing arm 400 to rotate around point E via the linkage arm 300. The swing arm 400 presses against the elastic element 500, and the elastic force generated by the elastic element 500 forms the pedal force after passing through the swing arm 400, the linkage arm 300, and the pedal arm 200. During this process, the elastic element 500 applies pressure to the force-receiving part 610 of the hysteresis block 600. This pressure is transmitted to the hysteresis part 620 after passing through the lever structure of the hysteresis block 600, causing the hysteresis part 620 to press against the arc surface 410 of the swing arm 400. Since the swing arm 400 is rotating, a hysteresis force is generated between the hysteresis part 620 and the arc surface 410 of the swing arm 400 through friction. This hysteresis force is transmitted to the pedal arm 200 through the swing arm 400, and then fed back to the driver.

[0049] It should be further explained here that the rotation angle (pedal stroke) of the pedal arm 200 determines the rotation angle of the swing arm 400, and the rotation angle of the swing arm 400 determines the compression of the elastic element 500. In other words, the rotation angle of the pedal arm 200 determines the elastic force of the elastic element 500. The pressure exerted by the hysteresis unit 620 on the arc surface 410 is determined by the elastic force of the elastic element 500. Therefore, the pedal stroke of the pedal arm 200 determines the magnitude of the hysteresis force. Specifically, the greater the pedal stroke of the pedal arm 200, the greater the hysteresis force generated.

[0050] like Figures 1 to 7 As shown, based on the above embodiment, the pedal arm 200 is stepped on at point A, the hinge point between the pedal arm 200 and the pedal seat 100 is set at point B, the hinge point between the pedal arm 200 and the connecting rod arm 300 is set at point C, the hinge point between the swing arm 400 and the connecting rod arm 300 is set at point D, and the hinge point between the swing arm 400 and the pedal seat 100 is set at point E. The straight line passing through points C and D is set as straight line CD. When the pedal stroke of the pedal arm 200 increases, the vertical distance between point B and straight line CD increases, and the vertical distance between point E and straight line CD decreases, resulting in a decrease in the lever ratio of the pedal mechanism.

[0051] For the pedal arm 200, point A can be located at one end of the pedal arm 200, and point B can be located at the other end of the pedal arm 200. For the swing arm 400, points D and E are located at the two ends of the swing arm 400, respectively, and the middle position of the swing arm 400 (i.e., point H) is used to connect with the elastic element 500.

[0052] The principle behind the pedal mechanism changing the lever ratio is as follows: During pedaling, since points B and E are hinge points, their positions remain unchanged throughout the pedaling process. However, the position of the connecting arm 30° changes, which causes changes in the perpendicular distances between points B and line CD, and between points E and line CD. The lever ratio is defined by the formula: rat io = L AB ×L E->CD / (L B->CD ×L E->FH As shown in the formula, the leverage ratio is determined by the lever arm lengths between the pedal arm 200 and the connecting rod arm 300, as well as the lever arm lengths between the swing arm 400 and the connecting rod arm 300. That is, when the perpendicular distances between point B and line CD, and between point E and line CD, change, the leverage ratio naturally changes. More specifically, if the perpendicular distance between point B and line CD increases, and the perpendicular distance between point E and line CD decreases, then according to the leverage ratio formula, the leverage ratio decreases.

[0053] Based on the above embodiment, the contact point between the elastic element 500 and the force-receiving part 610 is set as point F, and the contact point between the elastic element 500 and the swing arm 400 is set as point H. When the pedal stroke of the pedal arm 200 increases, the swing arm 400 swings and forces the elastic element 500 to compress, the distance between point F and point H decreases, the pressure value acting on the force-receiving part 610 increases, and the hysteresis force applied by the hysteresis part 620 to the swing arm 400 increases.

[0054] It is important to note here that although the hysteresis block 600 is oscillatingly connected to the pedal seat 100 and the hysteresis block 600 is designed as a lever structure, the oscillating structure (lever structure) of the hysteresis block 600 is only for transmitting the pressure of the force-bearing part 610 to the hysteresis part 620. The hysteresis block 600 does not rotate during actual operation, and only transmits pressure through the rotation center (support shaft 630). Therefore, the contact point (point F) between the elastic element 500 and the force-bearing part 610 can be regarded as a fixed point.

[0055] When the pedal is not depressed, the elastic element 500 is in its naturally extended state, and the distance between points F and H is at its maximum. When the driver applies force at point A, the pedal arm 200 rotates around point B, causing the linkage arm 300 to move. The linkage arm 300 pushes the swing arm 400 to rotate around point E, forcing the elastic element 500 to gradually compress. As the pedal travel increases, the movement of the swing arm 400 causes point H to move closer to point F, that is, the distance between points F and H gradually decreases. As the degree of compression increases, the elastic force provided by the elastic element 500 also increases accordingly, thereby increasing the pedal force and the hysteresis force.

[0056] It should be noted here that the leverage ratio is defined as: rat io = L AB ×L E->CD / (L B->CD ×L E->FH ), ratio is the leverage ratio, L AB Let L be the distance between point A and point B. E->CD Let L be the perpendicular distance between point E and line CD. B->CD Let L be the perpendicular distance between point B and line CD. E->FH The perpendicular distance from point E to line FH; the definition of the pedal force is: F pedal =F spring / ra tio, F pedal For pedal force, F spring The elastic force of the elastic element is 500.

[0057] L AB In reality, L is the distance from the pivot point of the pedal arm 200 to the point of force application, so L AB This can be set to a fixed value by default. As the travel of the pedal arm (200) increases, L... E->CD Decrease, L B->CD As the lever ratio increases, the lever ratio decreases, according to the definition formula. Conversely, as the pedal force increases, the spring force F... sprin g The force increases non-linearly, while the leverage ratio decreases, so the pedal force increases non-linearly.

[0058] like Figures 1 to 7As shown, based on the above embodiment, the pedal mechanism is configured as a four-bar linkage; when point A of the pedal arm 200 is subjected to pressure, point A and point C of the pedal arm 200 rotate together around point B, and point D and point H of the swing arm 400 rotate together around point E, and the rotation direction of the pedal arm 200 is opposite to the rotation direction of the swing arm 400.

[0059] When point A is subjected to a pedaling force, the pedal arm 200 rotates clockwise or counterclockwise around point B, while the swing arm 400 rotates counterclockwise or clockwise around point E. That is, by cleverly arranging the position of the hinge point, the pedal arm 200 and the swing arm 400 rotate in opposite directions. Through this motion logic, when the pedal arm 200 rotates around point B, the perpendicular distance between point B and line CD increases, and the perpendicular distance between point E and line CD decreases. This results in a decrease in the leverage ratio when the stroke of the pedal arm 200 increases.

[0060] Based on the above implementation, points A, B, and C of the pedal arm 200 form a triangular structure, and points A, B, and C are the three vertices of the triangular structure. Points D, H, and E of the swing arm 400 form another triangular structure, and points D, H, and E are the three vertices of the other triangular structure.

[0061] like Figures 1 to 7 As shown, based on the above embodiments, a vehicle includes a floor-mounted brake-by-wire pedal and a vehicle body. The pedal seat 100 of the floor-mounted brake-by-wire pedal is fixedly connected to the floor plate of the vehicle body via a fixing part 110.

[0062] The pedal seat 100 provides a solid supporting foundation for the entire pedal mechanism. It is fixed to the vehicle's floor via the fixing part 110. The vehicle's floor-mounted brake-by-wire pedal exhibits non-linear pedal force and hysteresis characteristics during braking. During braking, the pedal force increases with the increase in pedal travel, achieving ideal non-linear pedal force characteristics. This helps to obtain slight braking force when the pedal is lightly pressed initially, requiring greater force to further increase braking force as the pedal travel approaches its maximum, thus allowing for more precise and smooth braking control. The hysteresis block 600 forms a lever structure; as the pedal travel increases, the hysteresis force acting on the swing arm 400 increases, enhancing the realism and subtlety of the pedal feedback.

[0063] It should be noted that all directional indicators (such as up, down, left, right, front, back, etc.) in this utility model embodiment are only used to explain the relative positional relationship and movement of each component in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indicator will also change accordingly.

[0064] Furthermore, in this utility model, the use of terms such as "first," "second," and "a" is for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this utility model, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0065] In this utility model, unless otherwise explicitly specified and limited, the terms "connection," "fixing," etc., should be interpreted broadly. For example, "fixing" can mean a fixed connection, a detachable connection, or an integral part; it can mean a mechanical connection or an electrical connection; it can mean a direct connection or an indirect connection through an intermediate medium; it can mean the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0066] Furthermore, the technical solutions of the various embodiments of this utility model can be combined with each other, but only if they are based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or cannot be implemented, it should be considered that such combination of technical solutions does not exist and is not within the scope of protection claimed by this utility model.

Claims

1. A floor-mounted brake-by-wire pedal, characterized in that, include: A pedal seat (100) having a fixing part (110) for fixed connection with the vehicle floor, the pedal seat (100) being able to be fixedly connected with the vehicle floor via the fixing part (110) to form a floor-type structure; A pedal mechanism, comprising a pedal arm (200), a connecting arm (300), and a swing arm (400), wherein the pedal arm (200) is hinged to the pedal seat (100), the swing arm (400) is hinged to the pedal seat (100), and the two ends of the connecting arm (300) are respectively hinged to the pedal arm (200) and the swing arm (400); An elastic element (500) is connected to the swing arm (400); The pedal stroke of the pedal arm (200) determines the rotation angle of the pedal arm (200), the rotation angle of the pedal arm (200) determines the position of the linkage arm (300), and the position of the linkage arm (300) determines the leverage ratio of the pedal mechanism. When the pedal stroke of the pedal arm (200) increases, the leverage ratio of the pedal mechanism decreases, causing the pedal force transmitted from the elastic element (500) to the pedal arm (200) through the swing arm (400) and the linkage arm (300) to increase non-linearly.

2. A floor-mounted brake-by-wire pedal as described in claim 1, characterized in that: It also includes a hysteresis block (600), which includes a force-receiving part (610) and a hysteresis part (620). The hysteresis block (600) is oscillatingly connected to the pedal seat (100). The force-receiving part (610) and the hysteresis part (620) are located on both sides of the swing center of the hysteresis block (600) and form a lever structure. One end of the elastic member (500) is in contact with the force-receiving part (610) and the other end is in contact with the swing arm (400). The hysteresis part (620) is in contact with the swing arm (400). When the pedal arm (200) rotates, the hysteresis part (620) of the hysteresis block (600) applies a hysteresis force to the swing arm (400); the pedal stroke of the pedal arm (200) determines the pressure value applied by the elastic element (500) to the force receiving part (610), and the pressure value received by the force receiving part (610) determines the hysteresis force value applied by the hysteresis part (620) to the swing arm (400).

3. A floor-mounted brake-by-wire pedal as described in claim 2, characterized in that: The hysteresis block (600) has a support shaft (630) at its swing center position and the pedal seat (100) has a support groove (120) at its other position. The support shaft (630) is disposed in the support groove (120) so that the hysteresis block (600) can be oscillatingly connected to the pedal seat (100).

4. A floor-mounted brake-by-wire pedal as described in claim 2, characterized in that: The swing arm (400) is provided with an arc surface (410), which is set with the hinge axis between the swing arm (400) and the pedal seat (100) as the center. The hysteresis part (620) is in contact with the arc surface (410). When the swing arm (400) swings, a hysteresis force is generated between the hysteresis part (620) and the arc surface (410).

5. A floor-mounted brake-by-wire pedal as described in any one of claims 2 to 4, characterized in that: The stepping point of the pedal arm (200) is set as point A, the hinge point between the pedal arm (200) and the pedal seat (100) is set as point B, the hinge point between the pedal arm (200) and the connecting arm (300) is set as point C, the hinge point between the swing arm (400) and the connecting arm (300) is set as point D, the hinge point between the swing arm (400) and the pedal seat (100) is set as point E, and the straight line passing through points C and D is set as straight line CD; When the pedal stroke of the pedal arm (200) increases, the vertical distance between point B and line CD increases, and the vertical distance between point E and line CD decreases, resulting in a decrease in the lever ratio of the pedal mechanism.

6. A floor-mounted brake-by-wire pedal as described in claim 5, characterized in that: The contact point between the elastic element (500) and the force-receiving part (610) is set as point F, and the contact point between the elastic element (500) and the swing arm (400) is set as point H. When the pedal stroke of the pedal arm (200) increases, the swing arm (400) swings and forces the elastic element (500) to compress, the distance between point F and point H decreases, the pressure value acting on the force-receiving part (610) increases, and thus the hysteresis force applied by the hysteresis part (620) to the swing arm (400) increases.

7. A floor-mounted brake-by-wire pedal as described in claim 5, characterized in that: The pedal mechanism is configured as a four-bar linkage; when point A of the pedal arm (200) is subjected to pressure, point A and point C of the pedal arm (200) rotate together around point B, and point D and point H of the swing arm (400) rotate together around point E, and the rotation direction of the pedal arm (200) is opposite to the rotation direction of the swing arm (400).

8. A floor-mounted brake-by-wire pedal as described in claim 5, characterized in that: Points A, B, and C of the pedal arm (200) form a triangular structure, and points A, B, and C are the three vertices of the triangular structure. Points D, H, and E of the swing arm (400) form another triangular structure, and points D, H, and E are the three vertices of the other triangular structure.

9. A vehicle, characterized in that, The system includes a floor-mounted brake-by-wire pedal as described in any one of claims 1 to 8, and also includes a vehicle body, wherein the pedal seat (100) of the floor-mounted brake-by-wire pedal is fixedly connected to the floor plate of the vehicle body via a fixing part (110).

Images