Electronic mechanical brake device with embedded lead screw and output shaft and vehicle

Abstract

The invention provides an electronic mechanical braking device with a lead screw and an output shaft embedded and a vehicle. Comprising brake calipers, a ball screw and a speed reducer, the ball screw comprises a lead screw and a threaded sleeve, the speed reducer comprises an output shaft, one end of the output shaft is used for driving the lead screw to rotate, the threaded sleeve is used for moving in the axial direction of the lead screw along with rotation of the lead screw, and the brake calipers are used for fixing the speed reducer and containing the lead screw and the threaded sleeve. The end face of the lead screw faces the speed reducer in the axial direction of the lead screw and comprises axial grooves, one end of the output shaft is used for being embedded into one axial groove in the axial direction of the lead screw, and the axial grooves are used for being in transmission connection with one end of the output shaft. Or the axial protrusion is used for being embedded into or embedded into one end of the output shaft in the axial direction of the lead screw, and the axial protrusion is used for being in transmission connection with one end of the output shaft. According to the electronic mechanical braking device, the output shaft is embedded or nested in the lead screw, so that the axial size of the electronic mechanical braking device is reduced.

Description

Technical Field

[0001] The present application relates to the field of vehicle technology, and in particular to an electronic mechanical braking device in which a lead screw and an output shaft are embedded, and a vehicle. Background Art

[0002] Electromechanical brakes (EMBs) utilize a motor and a mechanical feed mechanism to actuate the brakes. They offer a simple structure, responsiveness, smooth load transfer, and the absence of hydraulic piping, resulting in high transmission efficiency. Furthermore, EMBs are trending towards miniaturization to accommodate wheel space. Summary of the Invention

[0003] The present application provides an electronic mechanical brake device and a vehicle in which a lead screw and an output shaft are embedded. The output shaft is embedded or nested in the lead screw to reduce the axial size of the electronic mechanical brake device. The present application specifically includes the following solutions:

[0004] In a first aspect, the present application provides an electronic mechanical brake device in which a screw and an output shaft are embedded. The electronic mechanical brake device includes a brake caliper, a ball screw, and a reducer. The ball screw includes a screw and a screw sleeve. The reducer includes an output shaft. One end of the output shaft is used to drive a screw to rotate. The screw sleeve is used to move along the axial direction of the screw as the screw rotates. A brake caliper is used to fix a reducer and to accommodate a screw and a screw sleeve. An end face of a screw faces a reducer along the axial direction of the screw. The end face includes:

[0005] An axial groove, one end of an output shaft is used to be embedded in an axial groove along the axial direction of the screw, and the axial groove is used to drive and connect one end of an output shaft; or,

[0006] An axial protrusion is used to be embedded in or nested in one end of an output shaft along the axial direction of a screw, and an axial protrusion is used to drive and connect one end of an output shaft.

[0007] The electronic mechanical device of the present application fixes a reducer through a brake caliper and accommodates a ball screw, so that a reducer can drive a screw to rotate through an output shaft, and a screw drives a sleeve to move along the axial direction of the screw and push one or more friction plates to achieve braking.

[0008] The end surface of a lead screw facing a reducer includes an axial groove or an axial protrusion. One end of an output shaft is embedded in an axial groove or an axial protrusion, or one end of an output shaft is nested in an axial protrusion, thereby achieving a transmission connection between the output shaft and the lead screw. The electronic mechanical brake device of the present application is embedded in an output shaft and a lead screw, which compresses the axial length of the electronic mechanical brake device, facilitates the miniaturization of the electronic mechanical brake device, and facilitates its adaptation to the wheel side space.

[0009] In one implementation, a thread on the inner circumference of a screw sleeve is used to engage a thread on the outer circumference of a lead screw, and a brake caliper includes a receiving cavity, and the receiving cavity is used to accommodate at least one of a pressure sensor or a thrust bearing, a screw sleeve, and a lead screw, wherein:

[0010] Along the axial direction of a lead screw, at least one of a pressure sensor and a thrust bearing is arranged between an end face and a cavity wall of an accommodating cavity.

[0011] In this embodiment, a threaded sleeve is disposed outside a lead screw and meshes with the lead screw for transmission. The outer circumference of the threaded sleeve is configured to abut the inner circumference of a receiving chamber. A pressure sensor or a thrust bearing is also accommodated between the cavity wall of the receiving chamber and an end face of the lead screw.

[0012] Among them, a pressure sensor is used to detect the axial thrust exerted on a screw during the operation of the electronic mechanical brake device, and then adjust the braking force output by the brake motor; a thrust bearing is used to bear the axial thrust exerted on a screw during the operation of the electronic mechanical brake device, ensuring that an output shaft drives a screw to rotate smoothly.

[0013] In one implementation, one end of an output shaft penetrates a cavity wall of an accommodating cavity to extend into the accommodating cavity and be embedded with a lead screw.

[0014] In this implementation, because an output shaft and a lead screw are embedded in a brake caliper, the transmission structure between an output shaft and a reducer can be simplified, so as to compress the axial size of a reducer.

[0015] In one implementation, along the axial direction of a lead screw, the length of one end of an output shaft embedded in the lead screw is greater than the length of the other end of the output shaft.

[0016] In one implementation, an end surface includes an axial protrusion, wherein:

[0017] Along the axial direction of a screw, the length of a screw is greater than the length of a sleeve;

[0018] Along the radial direction of a lead screw, a diameter of an axial protrusion is smaller than an inner diameter of a threaded sleeve;

[0019] Along the axial direction of a lead screw and in a direction toward a reducer, a thrust bearing and a pressure sensor are sequentially sleeved on an axial protrusion.

[0020] In this implementation, the length of a screw is greater than the length of a sleeve, so that a sleeve is always engaged with a screw during the axial sliding process along the screw; the diameter of an axial protrusion is smaller than the inner diameter of a sleeve, which can control the volume of the structure embedded between an axial protrusion and one end of an output shaft; a thrust bearing is supported between an end face of a screw and a pressure sensor, which can ensure that a pressure sensor is stationary relative to a brake caliper and ensure that a screw rotates smoothly.

[0021] In one implementation, along the radial direction of a lead screw:

[0022] The diameter of an axial protrusion is larger than the diameter of an output shaft, and the inner hole of a thrust bearing and the inner hole of a pressure sensor are respectively used to abut against the outer peripheral surface of an axial protrusion;

[0023] In this implementation, an axial protrusion is used to nest one end of an output shaft, and the outer peripheral surface of an axial protrusion is used to abut the inner hole of a thrust bearing and the inner hole of a pressure sensor, so as to achieve radial positioning of a thrust bearing and a pressure sensor respectively.

[0024] In one implementation, along the radial direction of a lead screw:

[0025] The diameter of an output shaft is larger than the diameter of an axial protrusion, and the inner hole of a thrust bearing and the inner hole of a pressure sensor are respectively used to abut against the outer peripheral surface of an output shaft.

[0026] In this implementation, an axial protrusion is used to embed one end of an output shaft, and the outer peripheral surface of one end of an output shaft is used to abut the inner hole of a thrust bearing and the inner hole of a pressure sensor, so as to achieve radial positioning of a thrust bearing and a pressure sensor respectively.

[0027] In one implementation, an end surface includes an axial groove, wherein:

[0028] Along the axial direction of a screw, the length of a screw is greater than the length of a sleeve;

[0029] Along the radial direction of a lead screw, the diameter of an axial groove is smaller than the inner diameter of a threaded sleeve;

[0030] A thrust bearing and a pressure sensor are sequentially sleeved on an output shaft along an axial direction of a lead screw and in a direction toward a reducer;

[0031] An inner hole of a thrust bearing and an inner hole of a pressure sensor are respectively used to abut against an outer peripheral surface of an output shaft.

[0032] In this implementation, the diameter of an axial groove is smaller than the inner diameter of a screw sleeve, which can control the volume of the structure embedded between one end of an output shaft and an axial groove; and on the side of an end face facing the reducer, because an axial protrusion structure is omitted, the outer peripheral surface of an output shaft is used to support the inner hole of a thrust bearing and the inner hole of a pressure sensor, thereby reducing the radial dimensions of a thrust bearing and a pressure sensor while achieving radial positioning of a thrust bearing and a pressure sensor.

[0033] In one implementation, an accommodating cavity along the axial direction of a lead screw includes a first section and a second section connected to each other, the inner circumference of the first section is used to abut the outer circumference of the screw sleeve, and the inner circumference of the second section is used to abut the outer circumference of the pressure sensor, wherein:

[0034] Along the radial direction of a lead screw, the inner circumference diameter of the second section is smaller than the inner circumference diameter of the first section and larger than the inner diameter of a screw sleeve;

[0035] Along the axial direction of a lead screw, the length of the second section is less than or equal to the sum of the lengths of a thrust bearing and a pressure sensor.

[0036] In this embodiment, the first section of a housing cavity supports a threaded sleeve, while a stepped surface formed between the first and second sections of the housing cavity supports the threaded sleeve to limit its axial displacement. The annular stepped surface also prevents interference with a rotating lead screw. The second section of the housing cavity houses a thrust bearing and a pressure sensor.

[0037] In one implementation, the axial accommodation cavity along one lead screw includes a third section, the third section being connected to the first section via the second section, wherein:

[0038] Along the radial direction of a lead screw, the inner circumferential surface diameter of the third section is smaller than the inner circumferential surface diameter of the second section and larger than the diameter of one end of an output shaft;

[0039] Along the axial direction of a lead screw, the end surface of the third section facing the lead screw is used to abut against an outer surface of a pressure sensor.

[0040] In this implementation, another step surface formed between the second section and the third section of a accommodating cavity is used to support an outer surface of a pressure sensor, and the other step surface is used to limit the axial displacement of a pressure sensor and bear the axial thrust transmitted to a pressure sensor by a screw.

[0041] In one implementation, an axial thrust bearing along a lead screw includes two opposite side surfaces, one of which is configured to fit an end surface of the lead screw, and the other is configured to fit another outer surface of a pressure sensor, wherein:

[0042] The outer diameter of one side face is less than or equal to the outer diameter of one end face;

[0043] The outer diameter of the other side surface is smaller than or equal to the outer diameter of the other outer surface.

[0044] In this implementation, the two side surfaces of a thrust bearing are completely fitted with an end face of a lead screw and the other outer surface of a pressure sensor, respectively, which can improve the stress condition of a pressure sensor and ensure that a pressure sensor works reliably.

[0045] In one implementation, one end of an output shaft passes through the wall of the accommodating cavity along the axial direction of a lead screw and is located in the accommodating cavity, wherein:

[0046] An outer peripheral surface of one end of an output shaft includes at least one radial groove, and the at least one radial groove is used to be embedded in an axial groove or an axial protrusion;

[0047] In this embodiment, one end of an output shaft is adapted to be embedded in an axial groove or an axial protrusion. Providing at least one radial groove on the outer circumference of one end of the output shaft can control the outer circumference diameter of one end of the output shaft, thereby controlling the volume of the structure embedded between a lead screw and one end of the output shaft.

[0048] In one implementation, the inner circumferential surface of one end of an output shaft includes at least one radial protrusion, and the at least one radial protrusion is used to be nested in an axial protrusion.

[0049] In this embodiment, an axial protrusion is used to embed one end of an output shaft. At least one radial protrusion is provided on the inner circumference of one end of an output shaft to control the outer circumference diameter of the axial protrusion, thereby controlling the volume of the structure embedded between a screw and one end of an output shaft.

[0050] In one implementation, a ball screw includes a piston, a piston portion being received in a receiving cavity, wherein:

[0051] Along the axial direction of a lead screw and toward a reducer, a piston and a threaded sleeve are arranged in sequence;

[0052] A piston includes a groove, a notch of the groove facing a speed reducer along the axial direction of a lead screw, and the groove is used to partially accommodate a lead screw;

[0053] Along the axial direction of a screw, the sum of the groove depth of a groove and the length of a screw sleeve is greater than or equal to the length of a screw.

[0054] In this implementation, a piston abuts a threaded sleeve along the axial direction of a lead screw to transmit braking force. The bottom of a piston groove extends into a receiving cavity and abuts a friction plate, thereby driving the friction plate toward the wheel's brake disc, achieving braking. The piston groove's relatively large bottom area ensures reliable transmission of braking force.

[0055] In one implementation, a reducer includes a planetary gear set, and the other end of an output shaft includes at least one shaft hole, the at least one shaft hole is used to fix at least one transmission shaft, and the at least one transmission shaft is used to drive and connect at least one planetary gear of a planetary gear set, wherein:

[0056] Along the axial direction of a lead screw, a planetary gear set is arranged on a side of an output shaft away from the lead screw;

[0057] Along the radial direction of a lead screw, the diameter of the other end of an output shaft is larger than the diameter of one end, and the axis of each shaft hole in at least one shaft hole is offset from the axis of a lead screw.

[0058] In this implementation, the other end of an output shaft is connected to a planetary gear set of a speed reducer. The other end of one of the output shafts is connected to at least one planetary gear of a planetary gear set, eliminating the need for a planetary carrier in the planetary gear set. The output shaft can directly output braking force through at least one planetary gear, thereby reducing the axial size of the speed reducer.

[0059] In one implementation, a planetary gear set includes a sun gear, which is used for driving connection with at least one planet gear, wherein:

[0060] Along the axial direction of a lead screw, a sun gear is arranged at intervals on a side of an output shaft away from a lead screw;

[0061] The other end of an output shaft includes a bearing receiving groove, and a notch of the bearing receiving groove is away from the lead screw along the axial direction of the lead screw;

[0062] A bearing receiving groove is used to fix the outer ring of a bearing, and an inner ring of a bearing is used to fix the transmission shaft of a sun gear.

[0063] In this implementation, because the axial hole at the other end of an output shaft is offset relative to the axis of a lead screw, the space at the other end of the output shaft along the lead screw axis can be used to secure the outer ring of a bearing, which in turn secures the drive shaft of a sun gear in a planetary gear set via the inner ring of the bearing. The relatively compact structure of the output shaft and the planetary gear set facilitates reducing the axial dimensions of the reducer.

[0064] In one implementation, along the axial direction of a lead screw, a brake caliper and a reducer housing include two side walls fixedly attached, each side wall includes a clearance hole, and both clearance holes are used to allow an output shaft to pass through, wherein:

[0065] Along the radial direction of a lead screw, the diameter of one avoidance hole is larger than the diameter of the other avoidance hole;

[0066] The inner circumference of one avoidance hole is used for fixing the outer ring of another bearing, and the inner ring of the other bearing is used for fixing the middle section of an output shaft.

[0067] In this implementation, the outer ring of another bearing is fixed using the avoidance hole of a brake caliper or the avoidance hole of a reducer housing, and the inner ring of another bearing is used to support the middle section of an output shaft, so that a reliable support structure can be formed for an output shaft to ensure that an output shaft drives a screw to rotate smoothly.

[0068] In one implementation, the electromechanical brake device includes a brake motor, a reducer for transmission connection between the brake motor and a ball screw, wherein:

[0069] Along the axial direction of a lead screw, a brake motor and a brake caliper are arranged on the same side of a reducer;

[0070] A brake caliper includes a receiving groove, which is spaced apart from a ball screw along the radial direction of a screw and is used to partially receive a brake motor.

[0071] In this implementation, a brake motor and a brake caliper are arranged on the same side of a reducer, which can shorten the axial dimension of the electronic mechanical brake device of the present application. The axial dimension of the motor is further reduced by partially accommodating the brake motor in a receiving groove of a brake caliper.

[0072] In one implementation, a speed reducer includes a parallel-axis gear set, each including an input shaft and an output shaft. The input shaft and the output shaft are spaced apart along the axial direction of a lead screw. The input shaft is coupled to a motor shaft of a brake motor, while the output shaft is coupled to another input shaft of a planetary gear set.

[0073] In a second aspect, the present application provides a vehicle, comprising wheels, and an electromechanical braking device provided by any of the above implementations, wherein:

[0074] The axis of a lead screw in the electromechanical brake device is parallel to the axis of the wheel;

[0075] A brake caliper of the electromechanical brake device is located closer to the wheel than a speed reducer in the axial direction of the wheel;

[0076] A screw sleeve in the electronic mechanical brake device is used to drive one or more friction plates to slide along the axial direction of the wheel to brake the brake disc of the wheel.

[0077] Because the electronic mechanical brake device provided in the first aspect of the present application has a shorter axial dimension, the vehicle provided in the second aspect of the present application also facilitates the arrangement of wheel side space, thereby obtaining a larger internal space or a more compact structure. BRIEF DESCRIPTION OF THE DRAWINGS

[0078] In order to more clearly illustrate the technical solution of the present application, the following is a brief introduction to the drawings required for use in the implementation. Obviously, the drawings described below are only some implementation methods of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work.

[0079] Figure 1 A schematic diagram of the appearance of the vehicle at the wheel provided in an embodiment of the present application;

[0080] Figure 2 A schematic diagram of the cross-sectional structure of a vehicle at a wheel provided in an embodiment of the present application;

[0081] Figure 3 A schematic diagram of the external structure of the electromechanical brake device provided in an embodiment of the present application;

[0082] Figure 4 A schematic diagram of the exploded structure of the electromechanical brake device provided in an embodiment of the present application;

[0083] Figure 5 A schematic cross-sectional view of the electromechanical brake device provided in an embodiment of the present application;

[0084] Figure 6A schematic cross-sectional view of the electromechanical brake device provided in an embodiment of the present application;

[0085] Figure 7 A schematic diagram of the external structure of some internal components of the electronic mechanical braking device provided in an embodiment of the present application;

[0086] Figure 8 A schematic diagram of the external structure of some internal components of the electronic mechanical braking device provided in an embodiment of the present application;

[0087] Figure 9 A schematic diagram of a partial cross-sectional structure of some internal components of the electronic mechanical brake device provided in an embodiment of the present application;

[0088] Figure 10 A schematic diagram of the external structure of some internal components of the electronic mechanical braking device provided in an embodiment of the present application;

[0089] Figure 11 A schematic diagram of the external structure of some internal components of the electronic mechanical braking device provided in an embodiment of the present application;

[0090] Figure 12 A schematic diagram of a partial cross-sectional structure of some internal components of the electronic mechanical brake device provided in an embodiment of the present application;

[0091] Figure 13 A schematic diagram of the external structure of some internal components of the electronic mechanical braking device provided in an embodiment of the present application;

[0092] Figure 14 A schematic diagram of the external structure of some internal components of the electronic mechanical braking device provided in an embodiment of the present application;

[0093] Figure 15 A schematic diagram of a partial cross-sectional structure of some internal components of the electronic mechanical brake device provided in an embodiment of the present application;

[0094] Figure 16 A schematic diagram of a partial cross-sectional structure of some internal components of the electronic mechanical brake device provided in an embodiment of the present application;

[0095] Figure 17 A partially enlarged structural diagram of a brake caliper of an electromechanical brake device provided in an embodiment of the present application;

[0096] Figure 18 A partially enlarged structural diagram of some internal components of the electromechanical brake device provided in an embodiment of the present application;

[0097] Figure 19 A schematic diagram of the external structure of the output shaft of the reducer of the electronic mechanical brake device provided in an embodiment of the present application;

[0098] Figure 20 A schematic diagram of the partial structure of a ball screw of an electronic mechanical brake device provided in an embodiment of the present application;

[0099] Figure 21 A schematic diagram of the external structure of the output shaft of the reducer of the electronic mechanical brake device provided in an embodiment of the present application;

[0100] Figure 22 A schematic diagram of the partial structure of a ball screw of an electronic mechanical brake device provided in an embodiment of the present application;

[0101] Figure 23 A schematic diagram of the external structure of the output shaft of the reducer of the electronic mechanical brake device provided in an embodiment of the present application;

[0102] Figure 24 A schematic diagram of the partial structure of a ball screw of an electronic mechanical brake device provided in an embodiment of the present application;

[0103] Figure 25 A partially enlarged structural diagram of some internal components of the electromechanical brake device provided in an embodiment of the present application;

[0104] Figure 26 A schematic diagram of the external structure of the piston of the ball screw of the electronic mechanical brake device provided in an embodiment of the present application;

[0105] Figure 27 A schematic structural diagram of the internal components of a reducer of an electromechanical brake device provided in an embodiment of the present application;

[0106] Figure 28 A schematic diagram of the exploded structure of the internal components of the reducer of the electromechanical brake device provided in an embodiment of the present application;

[0107] Figure 29 A partially enlarged structural diagram of some internal components of the electromechanical brake device provided in an embodiment of the present application;

[0108] Figure 30 A partially enlarged structural diagram of some internal components of the electromechanical brake device provided in an embodiment of the present application;

[0109] Figure 31 Schematic diagram of the transmission structure of the reducer and brake motor of the electronic mechanical braking device provided in an embodiment of the present application. DETAILED DESCRIPTION

[0110] The following will describe the technical solutions in the embodiments of this application in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of this application, not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by ordinary technicians in this field without making any creative work are within the scope of protection of this application.

[0111] The serial numbers assigned to the components herein, such as "first", "second", etc., are only used to distinguish the objects described and do not have any order or technical meaning. The "connection" mentioned in this application includes direct and indirect connections unless otherwise specified. In the description of this application, it should be understood that the orientation or position relationship indicated by the terms "upper", "lower", "front", "back", "top", "bottom", "inside", "outside", etc. is based on the orientation or position relationship shown in the accompanying drawings, and is only for the convenience of describing this application and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operate in a specific orientation, and therefore cannot be understood as a limitation on this application.

[0112] In this application, unless otherwise expressly specified or limited, when a first feature is "above" or "below" a second feature, it can mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediary. Furthermore, when a first feature is "above" or "above" a second feature, it can mean that the first feature is directly above or diagonally above the second feature, or simply means that the first feature is at a higher level than the second feature. When a first feature is "below" or "below" a second feature, it can mean that the first feature is directly below or diagonally below the second feature, or simply means that the first feature is at a lower level than the second feature.

[0113] The present application provides an electronic mechanical brake device in which a lead screw and an output shaft are embedded. The electronic mechanical brake device includes a brake caliper, a ball screw, and a reducer. The ball screw includes a lead screw and a screw sleeve. The reducer includes an output shaft. One end of the output shaft is used to drive a lead screw to rotate. The screw sleeve is used to move along the axial direction of the lead screw as the lead screw rotates. The brake caliper is used to fix the reducer and to accommodate the lead screw and the screw sleeve. An end face of the lead screw faces the reducer along the axial direction of the lead screw. The end face includes:

[0114] An axial groove, one end of an output shaft is used to be embedded in an axial groove along the axial direction of the screw, and the axial groove is used to drive and connect one end of an output shaft; or,

[0115] An axial protrusion is used to be embedded in or nested in one end of an output shaft along the axial direction of a screw, and an axial protrusion is used to drive and connect one end of an output shaft.

[0116] The electronic mechanical device of the present application is embedded with a lead screw through an output shaft, which compresses the axial length of the electronic mechanical brake device, is conducive to the miniaturization of the electronic mechanical brake device, and is easy to adapt to the wheel side space.

[0117] The present application provides a vehicle, comprising wheels and the above-mentioned electromechanical braking device, wherein:

[0118] The axis of a lead screw in the electromechanical brake device is parallel to the axis of the wheel;

[0119] A brake caliper of the electromechanical brake device is located closer to the wheel than a speed reducer in the axial direction of the wheel;

[0120] A screw sleeve in the electronic mechanical brake device is used to drive one or more friction plates to slide along the axial direction of the wheel to brake the brake disc of the wheel.

[0121] The vehicle of the present application facilitates the arrangement of wheel side space, thereby obtaining a larger interior space or a more compact structure.

[0122] The vehicle of the present application includes wheels and a frame, wherein the wheels are rotatably connected to the frame to drive the vehicle. The electronic mechanical brake device of the present application is fixed to the frame and located at the wheel, and the electronic mechanical brake device brakes the wheel through the action of its internal structure.

[0123] See Figure 1 ,in Figure 1 This is a schematic diagram of the appearance structure of the vehicle at the wheel provided in an embodiment of the present application.

[0124] like Figure 1 As shown, the wheel 1001 is provided with a brake disc 1002, which is coaxially fixed with the hub of the wheel 1001. The wheel 1001 rotates relative to the frame, and the brake disc 1002 rotates synchronously with the wheel 1001 relative to the frame. Figure 1 In the diagram, the outer diameter of the brake disc 1002 is smaller than the inner diameter of the inner ring of the wheel 1001 , and the brake disc 1002 is accommodated in the inner ring of the wheel 1001 .

[0125] The electronic mechanical brake device 100 provided in the present application, in which the lead screw and the output shaft are embedded, is fixed to the vehicle frame. The electronic mechanical brake device 100 at least partially extends into the inner ring of the wheel 1001 and cooperates with the brake disc 1002 to achieve braking of the wheel 1001.

[0126] For details, please refer to Figure 2 ,in Figure 2 This is a schematic diagram of the cross-sectional structure of the vehicle provided in this application at the wheel.

[0127] like Figure 2As shown, the electronic mechanical brake device 100 of the present application includes a brake caliper 10, a ball screw 20, a speed reducer 30, and a brake motor 40. The axis of the ball screw 20 is parallel to the axis of the wheel 1001. Along the axial direction of the ball screw 20, the brake caliper 10 is closer to the wheel 1001 than the speed reducer 30. The brake caliper 10 is used to fix the speed reducer 30 and to accommodate some components of the ball screw 20. The speed reducer 30 is used to transmit and connect the brake motor 40 and the ball screw 20.

[0128] In this embodiment, the electronic mechanical brake device 100 of the present application further includes a friction plate 51 and a caliper frame 52. Figure 2 In the diagram, there are two friction plates 51, which are arranged on both sides of the brake disc 1002 along the axial direction of the brake disc 1002. The two friction plates 51 face the two opposite outer surfaces of the brake disc 1002 respectively.

[0129] The caliper frame 52 is fixedly connected to the vehicle frame, the brake caliper 10 is slidably connected to the caliper frame 52, and the two friction plates 51 are slidably connected to the caliper frame 52. Along the axial direction of the ball screw 20, the friction plate 51 closer to the ball screw 20 is defined as the first friction plate 511, and the friction plate 51 farther from the ball screw 20 is defined as the second friction plate 512. The first friction plate 511 abuts the ball screw 20, while the second friction plate 512 abuts the brake caliper 10.

[0130] When the electromechanical brake device 100 is in operation, the brake motor 40 outputs a braking force to the reducer 30. The reducer 30 adjusts the speed and torque of the braking force and transmits the adjusted braking force to the ball screw 20. The ball screw 20 converts the braking force input from the reducer 30 into thrust along its own axis, pushing the first friction pad 511 to slide toward the brake disc 1002 until the first friction pad 511 contacts the brake disc 1002. The brake motor 40 continues to output a braking force, which is converted into thrust by the ball screw 20. The first friction pad 511 abuts the brake disc 1002 and pushes the caliper frame 52 of the brake caliper 10 to slide. The brake caliper 10 drives the second friction pad 512 to slide toward the brake disc 1002 until the second friction pad 512 contacts the brake disc 1002. The first friction pad 511 and the second friction pad 512 contact the brake disc 1002 from both sides, generating friction to brake the brake disc 1002, thereby achieving the braking function of the electromechanical brake device 100 of the present application.

[0131] In other embodiments, the number of friction plates 51 can be set to other numbers based on different structures or braking requirements of the wheel 1001. For example, the number of friction plates 51 is one. This application does not impose any particular limitation on this.

[0132] See Figure 3-Figure 6 ,in Figure 3 A schematic diagram of the external structure of the electronic mechanical braking device 100 provided in this application; Figure 4 This is a schematic diagram of the exploded structure of the electronic mechanical braking device 100 provided in this application; Figure 5 A schematic cross-sectional view of the electromechanical brake device 100 provided in this application;

[0133] Figure 6 This is a schematic cross-sectional view of the electronic mechanical braking device 100 provided in this application. Figure 5 and Figure 6 Schematic diagrams showing the cross-sectional structure of the electromechanical brake device 100 at different viewing angles.

[0134] like Figure 3-Figure 6 As shown, the ball screw 20 includes a lead screw 21 and a threaded sleeve 22, and the speed reducer 30 includes an output shaft 31. The brake caliper 10 is configured to accommodate the lead screw 21 and the threaded sleeve 22. The axis of the lead screw 21 coincides with the axis of the output shaft 31. Along the axial direction of the lead screw 21, one end of the output shaft 31 is configured to drive the lead screw 21 to rotate relative to the brake caliper 10, and the threaded sleeve 22 is configured to move axially along the lead screw 21 as the lead screw 21 rotates.

[0135] That is, when the electronic mechanical brake device 100 is in operation, the braking force output by the brake motor 40 drives the output shaft 31 of the reducer 30 to rotate relative to the brake caliper 10, so that the reducer 30 can drive the screw 21 to rotate via the output shaft 31. The screw 21 rotates, driving the threaded sleeve 22 to move axially along the screw 21, so that the two friction plates 51 slide toward each other, thereby braking the brake disc 1002. This achieves the braking function of the electronic mechanical brake device 100 of the present application.

[0136] The electronic mechanical brake device 100 of the present application further includes a return spring 53. The opposite ends of the return spring 53 are respectively used to abut against the first friction plate 511 and the second friction plate 512. During operation of the electronic mechanical brake device 100, the return spring 53 is gradually compressed as the two friction plates 51 slide toward each other. The compressed return spring 53 gradually releases its elastic force as the threaded sleeve 22 moves axially along the lead screw 21 toward the reducer 30, pushing the two friction plates 51 to slide away from the brake disc 1002, thereby releasing the brake applied by the electronic mechanical brake device 100 on the brake disc 1002.

[0137] That is, the setting of the return spring 53 enables the electronic mechanical brake device 100 of the present application to control the relative positions of the two friction plates 51 and the brake disc 1002 through the mutual cooperation between the return spring 53 and the screw sleeve 22, thereby achieving braking or releasing the brake disc 1002, and realizing the braking function and releasing the braking function of the electronic mechanical brake device 100 of the present application.

[0138] exist Figure 4 In the schematic diagram, there are two return springs 53, spaced apart and arranged perpendicular to the arrangement direction of the two friction plates 51. As will be appreciated, the provision of two return springs 53 ensures balanced force on the two friction plates 51, preventing deviation of the friction plates 51 during sliding due to uneven force. This ensures reliable braking of the electronic mechanical brake device 100 of the present application.

[0139] In other embodiments, the number of return springs 53 can also be set to other numbers based on different structures or braking requirements of the wheel 1001. For example, the number of return springs 53 is one. This application does not impose any particular limitation on this.

[0140] For ease of description, the end of the output shaft 31 used to drive the screw 21 to rotate is defined as the first end 31a, and the end of the output shaft 31 axially away from the screw 21 is defined as the second end 31b. One end face of each screw 21 faces one reducer 30 along the axial direction of the screw 21. The end face of the screw 21 axially facing the reducer 30 is defined as the first end face 21a, and the end face of the screw 21 axially away from the reducer 30 is defined as the second end face 21b.

[0141] In one embodiment, a brake caliper 10 includes a receiving chamber 11 for receiving a threaded sleeve 22 and a lead screw 21. The output shaft 31 and the lead screw 21 are transmission-connected via a matching structure between the first end 31a and the first end surface 21a.

[0142] For example, in one embodiment, the first end surface 21a includes an axial protrusion 211 (see Figure 7 ), an axial protrusion 211 is used to be embedded in one end (ie, the first end 31a) of an output shaft 31 along the axial direction of a screw 21, and an axial protrusion 211 is used to drively connect the first end 31a of an output shaft 31.

[0143] In another embodiment, the first end surface 21a includes an axial protrusion 211 (see Figure 10 ), an axial protrusion 211 is used to nest the first end 31a of an output shaft 31 along the axial direction of a screw 21, and an axial protrusion 211 is used to transmission connect the first end 31a of an output shaft 31.

[0144] In another embodiment, the first end surface 21a includes an axial groove 213 (see Figure 15 ), a first end 31a of an output shaft 31 is used to be embedded in an axial groove 213 along the axial direction of a screw 21, and an axial groove 213 is used to transmit and connect the first end 31a of an output shaft 31.

[0145] For details, please refer to Figure 7-Figure 9 ,in Figure 7 Schematic diagram of the external structure of some components inside the electronic mechanical brake device 100. Figure 8 Schematic diagram of the external structure of some components inside the electronic mechanical brake device 100. Figure 9 Schematic diagram of a partial cross-sectional structure of some components inside the electronic mechanical brake device 100.

[0146] In one embodiment, if Figure 7-Figure 9 As shown, along the radial direction of the lead screw 21, the diameter of the axial protrusion 211 is smaller than the diameter of the first end 31a of the output shaft 31. The first end 31a includes an axial mating groove 311, the notch of which faces the lead screw 21 along the axial direction of the lead screw 21. Axially, the axial protrusion 211 extends out of the accommodating cavity 11 and into the axial mating groove 311, thereby achieving a transmission connection between the lead screw 21 and the output shaft 31 and ensuring coaxial transmission between the lead screw 21 and the output shaft 31.

[0147] Specifically, the outer circumferential surface of the axial protrusion 211 and the groove wall of the axial mating groove 311 are both provided with mutually matching connection structures, so that the axial protrusion 211 can be embedded in the groove wall of the axial mating groove 311 along the radial direction of the screw 21, and the structure of the axial protrusion 211 embedded in the axial mating groove 311 can be circumferentially engaged with the structure within the axial mating groove 311, thereby realizing circumferential transmission between the axial protrusion 211 and the axial mating groove 311. For example, the connection between the axial protrusion 211 and the axial mating groove 311 can be achieved using a flat key or a spline.

[0148] That is, the mutual cooperation between the axial protrusion 211 and the axial matching groove 311 enables the braking force output by the brake motor 40 to be transmitted to the screw 21 through the output shaft 31 of the reducer 30 during the operation of the electronic mechanical brake device 100, and causes the screw 21 to rotate.

[0149] It can be understood that the mutual cooperation between the axial protrusion 211 and the axial matching groove 311 can reduce the axial space required for the transmission connection between the screw 21 and the output shaft 31 while realizing the transmission connection between the screw 21 and the output shaft 31, thereby compressing the axial length of the electronic mechanical brake device 100, which is conducive to the miniaturization of the electronic mechanical brake device 100 of the present application.

[0150] In another embodiment, the first end face 21a includes an axial protrusion 211, an axial protrusion 211 is used to nest the first end 31a of an output shaft 31 along the axial direction of a screw 21, and an axial protrusion 211 is used to transmission connect the first end 31a of an output shaft 31.

[0151] For details, please refer to Figure 10-12 ,in Figure 10 Schematic diagram of the external structure of some components inside the electronic mechanical brake device 100. Figure 11 Schematic diagram of the external structure of some components inside the electronic mechanical brake device 100. Figure 12 Schematic diagram of a partial cross-sectional structure of some components inside the electronic mechanical brake device 100.

[0152] like Figure 10-12 As shown, along the radial direction of the screw 21, the diameter of the axial protrusion 211 is greater than the diameter of the first end 31a of the output shaft 31. The axial protrusion 211 includes an axial receiving groove 212, the notch of which faces the reducer 30 along the axial direction of the screw 21. The first end 31a of the output shaft 31 is configured to extend into the axial receiving groove 212 along the axial direction of the screw 21, thereby achieving a transmission connection between the screw 21 and the output shaft 31 and ensuring coaxial transmission between the screw 21 and the output shaft 31.

[0153] Specifically, the groove wall of the axial receiving groove 212 and the outer circumferential surface of the first end 31a of the output shaft 31 are both provided with mutually matching connection structures, so that the first end 31a of the output shaft 31 can be embedded in the groove wall of the axial receiving groove 212 along the radial direction of the screw 21, and the structure of the first end 31a embedded in the axial receiving groove 212 can be circumferentially engaged with the structure within the axial receiving groove 212, thereby realizing circumferential transmission between the axial protrusion 211 and the first end 31a of the output shaft 31. For example, the connection between the axial protrusion 211 and the first end 31a of the output shaft 31 can be achieved using a flat key or a spline.

[0154] That is, the axial receiving groove 212 cooperates with the first end 31a of the output shaft 31 so that during the operation of the electronic mechanical brake device 100, the braking force output by the brake motor 40 can be transmitted to the screw 21 through the output shaft 31 of the reducer 30, causing the screw 21 to rotate.

[0155] Compared to the structure of the axial protrusion 211 employed in the previous embodiment, the provision of the axial receiving groove 212 on the axial protrusion 211 in this embodiment allows the first end 31a of the output shaft 31 to partially extend into the accommodating cavity 11 by extending into the axial receiving groove 212. This reduces the space occupied by the axial protrusion 211 outside the brake caliper 10, further reducing the axial space required for the transmission connection between the lead screw 21 and the output shaft 31, and further compressing the axial length of the electronic mechanical brake device 100, thereby facilitating the miniaturization of the electronic mechanical brake device 100 of this application.

[0156] In another embodiment, the first end face 21a includes an axial groove 213, and the first end 31a of an output shaft 31 is used to be embedded in an axial groove 213 along the axial direction of the screw 21, and the axial groove 213 is used to drively connect the first end 31a of an output shaft 31.

[0157] For details, please refer to Figure 13-15 ,in Figure 13 Schematic diagram of the external structure of some components inside the electronic mechanical brake device 100. Figure 14 Schematic diagram of the external structure of some components inside the electronic mechanical brake device 100. Figure 15 Schematic diagram of a partial cross-sectional structure of some components inside the electronic mechanical brake device 100.

[0158] like Figure 13-15 As shown, the notch of the axial groove 213 is oriented toward the reducer 30 along the axial direction of the lead screw 21. The first end 31a of the output shaft 31 of the reducer 30 penetrates the wall of the accommodating cavity 11 and extends into the accommodating cavity 11. It also extends into the axial groove 213 to be embedded with the lead screw 21. This realizes the transmission connection between the lead screw 21 and the output shaft 31, and enables the lead screw 21 and the output shaft 31 to drive coaxially.

[0159] Specifically, the groove wall of the axial groove 213 and the outer circumferential surface of the first end 31a of the output shaft 31 are both provided with mutually matching connection structures, so that the first end 31a of the output shaft 31 can be embedded in the groove wall of the axial groove 213 along the radial direction of the screw 21, and the structure of the first end 31a embedded in the axial groove 213 can be circumferentially engaged with the structure within the axial groove 213, thereby realizing circumferential transmission between the axial groove 213 and the first end 31a of the output shaft 31. Exemplarily, the connection between the axial groove 213 and the first end 31a of the output shaft 31 can be achieved using a flat key or a spline.

[0160] That is, the axial groove 213 cooperates with the first end 31a of the output shaft 31 so that during the operation of the electronic mechanical brake device 100, the braking force output by the brake motor 40 can be transmitted to the screw 21 through the output shaft 31 of the reducer 30, causing the screw 21 to rotate.

[0161] Because the lead screw 21 is housed within the accommodating cavity 11, compared to the structure of the axial protrusion 211 employed in the previous embodiment, it is understood that the provision of the axial groove 213 on the first end face 21a of the lead screw 21 allows the first end 31a of the output shaft 31 to fully extend into the accommodating cavity 11, allowing the output shaft 31 and the lead screw 21 to be embedded within the brake caliper 10. This further reduces the axial space required for the transmission connection between the lead screw 21 and the output shaft 31. This further compresses the axial length of the electronic mechanical brake device 100, facilitating the miniaturization of the electronic mechanical brake device 100 of the present application.

[0162] On the other hand, the first end 31a of the output shaft 31 is embedded in the axial groove 213, and the second end 31b of the output shaft 31 is used for transmission connection to the internal components of the reducer 30. The first end 31a of the output shaft 31 is embedded in the screw 21, so that the first end 31a and the screw 21 are coaxially fixed, which facilitates the coaxial fixation of the second end 31b with the internal gear of the reducer 30, or facilitates the second end 31b to be directly constructed as the internal structure of the reducer 30 (such as Figure 28 The planetary carrier is provided so that the reducer 30 can directly output the braking force through the output shaft 31. That is, the output shaft 31 is embedded in the axial groove 213, which simplifies the transmission structure between the output shaft 31 and the internal structure of the reducer 30 and facilitates the reduction of the axial size of the reducer 30.

[0163] Correspondingly, the vehicle of the present application also adopts the above-mentioned electronic mechanical braking device 100, so that the electronic mechanical braking device 100 of the present application can be easily adapted to the wheel side space of the vehicle, which is conducive to making the structure of the vehicle of the present application compact.

[0164] In this embodiment, during operation of the electronic mechanical brake device 100, when the lead screw 21 rotates relative to the brake caliper 10, the threaded sleeve 22 can move along the axis of the lead screw 21. Specifically, when the lead screw 21 rotates in a rotational direction about its own axis, the threaded sleeve 22 can move away from the reducer 30, pushing the two friction plates 51 to slide toward each other, thereby braking the brake disc 1002 and achieving the braking function of the electronic mechanical brake device 100.

[0165] Correspondingly, when the screw 21 rotates around its own axis in a direction opposite to the above-mentioned rotation direction, the sleeve 22 can move toward the direction of the reducer 30, so that the two friction plates 51 can move in the direction away from the brake disc 1002 under the action of the compressed return spring 53, so that the friction plates 51 release the brake disc 1002, thereby releasing the braking of the brake disc 1002 by the electronic mechanical braking device 100.

[0166] That is, the screw sleeve 22 cooperates with the lead screw 21 so that the screw sleeve 22 can move toward or away from the reducer 30 based on the different rotation directions of the lead screw 21, so as to cooperate with the friction plate 51 to brake or release the brake disc 1002. For example, in one embodiment, the threads on the inner circumference of one screw sleeve 22 are used to engage the threads on the outer circumference of one lead screw 21.

[0167] For details, please refer to Figure 16 ,in Figure 16 FIG. 1 is a schematic diagram of a partial cross-sectional structure of the electromechanical brake device 100 .

[0168] like Figure 16 As shown, the axis of the screw sleeve 22 coincides with the axis of the lead screw 21. The screw sleeve 22 is sleeved on the periphery of the lead screw 21 and meshes with the lead screw 21 for transmission. It is understandable that when the lead screw 21 rotates relative to the brake caliper 10, the screw sleeve 22 can slide along the axial direction of the lead screw 21 based on the mutual meshing of the threads on the outer circumference of the lead screw 21 and the threads on the inner circumference of the screw sleeve 22, and the screw sleeve 22 can have different movement directions based on the rotation direction of the lead screw 21. This ensures the braking function of the electronic mechanical brake device 100 of the present application.

[0169] On the other hand, the screw sleeve 22 is sleeved on the periphery of the lead screw 21, which can also reduce the axial space of the electronic mechanical brake device 100 of the present application occupied by the screw sleeve 22, compress the axial length of the electronic mechanical brake device 100, and is conducive to miniaturization of the electronic mechanical brake device 100.

[0170] The ball screw 20 further includes balls 23. In the radial direction of the screw 21, the balls 23 are located between the screw 21 and the sleeve 22. Specifically, Figure 16 As shown, there are multiple balls 23, each of which is spaced apart and arranged around the thread line of the sleeve 22 along the circumference of the screw 21. It will be appreciated that the arrangement of the balls 23 between the sleeve 22 and the screw 21 can reduce friction between the sleeve 22 and the screw 21 and improve the transmission accuracy between the sleeve 22 and the screw 21. This improves the efficiency of the ball screw 20 in converting braking force into thrust, thereby enhancing the braking efficiency and braking accuracy of the electronic mechanical brake device 100 of the present application.

[0171] Along the radial direction of the lead screw 21, the outer circumferential surface of the sleeve 22 is used to abut the inner circumferential surface of the accommodating chamber 11 to limit the radial position of the sleeve 22. Based on the meshing transmission of the outer circumferential surface of the lead screw 21 and the inner circumferential surface of the sleeve 22. It can be understood that the definition of the radial position of the sleeve 22 also defines the radial position of the lead screw 21, avoiding the possibility of collision between the lead screw 21 and the sleeve 22 due to radial movement during rotation, thereby ensuring smooth transmission between the lead screw 21 and the sleeve 22, and improving the braking efficiency of the electronic mechanical brake device 100 of the present application.

[0172] In one embodiment, the lead angles of the threads on the outer circumferential surface of the lead screw 21 and the threads on the inner circumferential surface of the threaded sleeve 22 are both less than or equal to the friction angle between the lead screw 21 and the threaded sleeve 22. In other words, the lead screw 21 and the threaded sleeve 22 can be self-locked along the axial direction of the lead screw 21 to prevent the elastic force within the compressed return spring 53 from driving the threaded sleeve 22 toward the reducer 30, thereby ensuring reliable braking of the electronic mechanical brake device 100 of the present application.

[0173] In one embodiment, the electronic mechanical brake device 100 of the present application further includes a pressure sensor 61. The axis of the pressure sensor 61 coincides with the axis of the lead screw 21. Along the axial direction of the lead screw 21, the pressure sensor 61 is arranged between the end surface of the lead screw 21 facing the reducer 30 and the wall of the accommodating chamber 11. The pressure sensor 61 is used to detect the braking force applied to the lead screw 21 during operation of the electronic mechanical brake device 100.

[0174] The pressure sensor 61 is also electrically connected to a drive circuit (not shown). During operation of the electromechanical brake device 100, the braking force output by the brake motor 40 is transmitted to the friction plate 51 via the reducer 30 and the ball screw 20. The force is then transmitted by the screw 21 to the pressure sensor 61 and detected by the pressure sensor 61. The pressure sensor 61 transmits the acquired braking force signal to the drive circuit. The drive circuit adjusts the output torque of the brake motor 40 based on the signal input by the pressure sensor 61, thereby adjusting the braking force output by the brake motor 40.

[0175] On the other hand, during operation of the electronic mechanical brake device 100, while the threaded sleeve 22 pushes the friction plates 51 toward each other, the return spring 53 between the two friction plates 51 applies an axial thrust to the threaded sleeve 22. This axial thrust prevents the friction plates 51 from contacting the brake disc 1002. Due to the axial self-locking between the threaded sleeve 22 and the lead screw 21, it is understood that during operation of the electronic mechanical brake device 100, the pressure sensor 61 can also detect the elastic force provided by the return spring 53. This elastic force, combined with the braking force transmitted by the lead screw 21, enables detection of the thrust acting on the friction plates 51.

[0176] In other words, the provision of the pressure sensor 61 enables real-time detection of the braking process, avoiding a mismatch between the braking force output by the brake motor 40 and the actual braking effect. This enables the power feedback function of the electronic mechanical brake device 100 of the present application, further ensuring the braking reliability of the electronic mechanical brake device 100 of the present application.

[0177] In one embodiment, the electronic mechanical brake device 100 of the present application further includes a thrust bearing 62, the axis of which coincides with the axis of the lead screw 21. Along the axial direction of the lead screw 21, the thrust bearing 62 is arranged between the end surface of the lead screw 21 facing the reducer 30 and the wall of the accommodating chamber 11. The thrust bearing 62 is sleeved around the periphery of the lead screw 21 to support the lead screw 21.

[0178] The thrust bearing 62 can also bear the axial thrust exerted on the lead screw 21, thereby ensuring that the output shaft 31 drives the lead screw 21 to rotate smoothly, thereby ensuring reliable braking of the electronic mechanical brake device 100 of the present application.

[0179] In one embodiment, the electronic mechanical brake device 100 of the present application includes both a pressure sensor 61 and a thrust bearing 62. Along the axial direction of the lead screw 21, the pressure sensor 61 and the thrust bearing 62 are arranged between the end surface of the lead screw 21 facing the reducer 30 and the wall of the accommodating chamber 11. As will be appreciated, the interaction between the pressure sensor 61 and the thrust bearing 62 further enhances the braking reliability of the electronic mechanical brake device 100 of the present application.

[0180] Specifically, in one embodiment, the first end surface 21a includes an axial protrusion 211. In the radial direction of the lead screw 21, the diameter of the axial protrusion 211 is smaller than the inner diameter of the threaded sleeve 22. A thrust bearing 62 and a pressure sensor 61 are sequentially sleeved on the axial protrusion 211 along the axial direction of the lead screw 21 and toward the reducer 30.

[0181] For example, Figure 7-12 As shown, since the axial protrusion 211 is used for transmission connection with the first end 31a of the output shaft 31, it is understandable that providing the axial protrusion 211 with a diameter smaller than the inner diameter of the screw sleeve 22 can reduce the radial space of the axial protrusion 211 while ensuring the transmission connection between the axial protrusion 211 and the first end 31a of the output shaft 31, thereby controlling the volume of the structure embedded between the axial protrusion 211 and the first end 31a of the output shaft 31. This can thereby reduce the overall volume of the electronic mechanical brake device 100 of the present application.

[0182] On the other hand, along the axial direction of the lead screw 21, the thrust bearing 62 is held between the first end face 21a of the lead screw 21 and the pressure sensor 61, so that the axial thrust exerted on the lead screw 21 can be transmitted to the thrust bearing 62 and, via the thrust bearing 62, to the pressure sensor 61. The pressure sensor 61 detects the axial thrust transmitted via the thrust bearing 62 and transmits a corresponding signal to the drive circuit to regulate the braking force output by the brake motor 40, thereby achieving control of the braking force of the electronic mechanical brake device 100 of the present application.

[0183] It is understood that the thrust bearing 62 is held between the first end face 21a of the lead screw 21 and the pressure sensor 61. This ensures smooth rotation of the lead screw 21, allowing the thrust bearing 62 to block the transmission path of the rotational torque of the lead screw 21 to the pressure sensor 61. This allows the pressure sensor 61 to remain stationary relative to the brake caliper 10 during operation of the electronic mechanical brake device 100, preventing the rotational torque of the lead screw 21 from affecting the pressure sensor 61's ability to detect the axial thrust of the lead screw 21. This ensures the detection accuracy of the pressure sensor 61 and improves the braking efficiency of the electronic mechanical brake device 100 of this application.

[0184] In one embodiment, along the radial direction of a screw 21 , the diameter of an output shaft 31 is larger than the diameter of an axial protrusion 211 , and the inner hole of a thrust bearing 62 and the inner hole of a pressure sensor 61 are respectively used to support the outer peripheral surface of an output shaft 31 .

[0185] Among them, such as Figure 7-Figure 9 As shown, the diameter of the output shaft 31 is set to the diameter of the axial protrusion 211 so that the axial protrusion 211 can be embedded in the first end 31a of the output shaft 31, ensuring a reliable transmission connection between the screw 21 and the output shaft 31.

[0186] On the other hand, the inner hole of the thrust bearing 62 abuts against the outer circumference of the output shaft 31, radially positioning the thrust bearing 62 and aligning the axis of the thrust bearing 62 with the axis of the lead screw 21. This prevents radial movement of the thrust bearing 62 due to external impacts, thereby ensuring smooth rotation of the lead screw 21.

[0187] The inner hole of the pressure sensor 61 abuts against the outer circumference of the output shaft 31, achieving radial positioning of the pressure sensor 61 and aligning the axis of the pressure sensor 61 with the axis of the lead screw 21. This prevents the pressure sensor 61 from radially moving under external impact, which would affect the detection accuracy of the pressure sensor 61.

[0188] In one embodiment, along the radial direction of a screw 21 , the diameter of an axial protrusion 211 is greater than the diameter of an output shaft 31 , and the inner hole of a thrust bearing 62 and the inner hole of a pressure sensor 61 are respectively used to support the outer peripheral surface of an axial protrusion 211 .

[0189] Among them, such as Figure 10-12As shown, the diameter of the output shaft 31 and the diameter of the axial protrusion 211 are configured so that the axial protrusion 211 can nest with the first end 31a of the output shaft 31, ensuring a reliable transmission connection between the lead screw 21 and the output shaft 31. Furthermore, the inner bore of the thrust bearing 62 abuts against the outer circumference of the output shaft 31, radially positioning the thrust bearing 62 and ensuring smooth rotation of the lead screw 21. The inner bore of the pressure sensor 61 abuts against the outer circumference of the output shaft 31, radially positioning the pressure sensor 61 and preventing radial movement of the pressure sensor 61 under external impact, which could affect its detection accuracy.

[0190] In one embodiment, the first end surface 21a of the screw 21 includes an axial groove 213, wherein: along the radial direction of the screw 21, the diameter of the axial groove 213 is smaller than the inner diameter of the threaded sleeve 22. Along the axial direction of the screw 21 and toward the reducer 30, a thrust bearing 62 and a pressure sensor 61 are sequentially sleeved on an output shaft 31. The inner holes of the thrust bearing 62 and the inner holes of the pressure sensor 61 are respectively used to abut the outer circumferential surface of an output shaft 31.

[0191] Specifically, such as Figure 13-15 As shown, since the axial groove 213 is used for transmission connection with the first end 31a of the output shaft 31, it is understandable that providing the axial groove 213 with a diameter smaller than the inner diameter of the screw sleeve 22 can control the volume of the structure embedded between the axial groove 213 and the first end 31a of the output shaft 31 while ensuring the transmission connection between the axial groove 213 and the first end 31a of the output shaft 31.

[0192] Compared to the axial protrusion 211 structure used in other embodiments, in this embodiment, the inner holes of the pressure sensor 61 and the thrust bearing 62 are both abutted against the outer circumferential surface of the output shaft 31. This allows the inner diameters of the pressure sensor 61 and the thrust bearing 62 to be reduced while maintaining radial positioning of the pressure sensor 61 and the thrust bearing 62, thereby reducing their radial dimensions. This facilitates the miniaturization of the electromechanical brake device 100 of this application.

[0193] In one embodiment, along the axial direction of the lead screw 21 , the length of the lead screw 21 is greater than the length of the threaded sleeve 22 .

[0194] Specifically, such as Figure 7-Figure 15As shown, due to the transmission engagement between the screw sleeve 22 and the lead screw 21, the screw sleeve 22 can slide along the axial direction of the lead screw 21 toward or away from the reducer 30 when the lead screw 21 rotates. In addition, since the axis of the screw sleeve 22 coincides with the axis of the lead screw 21. It can be understood that providing the lead screw 21 with an axial length greater than the axial length of the screw sleeve 22 can ensure that during the axial sliding process of the screw sleeve 22, the thread on the inner circumference of the screw sleeve 22 is always engaged with the thread on the outer circumference of the lead screw 21, thereby ensuring the meshing transmission effect between the screw sleeve 22 and the lead screw 21. It is ensured that the braking of the electronic mechanical brake device 100 of the present application is smooth.

[0195] On the other hand, the provision of a screw 21 with a larger axial dimension can reduce the possibility of the screw sleeve 22 being separated from the screw 21 during the axial sliding process, further ensuring the meshing transmission effect between the screw sleeve 22 and the screw 21, thereby ensuring smooth braking of the electronic mechanical brake device 100 of the present application.

[0196] In one embodiment, an accommodating cavity 11 includes a first segment 11a connected along the axial direction of a lead screw 21 (see Figure 17 ) and the second paragraph 11b (see Figure 17 ), the inner circumference of the first section 11a is used to abut the outer circumference of the screw sleeve 22, and the inner circumference of the second section 11b is used to abut the outer circumference of the pressure sensor 61, wherein: along the radial direction of a screw 21, the inner circumference diameter of the second section 11b is smaller than the inner circumference diameter of the first section 11a and larger than the inner diameter of a screw sleeve 22; along the axial direction of a screw 21, the length of the second section 11b is less than or equal to the sum of the lengths of a thrust bearing 62 and a pressure sensor 61.

[0197] For details, please refer to Figure 17 ,in Figure 17 FIG1 is a partial enlarged structural diagram of the brake caliper 10 of the electronic mechanical brake device 100. Figure 16 .

[0198] like Figure 16 and Figure 17 As shown, the first section 11a of the accommodating chamber 11 is used to support the screw sleeve 22, so that the screw sleeve 22 can slide axially within the first section 11a of the accommodating chamber 11. The inner diameter of the first section 11a is larger than the inner diameter of the second section 11b. The axis of the first section 11a and the axis of the second section 11b both coincide with the axis of the screw 21, so that a first step surface 111 is formed between the first section 11a and the second section 11b. The first step surface 111 is annular and faces away from the reducer 30 along the axial direction of the screw 21.

[0199] Because the inner diameter of the second section 11b is smaller than the inner diameter of the screw sleeve 22, and the outer surface of the screw sleeve 22 abuts the inner surface of the first section 11a, it is understood that the first step surface 111 is used to abut the end surface of the screw sleeve 22 facing the reducer 30, thereby limiting the sliding position of the screw sleeve 22 toward the reducer 30, thereby limiting the axial displacement of the screw sleeve 22. This prevents the screw sleeve 22 from falling off the lead screw 21 during axial sliding, thereby ensuring reliable braking of the electronic mechanical brake device 100 of the present application.

[0200] On the other hand, since the inner diameter of the second section 11b of the annular first stepped surface 111 is larger than the inner diameter of the screw sleeve 22, and the inner circumference of the screw sleeve 22 is used to engage the outer circumference of the transmission screw 21, it can be understood that the size of the second section 11b can also prevent interference between the first stepped surface 111 and the rotating screw 21, thereby ensuring smooth rotation of the screw 21 and ensuring smooth braking of the electronic mechanical brake device 100 of the present application.

[0201] In this embodiment, the second section 11b of the accommodating chamber 11 is used to accommodate the pressure sensor 61 and the thrust bearing 62. Since the threaded sleeve 22 is housed in the first section 11a of the accommodating chamber 11, it is understood that placing the pressure sensor 61 and the thrust bearing 62 within the second section 11b of the accommodating chamber 11 can prevent axial sliding of the threaded sleeve 22 from affecting the pressure sensor 61 and the thrust bearing 62, thereby ensuring the braking efficiency of the electronic mechanical brake device 100 of the present application.

[0202] In one embodiment, the axial accommodating cavity 11 along a screw 21 includes a third section 11c, and the third section 11c is connected to the first section 11a through the second section 11b, wherein: along the radial direction of a screw 21, the inner circumferential diameter of the third section 11c is smaller than the inner circumferential diameter of the second section 11b; along the axial direction of a screw 21, the end face of the third section 11c facing the screw 21 is used to abut an outer surface of a pressure sensor 61.

[0203] Specifically, such as Figure 16 and Figure 17 As shown, the inner diameter of the third section 11c is smaller than the inner diameter of the second section 11b, and the axis of the third section 11c coincides with the axis of the screw 21, so that a second step surface 112 is formed between the second section 11b and the third section 11c. The second step surface 112 is annular and faces away from the reducer 30 along the axial direction of the screw 21.

[0204] The second stepped surface 112 is used to abut the outer surface of the pressure sensor 61. Since the pressure sensor 61 is housed within the second section 11b of the accommodating cavity 11, and the inner diameter of the second section 11b is smaller than that of the second section 11b, the provision of the second stepped surface 112 limits the axial displacement of the pressure sensor 61 and allows the axial thrust transmitted from the lead screw 21 to the pressure sensor 61 to be carried by the second stepped surface 112, thereby ensuring that the pressure sensor 61 effectively detects the axial thrust of the lead screw 21.

[0205] In one embodiment, the first end surface 21 a of the screw 21 includes an axial protrusion 211 . Along the radial direction of the screw 21 , the inner circumferential surface diameter of the third section 11 c is larger than the diameter of the axial protrusion 211 .

[0206] Specifically, such as Figure 7-12 As shown, since the axial protrusion 211 needs to penetrate the wall of the accommodating chamber 11 and is intended to be embedded or nested in the first end 31a of the output shaft 31, it is understood that providing the third section 11c of the accommodating chamber 11 with a larger inner diameter ensures that the axial protrusion 211 can pass through the wall of the accommodating chamber 11 while preventing the axial protrusion 211 from interfering with the third section 11c of the accommodating chamber 11 when rotating with the output shaft 31. This ensures smooth braking of the electronic mechanical brake device 100 of the present application.

[0207] In one embodiment, the first end surface 21a of the screw 21 includes an axial groove 213. In the radial direction of the screw 21, the inner circumferential surface diameter of the third section 11c is larger than the diameter of the first end 31a of the output shaft 31.

[0208] Specifically, such as Figure 13-15 As shown, the first end 31a of the output shaft 31 needs to penetrate the wall of the accommodating chamber 11 and extend into the accommodating chamber 11, where it engages with the axial groove 213. As can be appreciated, providing the third section 11c of the accommodating chamber 11 with a larger inner diameter ensures that the first end 31a of the output shaft 31 can pass through the wall of the accommodating chamber 11 while preventing interference and compression between the output shaft 31 and the third section 11c of the accommodating chamber 11 during rotation. This ensures smooth braking of the electronic mechanical brake device 100 of the present application.

[0209] In one embodiment, the axial thrust bearing 62 along one lead screw 21 includes two opposite side surfaces 621 (see FIG. Figure 18), one side surface 621 is used to fit the first end surface 21a of a screw 21, and the other side surface 621 is used to fit the other outer surface of a pressure sensor 61, wherein: the outer diameter of one side surface 621 is less than or equal to the outer diameter of the first end surface 21a; the outer diameter of the other side surface 621 is less than or equal to the outer diameter of the other outer surface.

[0210] For details, please refer to Figure 18 ,in Figure 18 This is a partially enlarged structural diagram of some components inside the electronic mechanical brake device 100. Figure 9 、 Figure 12 ,as well as Figure 15 .

[0211] like Figure 9 、 Figure 12 、 Figure 15 as well as Figure 18 As shown, along the axial direction of the lead screw 21, two opposing side surfaces 621 of the thrust bearing 62 are defined as a first side surface 621a and a second side surface 621b. The first side surface 621a of the thrust bearing 62 is closer to the first end surface 21a of the lead screw 21 than the second side surface 621b of the thrust bearing 62. That is, the first side surface 621a of the thrust bearing 62 is configured to contact the first end surface 21a of the lead screw 21, while the second side surface 621b of the thrust bearing 62 is configured to contact the outer surface of the pressure sensor 61.

[0212] It can be understood that the size setting of the first side surface 621a of the thrust bearing 62 and the first end surface 21a of the screw 21, as well as the size setting of the second side surface 621b of the thrust bearing 62 and the outer surface of the pressure sensor 61, ensure the transmission effect of the thrust bearing 62 on the axial thrust of the screw 21, and improve the force condition of the pressure sensor 61, so that the axial thrust of the screw 21 can be transmitted to the pressure sensor 61 via the thrust bearing 62, thereby ensuring the reliable operation of the pressure sensor 61.

[0213] In one embodiment, the inner circumferential surface of the first end 31 a of an output shaft 31 includes at least one radial protrusion 312 , and the at least one radial protrusion 312 is configured to be nested in an axial protrusion 211 .

[0214] For details, please refer to Figure 19 and Figure 20 ,in Figure 19 FIG. 1 is a schematic diagram of the external structure of the output shaft 31 of the reducer 30 of the electronic mechanical brake device 100 . Figure 20 FIG. 1 is a partial structural diagram of the ball screw 20 of the electronic mechanical brake device 100. Figure 7-Figure 9 .

[0215] like Figure 7 、 Figure 8 、 Figure 9 、 Figure 19 and Figure 20 As shown, the first end surface 21a of the lead screw 21 includes an axial protrusion 211. The axial protrusion 211 extends through the wall of the accommodating cavity 11 and extends out of the brake caliper 10. The axial protrusion 211 is configured to engage with the first end 31a of the output shaft 31. A radial mating groove 214 is defined on the outer circumference of the axial protrusion 211. The first end 31a of the output shaft 31 is also defined by the axial mating groove 311. A radial protrusion 312 is located on the inner circumference of the axial mating groove 311, forming a structure similar to a flat key or spline.

[0216] exist Figure 19 In the diagram, there are multiple radial protrusions 312, which are spaced apart along the circumference of the screw 21 on the inner circumferential surface of the axial mating groove 311. The number of radial mating grooves 214 is the same as the number of radial protrusions 312, and the arrangement of the radial mating grooves 214 along the circumference of the screw 21 is the same as that of the radial protrusions 312.

[0217] In this embodiment, each radial protrusion 312 is capable of being embedded in a radial mating groove 214 on the outer circumferential surface of the axial protrusion 211, so that the braking force transmitted to the output shaft 31 can be transmitted to the axial protrusion 211 through the mutual engagement between the radial protrusion 312 and the radial mating groove 214. It can be understood that the provision of the radial protrusion 312 reduces the difficulty of coaxial transmission between the axial protrusion 211 and the output shaft 31, allowing the axial protrusion 211 to reduce its own outer circumferential diameter.

[0218] That is, the setting of the radial protrusion 312 realizes the control of the outer peripheral diameter of the axial protrusion 211, thereby realizing the control of the volume of the structure embedded between the screw 21 and the first end 31a of the output shaft 31, so that the radial dimension of the connection structure between the screw 21 and the output shaft 31 is smaller, which is conducive to the miniaturization of the electronic mechanical brake device 100 of the present application.

[0219] It is understandable that in other embodiments, the number of radial protrusions 312 may be set based on the actual transmission requirements between the output shaft 31 and the lead screw 21. For example, the number of radial protrusions 312 is one, which is not particularly limited in this application.

[0220] In one embodiment, the first end 31a of an output shaft 31 passes through the wall of the accommodating cavity 11 along the axial direction of a screw 21 and is located in the accommodating cavity 11, wherein: the outer peripheral surface of the first end 31a of an output shaft 31 includes at least one radial groove 313, and the at least one radial groove 313 is used to be embedded in an axial groove 213 or an axial protrusion 211.

[0221] For example, in one embodiment, please refer to Figure 21 and Figure 22 ,in Figure 21 FIG. 1 is a schematic diagram of the external structure of the output shaft 31 of the reducer 30 of the electronic mechanical brake device 100 . Figure 22 FIG. 1 is a partial structural diagram of the ball screw 20 of the electronic mechanical brake device 100. Figure 10-12 .

[0222] like Figure 10 、 Figure 11 、 Figure 12 、 Figure 21 and Figure 22 As shown, the first end surface 21a of the screw 21 includes an axial protrusion 211, which is configured to nest with the first end 31a of the output shaft 31. An axial receiving groove 212 is defined on the axial protrusion 211. A radially extending inner surface of the axial receiving groove 212 is provided with a radial mating protrusion 215, forming a structure similar to a flat key or spline.

[0223] exist Figure 21 In the diagram, the first end 31a of the output shaft 31 has a plurality of radial grooves 313, which are arranged at intervals along the circumference of the lead screw 21 on the outer circumferential surface of the first end 31a of the output shaft 31. The number of radial mating protrusions 215 is the same as the number of radial grooves 313, and the arrangement of the radial mating protrusions 215 along the circumference of the lead screw 21 is the same as that of the radial grooves 313.

[0224] In this embodiment, each radial mating protrusion 215 is embedded in a radial groove 313, so that the braking force transmitted to the output shaft 31 can be transmitted to the axial protrusion 211 through the mutual engagement between the radial mating protrusion 215 and the radial groove 313. As can be understood, the provision of the radial groove 313 reduces the difficulty of coaxial transmission between the axial protrusion 211 and the output shaft 31, allowing the first end 31a of the output shaft 31 to reduce its own outer circumferential diameter.

[0225] That is, the setting of the radial groove 313 realizes the control of the outer peripheral surface diameter of the first end 31a of the output shaft 31, thereby realizing the control of the volume of the structure embedded between the screw 21 and the first end 31a of the output shaft 31, making the radial dimension of the connection structure between the screw 21 and the output shaft 31 smaller, which is conducive to the miniaturization of the electronic mechanical brake device 100 of the present application.

[0226] In another embodiment, please refer to Figure 23 and Figure 24 ,in Figure 23 FIG. 1 is a schematic diagram of the external structure of the output shaft 31 of the reducer 30 of the electronic mechanical brake device 100 . Figure 24FIG. 1 is a partial structural diagram of the ball screw 20 of the electronic mechanical brake device 100. Figure 13-15 .

[0227] For similar reasons, when the first end face 21a of the screw 21 includes an axial groove 213, the output shaft 31 provided with a radial groove 313 is embedded in the axial groove 213, and each radial mating protrusion 215 on the axial groove 213 is embedded in a radial groove 313, which can also achieve control of the outer circumferential diameter of the first end 31a of the output shaft 31 and control of the volume of the structure embedded between the screw 21 and the first end 31a of the output shaft 31, so that the radial dimension of the connection structure between the screw 21 and the output shaft 31 is smaller, which is conducive to the miniaturization of the electronic mechanical brake device 100 of the present application.

[0228] It is understandable that in other embodiments, the number of radial grooves 313 may be set based on the actual transmission requirements between the output shaft 31 and the lead screw 21. For example, the number of radial grooves 313 is one, which is not particularly limited in this application.

[0229] Therefore, based on the limitations of the above embodiments, the electronic mechanical brake device 100 of the present application utilizes the threaded connection between the lead screw 21 and the screw sleeve 22, so that the braking force output by the brake motor 40 can be transmitted to the lead screw 21 via the reducer 30, so that the lead screw 21 rotates while the screw sleeve 22 slides axially. The braking force is then transmitted to the two friction plates 51 by virtue of the axial sliding of the screw sleeve 22, causing the two friction plates 51 to slide toward the brake disc 1002 and brake the brake disc 1002. Thus, the braking function of the electronic mechanical brake device 100 of the present application is achieved.

[0230] The electronic mechanical brake device 100 of the present application further provides an axial protrusion 211 or an axial groove 213 on the first end surface 21a of the lead screw 21, and allows the first end 31a of the output shaft 31 of the reducer 30 to be embedded in the axial protrusion 211 or the axial groove 213, or the first end 31a of the output shaft 31 of the reducer 30 to be nested in the axial protrusion 211, thereby achieving a transmission connection between the output shaft 31 and the lead screw 21. This reduces the space required for the transmission connection between the output shaft 31 and the lead screw 21, shortens the axial length of the electronic mechanical brake device 100, and facilitates miniaturization of the electronic mechanical brake device 100. This makes the structure of the electronic mechanical brake device 100 of the present application compact.

[0231] The electronic mechanical brake device 100 of the present application reduces the spatial dimensions of the transmission connection between the output shaft 31 and the lead screw 21, thereby reducing the axial dimensions of the electronic mechanical brake device 100 and achieving a compact structure. When the electronic mechanical brake device 100 of the present application is used in a vehicle, it can output a braking force through the brake motor 40, which is applied to the brake disc 1002 via the reducer 30, ball screw 20, brake caliper 10, and friction pad 51, thereby achieving the vehicle's braking function. The compact structure of the electronic mechanical brake device 100 facilitates miniaturization to fit within the wheel space of the vehicle, facilitates the arrangement of internal components near the vehicle's wheel 1001, and controls the overall volume of the vehicle.

[0232] It is understandable that the structure of the electronic mechanical brake device 100 of the present application can also be applied to other usage scenarios. For example, the structure of the electronic mechanical brake device 100 can also be applied to steering systems and machine tools, etc. This application does not impose any particular restrictions on this.

[0233] For the convenience of description, in the subsequent embodiments of this application, Figure 10-12 It is understood that the various limitations in the subsequent embodiments are Figure 7-Figure 9 The illustrated embodiment, and Figure 13-15 The same applies to the illustrated embodiment.

[0234] In one embodiment, a ball screw 20 includes a piston 24, and a piston 24 is partially accommodated in an accommodating chamber 11, wherein: along the axial direction of a screw 21 and toward a reducer 30, a piston 24 and a screw sleeve 22 are arranged in sequence; a piston 24 includes a groove 241, a notch 2411 of a groove 241 is axially facing a reducer 30, and a groove 241 is used to partially accommodate a screw 21; along the axial direction of a screw 21, the sum of the groove depth of a groove 241 and the length of a screw sleeve 22 is greater than or equal to the length of a screw 21.

[0235] For details, please refer to Figure 25 and Figure 26 .in Figure 25 is a partially enlarged structural diagram of some components inside the electronic mechanical brake device 100; Figure 26 Schematic diagram of the external structure of the piston 24 of the ball screw 20 of the electronic mechanical brake device 100.

[0236] like Figure 25 and Figure 26As shown, the axis of the piston 24 coincides with the axis of the lead screw 21. Along the axial direction of the lead screw 21, the piston 24 is located on the side of the threaded sleeve 22 away from the reducer 30. The lead screw 21 partially extends into the groove 241 of the piston 24, causing the threaded sleeve 22, which is sleeved around the outer periphery of the lead screw 21, to abut against the piston 24. The groove bottom 2412 of the piston 24 can extend out of the accommodating chamber 11 and abut against a friction plate 51.

[0237] When the electronic mechanical brake device 100 of the present application is in operation, the braking force output by the brake motor 40 is transmitted to the ball screw 20 via the reducer 30. The threaded connection between the lead screw 21 and the threaded sleeve 22 causes the threaded sleeve 22 to slide away from the reducer 30, thereby pushing the piston 24 to slide axially along the lead screw 21. Under the action of the braking force, the groove bottom 2412 of the piston 24 extends out of the accommodating cavity 11, pushing the friction plate 51 toward the brake disc 1002 of the wheel 1001. This achieves the braking function of the electronic mechanical brake device 100 of the present application.

[0238] In this embodiment, along the axial direction of the lead screw 21, the depth of the groove 241, the length of the screw sleeve 22, and the length of the lead screw 21 are configured such that the second end face 21b of the lead screw 21 extending into the groove 241 is spaced from the groove bottom 2412 of the groove 241, thereby preventing interference between the lead screw 21 and the groove bottom 2412 during rotation. This ensures smooth braking of the electronic mechanical brake device 100 of the present application.

[0239] On the other hand, the dimensions of the groove 241, the threaded sleeve 22, and the lead screw 21 also allow the groove bottom 2412 of the groove 241 to extend out of the accommodating chamber 11 and abut against the friction plate 51. Because the groove bottom 2412 of the groove 241 of the piston 24 has a relatively large area, the area of ​​the piston 24 abutting against the friction plate 51 is also relatively large, thereby improving the stability of the braking force transmitted by the piston 24 to the friction plate 51 and achieving reliable transmission of the braking force by the electronic mechanical brake device 100 of the present application.

[0240] In one embodiment, a speed reducer 30 includes a planetary gear set 32 ​​(see Figure 27 ), the other end (second end 31b) of an output shaft 31 includes at least one shaft hole 314 (see Figure 28 ), at least one shaft hole 314 is used to fix at least one transmission shaft 321 (see Figure 28 ), at least one transmission shaft 321 is used to drive and connect at least one planetary gear 322 of a planetary gear set 32 ​​(see Figure 28), wherein: along the axial direction of a screw 21, a planetary gear set 32 ​​is arranged on the side of an output shaft 31 away from a screw 21; along the radial direction of a screw 21, the diameter of the second end 31b of an output shaft 31 is larger than the diameter of the first end 31a of the output shaft 31, and the axis of each shaft hole 314 in at least one shaft hole 314 is offset from the axis of a screw 21.

[0241] For details, please refer to Figure 27 and Figure 28 .in Figure 27 Schematic diagram of the structure of the internal components of the speed reducer 30 of the electronic mechanical brake device 100; Figure 28 FIG. 1 is a schematic diagram of the exploded structure of some internal components of the retarder 30 of the electromechanical brake device 100 .

[0242] like Figure 27 and Figure 28 As shown, in the embodiment of the present application, the reducer 30 further includes a planetary gear set 32. The planetary gear set 32 ​​is housed in a housing 33 of the reducer. The planetary gear set 32 ​​is rotatable relative to the housing 33 of the reducer. The planetary gear set 32 ​​is used to drive the connection between the brake motor 40 and the output shaft 31.

[0243] When the brake motor 40 outputs a braking force, the braking force is transmitted to the planetary gear set 32. The planetary gear set 32 ​​adjusts the braking torque and speed and transmits the adjusted braking force to the output shaft 31. The output shaft 31 transmits the braking force to the ball screw 20. Under the action of the braking force, the ball screw 20 pushes the two friction plates 51 to brake the brake disc 1002, thereby achieving the braking function of the electronic mechanical brake device 100 of the present application.

[0244] In this embodiment, compared to conventional gear sets, the planetary gear set 32 ​​employed in this application can reduce the size of the reduction mechanism while maintaining the transmission ratio of the reducer 30. It will be appreciated that the placement of the planetary gear set 32 ​​within the reducer 30 can reduce the space occupied by the reducer 30 within the electronic mechanical brake device 100 of this application, thereby reducing the overall size of the electronic mechanical brake device 100 of this application and facilitating the miniaturization of the electronic mechanical brake device 100 of this application.

[0245] On the other hand, compared to conventional gear sets, the planetary gear set 32 ​​employed in the present application also has a larger transmission ratio. Specifically, the arrangement of the planetary gear set 32 ​​within the reducer 30 can also increase the torque transmitted from the reducer 30 to the ball screw 20, thereby increasing the thrust transmitted via the ball screw 20 to the friction plate 51, thereby increasing the braking force of the electronic mechanical brake device 100 of the present application. This, in turn, improves the braking efficiency of the electronic mechanical brake device 100 of the present application.

[0246] In this embodiment, the planetary gear set 32 ​​includes a transmission shaft 321, planetary gears 322, a sun gear 323, and a ring gear 324. The axes of the sun gear 323 and the ring gear 324 coincide with the axis of the lead screw 21. There are multiple planetary gears 322, and the axes of each planetary gear 322 are parallel to the axis of the lead screw 21. Along the axial direction of the lead screw 21, the planetary gear set 32 ​​is located on the side of the output shaft 31 away from the lead screw 21.

[0247] There are multiple transmission shafts 321. One of the transmission shafts 321 is used to coaxially secure the sun gear 323, and the remaining transmission shafts 321 are used to coaxially secure the planetary gears 322. For ease of description, the transmission shaft 321 that coaxially secures the sun gear 323 is defined as the first transmission shaft 321a, and the transmission shaft 321 that coaxially secures the planetary gears 322 is defined as the second transmission shaft 321b. The number of second transmission shafts 321b is equal to the number of planetary gears 322. The axis of the second transmission shaft 321b is parallel to the axis of the lead screw 21, while the axis of the first transmission shaft 321a coincides with the axis of the lead screw 21.

[0248] In this embodiment, a sun gear 323 is arranged on a side of an output shaft 31 away from a lead screw 21 along the axial direction of a lead screw 21. The sun gear 323 is rotatably connected to the second end 31b of the output shaft 31 via a first transmission shaft 321a. The ring gear 324 is coaxially sleeved around the outer periphery of the sun gear 323 and fixed to the housing 33 of the reducer 30. Each planetary gear 322 is used to transmit and connect between the ring gear 324 and the sun gear 323. Each second transmission shaft 321b is coaxially fixed to a planetary gear 322 and fixed in an axial hole 314, so that the second end 31b of the output shaft 31 forms a planetary carrier structure of the planetary gear set 32.

[0249] When the electronic mechanical brake device 100 of the present application is in operation, the braking force output by the brake motor 40 can be transmitted to the sun gear 323 of the planetary gear set 32, causing the sun gear 323 to rotate about the axis of the screw 21. The sun gear 323 transmits the braking force to each planetary gear 322, causing each planetary gear 322 to also rotate about the axis of the screw 21. The rotating planetary gears 322 transmit the braking force to the second end 31b of the output shaft 31, and the output shaft 31 transmits the braking force to the friction plate 51 via the ball screw 20, thereby realizing the braking function of the electronic mechanical brake device 100 of the present application.

[0250] In this embodiment, the electronic mechanical brake device 100 of the present application forms the second end 31b of the output shaft 31 into the planetary carrier structure of the planetary gear set 32, eliminating the planetary carrier structure in the planetary gear set 32. This allows the output shaft 31 to directly output the braking force using the planetary gears 322, thereby reducing the axial size of the reducer 30. This reduces the axial size of the electronic mechanical brake device 100 of the present application, facilitating miniaturization of the electronic mechanical brake device 100 of the present application.

[0251] In one embodiment, the second end 31b of an output shaft 31 includes a bearing receiving groove 315 (see Figure 29 ), a groove of a bearing accommodating groove 315 is away from a screw 21 along the axial direction of a screw 21; a bearing accommodating groove 315 is used to fix the outer ring of a bearing (first bearing 71), and the inner ring of a bearing is used to fix the transmission shaft 321 (first transmission shaft 321a) of a sun gear 323.

[0252] For details, please refer to Figure 29 ,in Figure 29 It is a partial enlarged structural diagram of some components inside the electromechanical brake device 100.

[0253] like Figure 29 As shown, the electronic mechanical brake device 100 of the present application further includes a first bearing 71, which includes an outer ring 711 and an inner ring 712. The outer ring 711 of the first bearing 71 is used to fix the groove wall of the bearing receiving groove 315, and the inner ring 712 of the first bearing 71 is used to fix the first transmission shaft 321a to achieve rotational connection between the sun gear 323 and the output shaft 31 and to define the radial position of the sun gear 323.

[0254] Because the shaft hole 314 on the second end 31b of the output shaft 31 is offset relative to the axis of the lead screw 21, the provision of the bearing receiving groove 315 can be understood to reduce the axial distance between the second end 31b of the output shaft 31 and the sun gear 323, making the structure between the output shaft 31 and the planetary gear set 32 ​​relatively compact, thereby reducing the axial size of the speed reducer 30. This facilitates the miniaturization of the electronic mechanical brake device 100 of the present application.

[0255] In one embodiment, along the axial direction of a screw 21, a brake caliper 10 and a housing 33 of a reducer 30 include two side walls that are fixedly fitted together, each side wall includes a avoidance hole, and both avoidance holes are used to allow an output shaft 31 to pass through, wherein: along the radial direction of a screw 21, the diameter of one avoidance hole is larger than the diameter of the other avoidance hole; the inner circumference of one avoidance hole is used to fix the outer ring of another bearing (i.e., the second bearing 72), and the inner ring of the other bearing is used to fix the middle section of an output shaft 31.

[0256] For ease of description, the two side walls fixedly attached between the brake caliper 10 and the housing 33 of the reducer 30 are defined as the first side wall 12 of the brake caliper 10 and the second side wall 331 of the housing 33 of the reducer 30 .

[0257] For details, please refer to Figure 30 ,in Figure 30 It is a partial enlarged structural diagram of some components inside the electromechanical brake device 100.

[0258] like Figure 30 As shown, the first side wall 12 includes a first avoidance hole 121, and the second side wall 331 includes a second avoidance hole 3311. The axes of the first avoidance hole 121 and the second avoidance hole 3311 coincide with the axis of the screw 21. The first avoidance hole 121 and the second avoidance hole 3311 are both used to allow the output shaft 31 to pass through.

[0259] In this embodiment, the diameter of the second avoidance hole 3311 is greater than the diameter of the first avoidance hole 121. The electronic mechanical brake device 100 of the present application also includes a second bearing 72, which includes an outer ring 721 and an inner ring 722. The inner circumferential surface of the second avoidance hole 3311 is used to fix the outer ring 721 of the second bearing 72, and the inner ring 722 of the second bearing 72 is used to fix the middle section of the output shaft 31, thereby forming a reliable support structure for the output shaft 31 and ensuring that the output shaft 31 drives the screw 21 to rotate smoothly.

[0260] On the other hand, the fixed fit between the reducer 30 and the brake caliper 10 also allows, during operation of the electronic mechanical brake device 100, when the ball screw 20 pushes the first friction plate 511 against the brake disc 1002, the braking force of the ball screw 20 can push the housing 33 of the reducer 30 to slide via the screw 21, thereby driving the brake caliper 10 to slide, thereby enabling the ball screw 20 to push the second friction plate 512 to slide toward the brake disc 1002, thereby achieving the braking function of the electronic mechanical brake device 100 of the present application.

[0261] In another embodiment, the diameter of the first avoidance hole 121 is larger than the diameter of the second avoidance hole 3311. Correspondingly, the inner circumference of the first avoidance hole 121 is used to fix the outer ring 721 of the second bearing 72, and the inner ring 722 of the second bearing 72 is used to fix the middle section of the output shaft 31 to achieve support for the output shaft 31.

[0262] In one embodiment, a brake motor 40 and a brake caliper 10 are arranged on the same side of a reducer 30 along the axial direction of a lead screw 21; a brake caliper 10 includes a receiving groove 13 (see Figure 4), an accommodating groove 13 is arranged at intervals with a ball screw 20 along the radial direction of a screw 21, and an accommodating groove 13 is used to partially accommodate a brake motor 40.

[0263] Specifically, such as Figure 3-Figure 6 As shown, the reducer 30 is connected to the brake motor 40 and the ball screw 20, and the ball screw 20 is housed in the accommodating cavity 11 of the brake caliper 10. It is understood that arranging the brake motor 40 and the brake caliper on the side of the reducer 30 where the output shaft 31 is provided can reduce the axial space occupied by the brake motor 40, thereby reducing the axial size of the electronic mechanical brake device 100 of the present application. Furthermore, partially accommodating the brake motor 40 in the accommodating groove 13 of the brake caliper 10 can further reduce the axial space occupied by the brake motor 40, thereby further reducing the axial size of the electronic mechanical brake device 100 of the present application.

[0264] In one embodiment, a speed reducer 30 includes a parallel axis gear set 34 (see Figure 31 ), a parallel axis gear set 34 includes an input shaft 341 and another output shaft (second output shaft 342). An input shaft 341 and another output shaft are arranged at intervals along the axial direction of a screw 21. An input shaft 341 is used for transmission connection to a motor shaft 41 of a brake motor 40 (see Figure 31 ), and the other output shaft is used to drively connect to another input shaft (second input shaft 325) of a planetary gear set 32.

[0265] For details, please refer to Figure 31 ,in Figure 31 Schematic diagram of the transmission structure of the reducer 30 and the brake motor 40 of the electronic mechanical brake device 100. Figure 27 .

[0266] like Figure 27 and Figure 31 As shown, the parallel axis gear set 34 includes an input shaft 341, a second output shaft 342, a first parallel wheel 343, and a second parallel wheel 344. The axis of the input shaft 341, the axis of the second output shaft 342, the axis of the first parallel wheel 343, and the axis of the second parallel wheel 344 are all parallel to the axis of the screw 21.

[0267] The input shaft 341 is coaxially fixed to the first parallel wheel 343 and is used for transmission connection to the motor shaft 41 of the brake motor 40. The second parallel wheel 344 is coaxially fixed to the second output shaft 342 and is used for transmission connection to the second input shaft 325 of the planetary gear set 32. The second parallel wheel 344 meshes with the first parallel wheel 343 for transmission.

[0268] The planetary gear set 32 ​​further includes a first transmission wheel 326 and a second transmission wheel 327. The axis of the first transmission wheel 326 coincides with the axis of the screw 21. The first transmission wheel 326 is used to coaxially drive the sun gear 323. The axis of the second transmission wheel 327 is parallel to the axis of the screw 21. The second transmission wheel 327 is coaxially fixed to the second input shaft 325. Figure 27 In the diagram, the second input shaft 325 is coaxially fixed with the second output shaft 342 , and the second transmission wheel 327 is used to engage and drive the first transmission wheel 326 .

[0269] When the electronic mechanical brake device 100 of the present application is in operation, the brake motor 40 outputs a braking force to the input shaft 341 via the motor shaft 41. The input shaft 341 drives the first parallel pulley 343 to rotate, causing the second parallel pulley 344 to rotate relative to the housing 33 of the reducer 30. The rotating second parallel pulley 344 transmits the braking force to the sun gear 323 via the second output shaft 342, the second input shaft 325, the second transmission pulley 327, and the first transmission pulley 326. The braking force is then transmitted to the output shaft 31 via the various gears within the planetary gear set 32. The output shaft 31 then transmits the braking force to the friction plate 51 via the ball screw 20, thereby achieving the braking function of the electronic mechanical brake device 100 of the present application.

[0270] In this embodiment, the diameter of the second transmission wheel 327 is smaller than the diameter of the second parallel wheel 344, so that there is a larger transmission ratio between the second transmission wheel 327 and the sun gear 323, so as to facilitate the adjustment of the torque of the braking force transmitted to the planetary gear set 32, thereby increasing the thrust acting on the friction plate 51 through the reducer 30 and the ball screw 20, and improving the braking efficiency of the electronic mechanical braking device 100 of this application.

[0271] Obviously, those skilled in the art may make various modifications and variations to this application without departing from the scope of protection of this application. Thus, if these modifications and variations of this application fall within the scope of the claims of this application and their equivalents, this application is intended to include these modifications and variations.

Claims

1. An electromechanical brake device in which a lead screw and an output shaft are embedded, characterized in that: The electronic mechanical brake device includes a brake caliper, a ball screw and a reducer, wherein the ball screw includes a screw and a screw sleeve, the reducer includes an output shaft, one end of the output shaft is used to drive the screw to rotate, and the screw sleeve is used to move along the axial direction of the screw as the screw rotates, the brake caliper is used to fix the reducer and to accommodate the screw and the screw sleeve, an end face of the screw faces the reducer along the axial direction of the screw, and the end face includes: an axial groove, wherein the one end of the one output shaft is used to be embedded in the one axial groove along the axial direction of the screw, and the one axial groove is used to drively connect the one end of the one output shaft; or, An axial protrusion is used to be embedded in or nested in the one end of the output shaft along the axial direction of the screw, and the axial protrusion is used to transmission-connect the one end of the output shaft.

2. The electromechanical brake device according to claim 1, characterized in that The threads on the inner circumference of the sleeve are used to engage with the threads on the outer circumference of the lead screw, and the brake caliper includes an accommodating cavity, which is used to accommodate at least one of a pressure sensor or a thrust bearing, the sleeve, and the lead screw, wherein: Along the axial direction of the lead screw, at least one of the pressure sensor and the thrust bearing is arranged between the end surface and the cavity wall of the accommodating cavity.

3. The electromechanical brake device according to claim 2, characterized in that: The one end surface includes the one axial protrusion, wherein: Along the axial direction of the one screw, the length of the one screw is greater than the length of the one sleeve; Along the radial direction of the lead screw, the diameter of the axial protrusion is smaller than the inner diameter of the screw sleeve; Along the axial direction of the lead screw and in the direction toward the reducer, the thrust bearing and the pressure sensor are sequentially sleeved on the axial protrusion.

4. The electromechanical brake device according to claim 3, characterized in that Along the radial direction of one of the screws: The diameter of the one axial protrusion is larger than the diameter of the one output shaft, and the inner hole of the one thrust bearing and the inner hole of the one pressure sensor are respectively used to abut against the outer peripheral surface of the one axial protrusion; or, The diameter of the output shaft is larger than the diameter of the axial protrusion, and the inner hole of the thrust bearing and the inner hole of the pressure sensor are respectively used to abut against the outer peripheral surface of the output shaft.

5. The electromechanical brake device according to claim 2, wherein: The one end surface comprises the one axial groove, wherein: Along the axial direction of the one screw, the length of the one screw is greater than the length of the one sleeve; Along the radial direction of the lead screw, the diameter of the axial groove is smaller than the inner diameter of the screw sleeve; Along the axial direction of the lead screw and in the direction toward the reducer, the thrust bearing and the pressure sensor are sequentially sleeved on the output shaft; The inner hole of the thrust bearing and the inner hole of the pressure sensor are respectively used to abut against the outer peripheral surface of the output shaft.

6. The electromechanical brake device according to any one of claims 3 to 5, characterized in that: The accommodating cavity includes a first section and a second section connected along the axial direction of the lead screw, the inner circumferential surface of the first section is used to abut the outer circumferential surface of the screw sleeve, and the inner circumferential surface of the second section is used to abut the outer circumferential surface of the pressure sensor, wherein: Along the radial direction of the one lead screw, the inner circumferential diameter of the first section is smaller than the inner circumferential diameter of the second section and larger than the inner diameter of the one screw sleeve; Along the axial direction of the one screw, the length of the second section is less than or equal to the sum of the lengths of the one thrust bearing and the one pressure sensor.

7. The electromechanical brake device according to claim 6, characterized in that: The accommodating cavity includes a third section along the axial direction of the one lead screw, and the third section is connected to the first section through the second section, wherein: Along the radial direction of the one lead screw, the inner circumferential diameter of the third section is smaller than the inner circumferential diameter of the second section and larger than the diameter of the one end of the one output shaft; Along the axial direction of the lead screw, the end surface of the third section facing the lead screw is used to abut against an outer surface of the pressure sensor.

8. The electromechanical brake device according to any one of claims 3 to 7, characterized in that: The thrust bearing includes two opposite side surfaces along the axial direction of the one lead screw, wherein one of the side surfaces is used to fit the one end surface of the one lead screw, and the other side surface is used to fit the other outer surface of the one pressure sensor, wherein: The outer diameter of the one side surface is less than or equal to the outer diameter of the one end surface; An outer diameter of the other side surface is smaller than or equal to an outer diameter of the other outer surface.

9. The electromechanical brake device according to any one of claims 2 to 8, characterized in that: The one end of the one output shaft passes through the cavity wall of the accommodating cavity along the axial direction of the one lead screw and is located in the accommodating cavity, wherein: The outer peripheral surface of the one end of the one output shaft comprises at least one radial groove, and the at least one radial groove is used to be embedded in the one axial groove or the one axial protrusion; or, The inner circumferential surface of the one end of the one output shaft includes at least one radial protrusion, and the at least one radial protrusion is used to be nested in the one axial protrusion.

10. The electromechanical brake device according to any one of claims 1 to 9, characterized in that: The ball screw includes a piston, and the piston is partially accommodated in the accommodating cavity, wherein: Along the axial direction of the lead screw and toward the reducer, the piston and the threaded sleeve are arranged in sequence; The piston comprises a groove, the notch of the groove is oriented toward the reducer along the axial direction of the lead screw, and the groove is used to partially accommodate the lead screw; Along the axial direction of the lead screw, the sum of the groove depth of the groove and the length of the screw sleeve is greater than or equal to the length of the lead screw.

11. The electromechanical brake device according to any one of claims 1 to 10, characterized in that: The one reducer includes a planetary gear set, the other end of the one output shaft includes at least one shaft hole, the at least one shaft hole is used to fix at least one transmission shaft, and the at least one transmission shaft is used to drive the at least one planetary gear of the one planetary gear set, wherein: Along the axial direction of the one screw, the one planetary gear set is arranged on a side of the one output shaft away from the one screw; Along the radial direction of the one screw, the diameter of the other end of the one output shaft is larger than the diameter of the one end, and the axis of each of the at least one axial hole is offset from the axis of the one screw.

12. The electromechanical brake device according to claim 11, characterized in that: The one planetary gear set includes a sun gear, and the sun gear is used for driving connection with the at least one planetary gear, wherein: Along the axial direction of the one screw, the one sun gear is arranged at intervals on a side of the one output shaft away from the one screw; The other end of the output shaft comprises a bearing receiving groove, wherein the notch of the bearing receiving groove is away from the lead screw along the axial direction of the lead screw; The bearing receiving groove is used to fix the outer ring of a bearing, and the inner ring of the bearing is used to fix the transmission shaft of the sun gear.

13. The electromechanical brake device according to any one of claims 1 to 12, characterized in that: Along the axial direction of the one screw, the one brake caliper and the one reducer housing include two side walls fixedly attached, each of the side walls includes a position avoidance hole, and the two position avoidance holes are used to allow the one output shaft to pass through, wherein: Along the radial direction of the one lead screw, the diameter of one of the avoidance holes is larger than the diameter of the other avoidance hole; The inner circumferential surface of the one avoidance hole is used to fix the outer ring of another bearing, and the inner ring of the other bearing is used to fix the middle section of the one output shaft.

14. The electromechanical brake device according to any one of claims 1 to 13, characterized in that: The electronic mechanical braking device includes a brake motor, and the reducer is used for transmission connection between the brake motor and the ball screw, wherein: Along the radial direction of the lead screw, the brake motor and the brake caliper are arranged on the same side of the reducer; The brake caliper includes a receiving groove, which is spaced apart from the ball screw along the radial direction of the screw, and is used to partially receive the brake motor.

15. A vehicle, characterized in that: The invention comprises a wheel and an electromechanical brake device according to any one of claims 1 to 14, wherein: The axis of a lead screw in the electronic mechanical brake device is parallel to the axis of the wheel; A brake caliper of the electronic mechanical brake device is closer to the wheel than a speed reducer along the axial direction of the wheel; A screw sleeve in the electronic mechanical brake device is used to drive one or more friction plates to slide along the axial direction of the wheel to brake the brake disc of the wheel.

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