Brake system for vehicles

Abstract

Braking device for vehicles, comprising: a cylinder; a motor that is coupled to the cylinder and is designed to generate a rotational force; a threaded spindle that is installed in the cylinder and is designed to receive the torque from the motor and rotate around an axis thereof; a nut that is coupled to the threaded spindle via a ball and is designed to move back and forth in an axial direction of the threaded spindle according to a direction of rotation of the threaded spindle; a piston that is coupled to the nut and designed to move together with the nut; a sleeve that is arranged in the cylinder and is designed to guide the movement of the piston inserted into the sleeve; and a damper that is coupled to the threaded spindle and is elastically deformable.

Description

Background area

[0001] Exemplary embodiments of the present disclosure relate to a braking device for vehicles and in particular to a braking device for vehicles in which a rotary motion of a threaded spindle, which is rotated by receiving a rotary force from a motor, can be converted into a linear motion of a piston. Discussion of the state of the art

[0002] Due to the characteristics of electrically operated braking devices for vehicles, a mechanism is generally required that is set up to convert a rotary motion of a motor into a linear motion of a piston in a cylinder in order to generate hydraulic brake pressure.

[0003] A ball screw drive is used in an electric brake device as the mechanism to convert the rotary motion of the motor into linear motion. The ball screw drive comprises a threaded spindle that receives the rotary force from the motor and rotates about an axis, a nut that is coupled to the threaded spindle via balls and is configured to move in an axial direction along the threaded spindle, and a piston that is coupled to the nut and pressurizes a working fluid in the cylinder.

[0004] In the prior art, during the process of generating hydraulic brake pressure, resonance occurring in the ball screw drive can cause problems such as damage to a coupling section with a motor, power loss, and the generation of vibrations and noise. Therefore, improvements are needed to solve these problems.

[0005] The technical background of the present disclosure is disclosed in Korean patent publication no. 10-2021-0064367 (published on June 2, 2021, entitled “Hydraulic unit for hydraulic vehicle braking system”). Summary

[0006] Various designs aim to provide a braking device for vehicles that can reduce resonance generated in a threaded spindle.

[0007] Various embodiments aim to provide a braking device for vehicles that can convert a rotary motion of a threaded spindle, which is rotated by receiving a rotary force from a motor, into a linear motion of a piston.

[0008] To achieve the aforementioned objectives, a braking device for vehicles according to an embodiment of the present disclosure may comprise the following: a cylinder; a motor coupled to the cylinder and configured to generate a rotational force; a threaded spindle installed in the cylinder and configured to receive the rotational force from the motor and to rotate about an axis thereof; a nut coupled to the threaded spindle via a ball and configured to move back and forth in an axial direction of the threaded spindle corresponding to a direction of rotation of the threaded spindle; a piston coupled to the nut and configured to move together with the nut; a sleeve arranged in the cylinder and configured to guide a movement of the piston inserted into the sleeve; and a damper coupled to the threaded spindle and elastically deformable.

[0009] The piston may comprise: a rod which engages in threaded engagement with an outer surface of the nut; and a head which is formed integrally with the rod and is configured to move back and forth in the sleeve in a longitudinal direction of the sleeve.

[0010] The braking device may further include a shaft bearing arranged in the cylinder and coupled to the threaded spindle, the shaft bearing being designed to absorb an axial load during the formation of hydraulic pressure in the cylinder.

[0011] The threaded spindle may comprise: a screw body rotatably arranged about an axis in the cylinder; a neck section protruding from the screw body; a power transmission section extending from the neck section and configured to receive a rotational force from the motor; and a shaft cover enclosing the neck section and the power transmission section.

[0012] The damper can be made of a metallic material. The shaft cover can be made of a plastic material.

[0013] The diameter of the power transmission section can be larger than the diameter of the neck section.

[0014] A gap may be provided between the neck section and the shaft cover.

[0015] The damper may comprise: a damper body arranged between the shaft cover and the neck section, configured to enclose the neck section; and an elastic section projecting convexly from the damper body, configured to elastically support the shaft cover.

[0016] The elastic section can project from an outer circumferential surface of the damper body in a radial direction of the damper body and can be formed in a circumferential direction of the damper body.

[0017] The damper body can be designed in a ring shape, with one side of its outer circumferential surface being open.

[0018] A braking device for vehicles according to an embodiment of the present disclosure may comprise the following: a cylinder; a motor configured to generate rotational force; a threaded spindle arranged in the cylinder and configured to receive the rotational force from the motor and to rotate about an axis thereof; a nut coupled to the threaded spindle and configured to move back and forth in an axial direction corresponding to a rotation of the threaded spindle; a sleeve arranged between the cylinder and the threaded spindle; a piston coupled to the nut and having a head that moves back and forth in the sleeve corresponding to the reciprocating movement of the nut;and a vibration damper comprising a first side supported on the threaded spindle and a second side supported on the motor, wherein the vibration damper is elastically deformable.

[0019] The vibration damper may include a helical spring.

[0020] The helical spring can have an interrupted ring shape.

[0021] The helical spring can comprise a metallic material.

[0022] The vibration damper may include a torsion spring.

[0023] The threaded spindle may comprise: a screw body rotatably arranged about an axis thereof in the cylinder; a neck section projecting from the screw body; and a force transmission section extending from the neck section and configured to receive the rotational force from the motor, the first side of the vibration damper being supported in contact with a stepped section in a connection area between the screw body and the neck section.

[0024] The second side of the vibration damper can be supported in contact with a conical surface of the engine.

[0025] The second side of the vibration damper can be positioned further away from the sleeve than the first side of the vibration damper.

[0026] The piston may comprise: a rod coupled to an outer surface of the nut; and the head formed integrally with the rod and configured to move back and forth within the sleeve in a longitudinal direction of the sleeve.

[0027] The braking device may further comprise a shaft bearing arranged in the cylinder and coupled to the threaded spindle, wherein the shaft bearing is designed to absorb an axial load during the formation of hydraulic pressure in the cylinder. Brief description of the drawings Fig. Figure 1 is a sectional view showing a braking device for vehicles according to an embodiment of the present disclosure. Fig. Figure 2 is a perspective view showing a cylinder viewed from one direction, according to an embodiment of the present disclosure. Fig. 3 is a perspective view showing the cylinder from Fig. 2 is viewed from a different direction. Fig. 4 is a perspective exploded view showing the cylinder from Fig. 2 represents. Fig. Figure 5 is a perspective exploded view showing the cylinder from Fig. 3 represents. Fig. Figure 6 is a sectional view showing the cylinder according to one embodiment of the present disclosure. Fig. 7 is an enlarged view showing a section from Fig. 6 represents. Fig. Figure 8 is a perspective view showing a damper according to one embodiment of the present disclosure. Fig. Figure 9 is a sectional view showing an operating state in which a piston in the brake device for vehicles according to an embodiment of the present disclosure moves forward into the cylinder. Fig. Figure 10 is a sectional view showing an operating condition in which the piston in the brake device for vehicles according to an embodiment of the present disclosure moves backwards in the cylinder. Fig. Figure 11 is a sectional view showing a braking device for vehicles according to another embodiment of the present disclosure. Fig. Figure 12 is a perspective view showing a cylinder viewed from one direction according to another embodiment of the present disclosure. Fig. Figure 13 is a perspective view showing the cylinder of Fig. 12 is presented from a different perspective. Fig. Figure 14 is a sectional view schematically representing the braking device for vehicles according to another embodiment of the present disclosure. Fig. Figure 15 is an enlarged sectional view of an area around a vibration damper according to another embodiment of the present disclosure. Fig. Figure 16 is a view representing an operating state in which a piston moves forward in the cylinder of the brake device for vehicles according to another embodiment of the present disclosure. Fig. Figure 17 is a view representing an operating condition in which the piston in the cylinder in the brake device for vehicles according to another embodiment of the present disclosure moves backwards. Detailed description

[0028] The following describes embodiments of a braking device for vehicles according to the present disclosure with reference to the accompanying drawings. It should be noted that the drawings are not to scale and the line thickness or the size of components may be exaggerated for clarity. The terms used herein are defined in consideration of the functions of the present disclosure and may be modified according to user or operator requirements. Therefore, the definitions of terms should be consistent with the overall descriptions set forth herein.

[0029] Fig. Figure 1 is a sectional view showing a braking device for vehicles according to an embodiment of the present disclosure. Fig. Figure 2 is a perspective view showing a cylinder according to an embodiment of the present disclosure viewed from one direction. Fig. Figure 3 is a perspective view showing the cylinder of Fig. 2 shows a view from a different direction. Fig. Figure 4 is a perspective exploded view showing the cylinder of Fig. 2 shows. Fig. Figure 5 is a perspective exploded view showing the cylinder of Fig. 3 shows. Fig. Figure 6 is a sectional view showing the cylinder according to one embodiment of the present disclosure.

[0030] With reference to Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5 to Fig. 6. A braking device for vehicles according to an embodiment of the present disclosure may comprise a cylinder 200, a motor 300, a threaded spindle 400, a nut 500, a piston 600, a sleeve 700 and a damper 800, which are described in detail below.

[0031] The cylinder 200 can be installed in a housing 100 by press fit and can withstand the torque generated by the hydraulic pressure resulting from the reciprocating movement of the piston 600. According to one embodiment of the present disclosure, the housing 100 can have a hollow shape with an interior space.

[0032] The housing 100 can be attached to one outside of the cylinder 200 (on the left side based on Fig. 1) be provided. The cylinder 200 can be assembled with the housing 100 under controlled concentricity.

[0033] The cylinder 200 can have a hollow shape. The sleeve 700, in which an actuating section is provided that allows the build-up of hydraulic pressure by pressing the piston 600, can be located in a side compartment (on the left side based on Fig. 1) be provided in cylinder 200.

[0034] Motor 300 can be connected to cylinder 200, and various drive devices can be used to generate torque, depending on the technical concept. Motor 300 can transmit torque to the threaded spindle 400.

[0035] The motor 300 can include a stationary component 310, a rotating component 320 and a motor bearing 330.

[0036] The stationary component 310 can be attached to the housing 100 and can have various shapes, with the magnetic force being changed by the supply of current. The stationary component 310 can have a mounting frame 311, which is attached to one side of the housing 100 (on a right-hand side based on Fig. 1) is attached, and comprise a stator 312 which is attached to the inner surface of the mounting frame 311 opposite the rotating component 320 and is configured to generate a magnetic force.

[0037] The mounting frame 311 can be connected to one side of the housing 100. The rotating component 320 can be rotatably installed in the mounting frame 311.

[0038] The stator 312, which is an electromagnet, can be installed in a circumferential direction on an inner surface of the mounting frame 311 and can rotate the rotational component 320 by changing the magnetic flux in response to a control signal from a controller (not shown).

[0039] The rotating component 320 can be connected to the threaded spindle 400 and rotate together with the threaded spindle 400. Within the framework of a technical concept, the rotating component 320 can be formed into various shapes in which the rotating component 320 can rotate according to a change in the magnetic force of the stationary component 310.

[0040] The rotating component 320 can be rotatably installed in the mounting frame 311. The rotating component 320 can have an approximately "C"-shaped cross-section and can be designed in a hollow form.

[0041] The rotation component 320 can form a rotating frame 321, which is installed in a form that forms one side (the right side based on Fig. 1) of the cylinder 200, and comprise a rotor 322 which is installed on an outer surface of the rotary frame 321 which faces the stationary component 310 and has a magnetic force.

[0042] The rotary frame 321 can have a splined toothing which engages with the threaded spindle 400 and is described below.

[0043] The motor bearing 330 can be installed between the stationary component 310 and the rotating component 320 to reduce the friction generated during the rotation of the rotating component 320. The rotor 322, which consists of a plurality of magnets installed circumferentially on the rotating frame 321, can rotate together with the rotating frame 321 by changing the magnetic force of the stator 312.

[0044] A frame cover 340 attached to the mounting frame 311 can be installed in a form that encloses an outer surface of one end of the rotating frame 321 to prevent the ingress of foreign substances.

[0045] The threaded spindle 400 can be provided in the cylinder 200. The threaded spindle 400 can be inserted in a longitudinal direction of the cylinder 200 and axially coupled to the cylinder 200.

[0046] The central axis of the cylinder 200 and the central axis of the threaded spindle 400 can coincide. The threaded spindle 400 can be attached to a shaft bearing 900, which is described below, via a support component 1000.

[0047] The threaded spindle 400 can comprise a screw body 410, a neck section 420, a power transmission section 430, a shaft cover 440 and a coupling section 450.

[0048] The screw body 410 can be rotatably installed in the cylinder 200 and can have a screw thread that extends along a longitudinal direction of the threaded spindle 400. The screw body 410 can be arranged in the rotary frame 321, which is provided in the motor 300.

[0049] The neck section 420 can extend from an outer surface around a pivot point of the screw body 410 towards a first side (a right side based on Fig. 1) protrude and can be shaped so that it has a smaller diameter than the screw body 410.

[0050] The power transmission section 430 can extend from a free end of the neck section 420 towards the first side (the right side in Fig. 1) extend and can be shaped so that it has a larger diameter than that of the neck section 420.

[0051] A splined connection can be formed along a circumferential direction on an outer surface of the power transmission section 430, which faces the rotary frame 321. Accordingly, the rotary frame 321 and the power transmission section 430 can interlock, thus achieving power transmission.

[0052] The shaft cover 440 can be designed to enclose the neck section 420 and the power transmission section 430. A gap G can be formed between the neck section 420 and the shaft cover 440. The damper 800, which is described below, can be installed in the gap G.

[0053] The shaft cover 440 can be arranged between the power transmission section 430 and the rotary frame 321 to prevent the formation of metallic rattling noises.

[0054] A splined connection can be formed on an outer surface of the shaft cover 440 along a circumferential direction of the shaft cover 440 and can engage with the rotary frame 321. An outer shape of the shaft cover 440 can correspond to an outer shape of the power transmission section 430.

[0055] The coupling section 450 can extend from the outer surface around the center of rotation of the screw body 410 to a second side (a left side based on Fig. 1) extend and can be shaped so that it has a smaller diameter than that of the screw body 410.

[0056] The coupling section 450 can be rotatably coupled via the shaft bearing 900, as described below.

[0057] The nut 500 can be positioned within the rotary frame 321 provided in the motor 300 and provided in the cylinder 200.

[0058] The nut 500 can be coupled to an outer surface of the threaded spindle 400 via a ball B.

[0059] The threaded spindle 400 can be coupled to the nut 500 by passing through the nut 500. The ball B is positioned between a screw thread formed on an inner surface of the nut 500 and the screw thread formed on an outer surface of the screw body 410, so that the rotary motion of the threaded spindle 400 can be converted into a linear motion by the nut 500.

[0060] The nut 500 can move back and forth in an axial direction of the threaded spindle 400 in accordance with the direction of rotation of the threaded spindle 400.

[0061] The piston 600 can be coupled in such a way that it encloses one outer surface of the nut 500. The piston 600 can move along with the movement of the nut 500 in the longitudinal direction of the cylinder 200.

[0062] The piston 600 can include a rod 610 and a head 620.

[0063] The rod 610 can be hollow and positioned in the rotary frame 321 provided in the motor 300. The outer surface of the nut 500 and an inner surface of the rod 610 can engage with each other via a thread.

[0064] The head 620 can be formed integrally with the rod 610. The diameter of the head 620 can be larger than the diameter of the rod 610.

[0065] The head 620 can be designed in a ring shape, positioned in the housing 100, and move back and forth in the sleeve 700 to move the working fluid in the sleeve 700 towards the ports 210. Accordingly, the cylinder 200 can generate double-acting hydraulic pressure in accordance with the reciprocating movement of the piston 600.

[0066] The sleeve 700 can be positioned in the housing 100 and provided in the cylinder 200. The sleeve 700 can guide the movement of the piston 600 inserted therein.

[0067] The sleeve 700 can be designed to enclose the head 620 of the piston 600.

[0068] The ports 210, through which the working fluid flows, can be provided on an outer surface of the cylinder 200 corresponding to the sleeve 700. The ports 210 can each be located longitudinally on opposite sides of the cylinder 200. The working fluid, moved by the movement of the piston 600, can be guided through the ports 210 to generate the required brake pressure.

[0069] A drain hole 710 connected to the connections 210 can be formed in the outer surface of the sleeve 700.

[0070] A plurality of drain holes 710 can be arranged such that they are spaced apart from each other in the circumferential direction of the sleeve 700. Accordingly, the working fluid in the sleeve 700 can be drained in a radial direction of the piston 600.

[0071] Fig. 7 is an enlarged view showing a section of Fig. 6 shows. Fig. Figure 8 is a perspective view showing a damper according to one embodiment of the present disclosure.

[0072] With reference to the Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5, Fig. 6, Fig. 7 to Fig. According to one embodiment of the present disclosure, the damper 800 can be coupled to the threaded spindle 400. The damper 800 can be installed such that it surrounds the neck section 420.

[0073] The damper 800 can be installed in a gap G between the neck section 420 and the shaft cover 440. The damper 800 can be made of a metallic material.

[0074] The damper 800 can be elastically deformed to reduce resonances that may occur in the threaded spindle 400.

[0075] The central axis of the threaded spindle 400 may be inclined due to the load generated by the hydraulic pressure during the forward movement of the piston 600 and due to backlash tolerances. Wobble of the threaded spindle 400 may occur with the coupling section 450 as a reference point. The degree of wobble of the threaded spindle 400 may be greatest at the neck section 420, which is furthest from the coupling section 450.

[0076] If resonance occurs in the threaded spindle 400, the greatest wobble (vibration) may occur at the neck section 420, which may lead to damage to the shaft cover 440, a deterioration of system performance and quality problems due to the generation of noise and vibrations.

[0077] If wobble occurs in the threaded spindle 400, the shaft cover 440 can deform and resonance can occur in the gap G. The elastic damper 800 can be installed in a space where resonance may occur in order to reduce the resonance if it does.

[0078] The damper 800 can comprise a damper body 810 and an elastic section 820.

[0079] A central section of the damper body 810 can be open in the axial direction of the threaded spindle 400, and the damper body 810 can have a circular or elliptical ring shape with a defined length. The damper body 810 can be approximately C-shaped, with one side of its outer circumferential surface being open.

[0080] The damper body 810 can be designed to enclose the neck section 420. The damper body 810 can be inserted between the shaft cover 440 and the neck section 420.

[0081] The elastic section 820 can project convexly from the damper body 810. The elastic section 820 can project radially from the outer circumferential surface of the damper body 810. The elastic section 820 can be formed along a circumferential direction of the damper body 810.

[0082] The elastic section 820 can elastically support the shaft cover 440. An inner circumferential surface of the elastic section 820 cannot touch an outer circumferential surface of the neck section 420, and an outer circumferential surface of the elastic section 820 can be in close contact with an inner circumferential surface of the shaft cover 440 to elastically support the shaft cover 440.

[0083] The braking device for vehicles according to an embodiment of the present disclosure may include the shaft bearing 900.

[0084] The shaft bearing 900 can be positioned in the housing 100 and provided at an inner end of the cylinder 200.

[0085] An outer surface of the shaft bearing 900 and an outer surface of the sleeve 700 can be installed in contact with each other. The shaft bearing 900 can be coupled to the threaded spindle 400 in a form that encloses the coupling section 450 of the threaded spindle 400.

[0086] The shaft bearing 900 can comprise an inner ring 910, which is installed in contact with the coupling section 450 of the threaded spindle 400, and an outer ring 920, which is installed in contact with the inner surface of the cylinder 200.

[0087] The shaft bearing 900 can absorb an axial load during the formation of hydraulic pressure in the cylinder 200 by the piston 600, which moves back and forth in the axial direction of the threaded spindle 400.

[0088] The braking device for vehicles according to an embodiment of the present disclosure may comprise the support component 1000.

[0089] The support component 1000 can be provided in the cylinder 200. One end of the coupling section 450 can be received in the support component 1000. The shaft bearing 900 can be attached to an outer circumferential surface of the support component 1000. The support component 1000 can rotatably support the threaded spindle 400.

[0090] An operating procedure of the braking device for vehicles according to an embodiment of the present disclosure with the aforementioned configuration is described below.

[0091] Fig. Figure 9 is a sectional view showing an operating state in which the piston in the brake device for vehicles according to an embodiment of the present disclosure moves forward into the cylinder.

[0092] With reference to Fig. 9 When the motor 300 is in operation to transmit a rotational force to the threaded spindle 400, the threaded spindle 400 can rotate in a first direction of rotation about its axis in the cylinder 200, and the nut 500 can move forward along the threaded spindle 400 in the direction of the sleeve 700.

[0093] When the nut 500 moves towards the sleeve 700, the piston 600 connected to the nut 500 moves together with the nut 500 and moves linearly forward in the cylinder 200, thereby generating hydraulic brake pressure.

[0094] Fig. Figure 10 is a sectional view showing an operating state in which the piston in the cylinder of the brake device for vehicles according to an embodiment of the present disclosure moves backwards.

[0095] With reference to Fig. 10. The nut 500 can move backwards along the threaded spindle 400 in a direction opposite to that of the sleeve 700 if the motor 300 operates in such a way that the threaded spindle 400 rotates in the cylinder 200 in a second direction of rotation which is opposite to the first direction of rotation.

[0096] When the nut 500 moves in the opposite direction to the sleeve 700, the piston 600 connected to the nut 500 moves together with the nut 500 and moves linearly backwards in the cylinder 200, thereby generating hydraulic brake pressure. Accordingly, double-acting hydraulic pressure is generated when the piston 600 moves linearly forwards and backwards in the cylinder 200.

[0097] In the braking device for vehicles according to an embodiment of the present disclosure, if wobbling of the threaded spindle 400 occurs, the damper 800, which is elastically deformable and installed in the gap G between the neck section 420 of the threaded spindle 400 and the shaft cover 440, can reduce the resonance of the threaded spindle 400 and compensate for the wobbling of the threaded spindle 400. This allows the coupling force between the threaded spindle 400 and the motor 300 to be improved.

[0098] In the braking device for vehicles according to an embodiment of the present disclosure, an axial load caused by the reaction force during the formation of the hydraulic pressure can be supported in both directions by the shaft bearing 900 coupled to the cylinder 200, so that the axial load caused by the hydraulic pressure can be prevented from being transferred to the motor 300.

[0099] Since in the braking device for vehicles according to an embodiment of the present disclosure the motor 300 does not carry an axial load, the weights and sizes of the housing 100 and the shaft bearing 900 can be reduced.

[0100] In the braking device for vehicles according to an embodiment of the present disclosure, perpendicularity and concentricity can be compensated for by using an inherent clearance of the shaft bearing 900, making it possible to omit existing separate components for shaft alignment, thereby reducing manufacturing costs and shortening the overall axial length.

[0101] Fig. Figure 11 is a sectional view showing a braking device for vehicles according to a further embodiment of the present disclosure. Fig. Figure 12 is a perspective view showing a cylinder as seen from one direction according to a further embodiment of the present disclosure. Fig. Figure 13 is a perspective view showing the cylinder of Fig. 12 shows it viewed from a different direction. Fig. Figure 14 is a sectional view schematically showing the braking device for vehicles according to a further embodiment of the present disclosure. Fig. Figure 15 is an enlarged sectional view of an area around a vibration damper according to a further embodiment of the present disclosure. Fig. Figure 16 is a view showing an operating state in which a piston moves forward in the cylinder of the brake device for vehicles according to a further embodiment of the present disclosure. Fig. Figure 17 is a view showing an operating state in which the piston in the cylinder of the brake device for vehicles according to a further embodiment of the present disclosure moves backwards.

[0102] With reference to Fig. 11, Fig. 12, Fig. 13, Fig. 14, Fig. 15, Fig. 16 to Fig. 17 The braking device for vehicles according to another embodiment of the present disclosure may comprise a cylinder 200, a motor 300, a threaded spindle 400, a nut 500, a piston 600, a sleeve 700 and a vibration damper 800, which are described in detail below.

[0103] The cylinder 200 can be arranged in a housing 100 and can withstand the torque generated by the hydraulic pressure produced by the reciprocating movement of the piston 600. According to the present embodiment, the housing 100 can have a hollow shape with an interior space, and the cylinder 200 can be pressed into the housing 100.

[0104] The housing 100 can be attached to one outside of the cylinder 200 (on the left side based on Fig. 11) be provided. The cylinder 200 can be assembled with the housing 100 under controlled concentricity.

[0105] The cylinder 200 can have a hollow shape. The sleeve 700, in which an actuating section is provided that allows the build-up of hydraulic pressure by pressing the piston 600, can be located in a side compartment (on the left side based on Fig. 11) be provided in cylinder 200.

[0106] Motor 300 can be connected to cylinder 200, and various drive devices can be used to generate torque, depending on the technical concept. Motor 300 can transmit torque to the threaded spindle 400.

[0107] The motor 300 can include a stationary component 310, a rotating component 320 and a motor bearing 330.

[0108] The stationary component 310 can be attached to the housing 100 and can be designed in various forms as part of a technical idea in which the magnetic force is changed by supplying current.

[0109] The stationary component 310 can have a mounting frame 311, which is attached to one side of the housing 100 (on the right side based on Fig. 11) is attached, and comprise a stator 312 which is installed on an inner surface of the mounting frame 311 which faces the rotating component 320 and which is configured to generate a magnetic force.

[0110] The mounting frame 311 can be connected to one side of the housing 100. The rotating component 320 can be rotatably installed in the mounting frame 311.

[0111] The stator 312, which is an electromagnet, can be installed in a circumferential direction on an inner surface of the mounting frame 311 and can rotate the rotational component 320 by changing the magnetic flux in response to a control signal from a controller (not shown).

[0112] The rotating component 320 can be connected to the threaded spindle 400 and rotate together with the threaded spindle 400. Within the framework of a technical concept, the rotating component 320 can be formed into various shapes in which the rotating component 320 can rotate according to a change in the magnetic force of the stationary component 310.

[0113] The rotating component 320 can be rotatably installed in the mounting frame 311. The rotating component 320 can have an approximately "C"-shaped cross-section and be designed in a hollow form.

[0114] The rotation component 320 can form a rotating frame 321, which is installed in a form that forms one side (the right side based on Fig. 11) of the cylinder 200, and comprise a rotor 322 which is installed on an outer surface of the rotary frame 321 which faces the stationary component 310 and has a magnetic force.

[0115] In the rotary frame 321, in particular on an inner surface of the rotary frame 321, a wedge toothing can be formed which engages with the threaded spindle 400.

[0116] The motor bearing 330 can be provided between the stationary component 310 and the rotating component 320 to reduce the friction generated during the rotation of the rotating component 320. The rotor 322, which consists of a plurality of magnets installed circumferentially on the rotating frame 321, can be rotated together with the rotating frame 321 by changing the magnetic force of the stator 312.

[0117] A frame cover 340 attached to the mounting frame 311 can be installed in a form that encloses an outer surface of one end of the rotating frame 321 to prevent the ingress of foreign substances.

[0118] The threaded spindle 400 can be provided in the cylinder 200. The threaded spindle 400 can be installed in a longitudinal direction within the cylinder 200 (a left-right direction based on Fig. 11) inserted and axially coupled to the cylinder 200. A central axis of the cylinder 200 and a central axis of the threaded spindle 400 can coincide.

[0119] The threaded spindle 400 can be attached to a shaft bearing 900 by means of a support component 1000. The support component 1000 can rotatably mount the threaded spindle 400.

[0120] The threaded spindle 400 can comprise a screw body 410, a neck section 420, a power transmission section 430 and a coupling section 450.

[0121] The screw body 410 can be rotatably installed in the cylinder 200 and can have a screw thread that extends along a longitudinal direction of the threaded spindle 400. The screw body 410 can be arranged in the rotary frame 321 of the motor 300.

[0122] The neck section 420 can extend from an outer surface around a pivot point of the screw body 410 towards a first side (a right side based on Fig. 11) protrudes and can be shaped so that it has a smaller diameter than that of the screw body 410.

[0123] The power transmission section 430 can extend from a free end of the neck section 420 towards the first side (the right side based on Fig. 11) extend and can be shaped so that it has a larger diameter than that of the neck section 420.

[0124] A splined connection can be formed along a circumferential direction on an outer surface of the power transmission section 430 facing the rotary frame 321. If no shaft cover 440 (which will be described later) is provided, the rotary frame 321 and the power transmission section 430 can accordingly engage with each other for power transmission.

[0125] The threaded spindle 400 can further comprise a shaft cover 440. The shaft cover 440 can be arranged to enclose the neck section 420 and the power transmission section 430. The shaft cover 440 can be arranged between the power transmission section 430 and the rotary frame 321 to prevent the generation of metallic rattling noises.

[0126] A splined connection can be formed on an outer surface of the shaft cover 440 along a circumferential direction of the shaft cover 440, which can engage with the rotary frame 321. An outer shape of the shaft cover 440 can correspond to an outer shape of the power transmission section 430.

[0127] A splined connection can be formed along the circumferential direction on an outer surface of the power transmission section 430, which faces the shaft cover 440. Accordingly, the shaft cover 440 and the power transmission section 430 can mesh with each other for power transmission.

[0128] The coupling section 450 can extend from the outer surface around the pivot point of the screw body 410 to a second side (left in Fig. 11) extend and be rotatably coupled to the shaft bearing 900. The connection to the shaft bearing 900 can be made by press fit. The coupling section 450 can be designed to have a diameter that is equal to or smaller than that of the screw body 410.

[0129] The nut 500 can be positioned in the rotating frame 321 of the motor 300 and can be arranged in the cylinder 200.

[0130] The nut 500 can be coupled to an outer surface of the threaded spindle 400 via a ball B.

[0131] The threaded spindle 400 can be coupled by the nut 500. Since the ball B is arranged between a screw thread formed on an inner surface of the nut 500 and the screw thread formed on an outer surface of the screw body 410, the rotary motion of the threaded spindle 400 can be converted into a linear motion by the nut 500.

[0132] An anti-rotation projection (not shown) can be formed on an outer surface of the nut 500, and a movement groove (not shown) can be formed on an inner surface of the cylinder 200.

[0133] When the threaded spindle 400 rotates, the nut 500 does not rotate because the rotation of the anti-rotation projection of the nut 500 is blocked by the movement groove. Accordingly, the rotary motion of the threaded spindle 400 can be converted into a linear motion of the nut 500 by the anti-rotation projection and the movement groove.

[0134] The nut 500 can move back and forth in an axial direction along the threaded spindle 400, corresponding to the direction of rotation of the threaded spindle 400. For example, if the nut 500 moves forward when the threaded spindle 400 rotates in a first direction, the nut 500 can move backward when the threaded spindle 400 rotates in a second direction opposite to the first.

[0135] The piston 600 can be coupled in such a way that it encloses one outer surface of the nut 500. The piston 600 can move longitudinally along the cylinder 200 in conjunction with the reciprocating motion of the nut 500.

[0136] The piston 600 can include a rod 610 and a head 620.

[0137] The rod 610 can be hollow and positioned in the rotating frame 321 of the motor 300. The outer surface of the nut 500 and an inner surface of the rod 610 can engage with each other via a thread.

[0138] The head 620 can be formed integrally with the rod 610. The outer diameter of the head 620 can be larger than the outer diameter of the rod 610.

[0139] The head 620 can be designed in a ring shape, positioned in the housing 100, and move back and forth in the sleeve 700 to move the working fluid in the sleeve 700 towards the ports 210. Accordingly, the cylinder 200 can generate double-acting hydraulic pressure in accordance with the reciprocating movement of the piston 600.

[0140] The sleeve 700 can be positioned in the housing 100 and arranged in the cylinder 200. The sleeve 700 can guide the movement of the piston 600 inserted therein.

[0141] The sleeve 700 can be shaped to enclose the head 620 of the piston 600.

[0142] The ports 210, through which the working fluid flows, can be provided on an outer surface of a region of the cylinder 200 in which the sleeve 700 is located. The ports 210 can each be provided at multiple points along the longitudinal direction of the cylinder 200. Working fluid, moving in accordance with the movement of the piston 600, can be guided through the ports 210 to generate the required brake pressure.

[0143] A drain hole 710, connected to the connections 210, can be formed in the outer surface of the sleeve 700.

[0144] A plurality of drain holes 710 can be arranged such that they are spaced apart from one another in a circumferential direction of the sleeve 700. Accordingly, the working fluid in the sleeve 700 can be drained in a radial direction of the piston 600.

[0145] The threaded spindle 400 may tilt or wobble around its central axis due to a load generated by hydraulic pressure during the forward movement of the piston 600 or due to backlash tolerances. The tilting or wobbling of the threaded spindle 400 can occur with a coupling area between the coupling section 450 and the support component 1000 serving as a reference point (a center point).

[0146] While the threaded spindle 400 wobbles, the amplitude of the threaded spindle 400 may gradually increase with increasing distance from the reference point of wobble and may be greatest at the neck section 420, which is furthest from the reference point of wobble.

[0147] In the present embodiment, the vibration damper 800 can prevent the amplitude of the threaded spindle 400 from increasing significantly or from resonances occurring in advance. This prevents damage to the power transmission section 430 or the shaft cover 440. As a result, disruptions to the normal power transmission from the motor 300 to the threaded spindle 400 or quality problems caused by noise and vibration are avoided.

[0148] In the present embodiment, the vibration damper 800 can have a first side (a left side in Fig. 15), which is supported by the threaded spindle 400, and a second side (a right side in Fig. 15) exhibit, which is carried by the motor 300. Accordingly, the vibration damper 800 can prevent the neck section 420 of the threaded spindle 400 from vibrating excessively away from the central axis of the threaded spindle 400 in the rotary frame 321 of the motor 300.

[0149] The neck section 420 of the threaded spindle 400 comes into indirect contact with the rotary frame 321 via the vibration damper 800. During operation of the vehicle braking device, the relative displacement between the neck section 420 of the threaded spindle 400 and the rotary frame 321 can therefore be reduced, thereby reducing the amplitude of the threaded spindle 400.

[0150] The vibration damper 800 is elastically deformable while being supported by both the threaded spindle 400 and the motor 300. Therefore, when the threaded spindle 400 vibrates, the vibration damper 800 undergoes elastic deformation and thus absorbs the vibration of the threaded spindle 400 or the impact caused by the vibration.

[0151] The vibration damper 800 can be a helical spring.

[0152] The vibration damper 800 can be designed in an interrupted ring shape. That is, as in Fig. As shown in Figure 12, the vibration damper 800 can be designed in a ring shape, with one side of its outer circumferential surface being open.

[0153] Since the vibration damper 800 has two ends, the vibration of the threaded spindle 400 can be transferred to the vibration damper 800 and then dissipated to the outside through each end of the vibration damper 800.

[0154] The second side of the vibration damper 800 can be positioned further away from the sleeve 700 than the first side of the vibration damper 800.

[0155] As in Fig. As shown in Figure 15, the contact points of the vibration damper 800 with the threaded spindle 400 and the contact point with the rotary frame 321 of the motor 300 are arranged diagonally. This allows the vibration damper 800 to absorb vibrations in all directions (360 degrees) around the central axis of the threaded spindle 400.

[0156] The vibration damper 800 can be made of steel. More precisely, the vibration damper 800 can be made of stainless steel.

[0157] The vibration damper 800 can be a torsion spring or a torsion coil.

[0158] The first side of the vibration damper 800 can be supported in contact with a stepped section 411 in a connection area between the screw body 410 and the neck section 420. Since the stepped section 411 is designed in the form of a flat surface, the first side of the vibration damper 800 can be supported elastically and stably on the stepped section 411.

[0159] The second side of the vibration damper 800 can be supported in contact with the rotating frame 321 of the motor 300. The second side of the vibration damper 800 can be supported in contact with a conical surface 325 of the rotating frame 321. Since the conical surface 325 has the shape of a flat surface, the second side of the vibration damper 800 can be supported elastically and stably on the conical surface 325.

[0160] Since the threaded spindle 400 is coupled to the nut 500 via the ball B, a certain degree of vibration is necessary to prevent power loss or jamming during movement. In the present embodiment, the vibration damper 800 is located in a space where the threaded spindle 400 vibrates. This makes it possible to effectively reduce any vibrations that occur without restricting the degrees of freedom of vibration of the threaded spindle 400.

[0161] The vibration damper 800 can be arranged to enclose the neck section 420 of the threaded spindle 400 without affecting the shaft cover 440. The vibration damper 800 can also be arranged so that it does not come into contact with an inner circumferential surface of the neck section 420.

[0162] The braking device for vehicles according to another embodiment of the present disclosure may further comprise the shaft bearing 900.

[0163] The shaft bearing 900 can be positioned in the housing 100 and provided at an inner end of the cylinder 200.

[0164] An outer surface of the shaft bearing 900 and an outer surface of the sleeve 700 can be installed in contact with each other. The shaft bearing 900 can be coupled to the threaded spindle 400 in a form that encloses the coupling section 450 of the threaded spindle 400.

[0165] The shaft bearing 900 can comprise an inner ring 910, a bearing ball 915, and an outer ring 920. The inner ring 910 can be installed in contact with the coupling section 450 of the threaded spindle 400, and the outer ring 920 can be installed in contact with the inner surface of the cylinder 200.

[0166] The shaft bearing 900 can absorb an axial load during the formation of hydraulic pressure in the cylinder 200 by the piston 600, which moves back and forth in the axial direction of the threaded spindle 400.

[0167] The braking device for vehicles according to another embodiment of the present disclosure may comprise the support component 1000.

[0168] The support component 1000 can be provided in the cylinder 200. The support component 1000 can be inserted into the coupling section 450 and coupled to the threaded spindle 400. The support component 1000 can be screwed to the threaded spindle 400. The shaft bearing 900 can be attached to the support component 1000. The support component 1000 can rotatably support the threaded spindle 400. The support component 1000 can be a screw.

[0169] The braking device for vehicles according to another embodiment of the present disclosure may comprise a reaction force component 1100.

[0170] A first side of the reaction force component 1100 can be supported by the cylinder 200, and a second side of the reaction force component 1100 can be brought into contact with the sleeve 700 to push the sleeve 700 towards the shaft bearing 900. The reaction force component 1100 can be a wave spring.

[0171] An operating procedure of the braking device for vehicles according to another embodiment of the present disclosure with the aforementioned configuration is described below.

[0172] With reference to Fig. 16. When the motor 300 is in operation to transmit a rotational force to the threaded spindle 400, the threaded spindle 400 can rotate in a first direction of rotation about its axis in the cylinder 200, and the nut 500 can move forward along the threaded spindle 400 in the direction of the sleeve 700.

[0173] In response to the movement of the nut 500 towards the sleeve 700, the piston 600 connected to the nut 500 can move linearly forward in the cylinder 200 in the same direction as the direction of movement of the nut 500, thereby generating hydraulic brake pressure.

[0174] With reference to Fig.17. The nut 500 can move backwards along the threaded spindle 400 in a direction opposite to that of the sleeve 700 if the motor 300 operates in such a way that the threaded spindle 400 rotates in the cylinder 200 in a second direction of rotation which is opposite to the first direction of rotation.

[0175] In response to the movement of the nut 500 in the direction opposite to the sleeve 700, the piston 600 connected to the nut 500 can move linearly backwards in the cylinder 200 in the same direction as the movement of the nut 500, thus building up hydraulic brake pressure. Accordingly, a double-acting hydraulic pressure can be built up by the linear forward and backward movement of the piston 600 in the cylinder 200.

[0176] In the braking device for vehicles according to another embodiment of the present disclosure, if wobbling of the threaded spindle 400 occurs, the amplitude of the threaded spindle 400 can be reduced by the vibration damper 800, which is elastically deformable and is arranged between the threaded spindle 400 and the motor 300, and a coupling force between the threaded spindle 400 and the motor 300 can be improved.

[0177] The present disclosure provides an effect in which, when wobbling occurs in a threaded spindle, an elastically deformable damper, installed in a gap between a neck section of the threaded spindle and a shaft cover, can compensate for the wobbling and reduce the resonance of the threaded spindle, thereby improving the coupling force between the threaded spindle and a motor.

[0178] The present disclosure provides an action to support an axial load caused by a reaction force during the formation of a hydraulic pressure in both directions by means of a shaft bearing coupled to a cylinder, thereby preventing the axial load caused by the hydraulic pressure from being transferred to the motor.

[0179] Since the motor in the present disclosure does not carry an axial load, the weights and sizes of a housing and shaft bearing can be reduced.

[0180] In the present disclosure, perpendicularity and concentricity can be compensated for by using an inherent clearance of the shaft bearing, making it possible to omit existing separate components for shaft alignment, thereby reducing manufacturing costs and shortening the overall axial length.

[0181] In the present disclosure, a vibration damper can prevent the threaded spindle from swinging away from its central axis.

[0182] Since the vibration damper in the present disclosure is elastically deformable, it can absorb the vibration of the threaded spindle or shocks caused by the vibration.

[0183] Although exemplary embodiments of the disclosure have been disclosed for illustrative purposes, it is apparent to the person skilled in the art that various modifications, additions, and substitutions are possible without departing from the scope of protection and the spirit of the disclosure as defined in the appended claims. The true technical scope of the disclosure should therefore be defined by the following claims. QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] KR 10-2021-0064367

[0005]

Claims

[1] Braking device for vehicles, comprising: a cylinder; a motor that is coupled to the cylinder and is designed to generate a rotational force; a threaded spindle that is installed in the cylinder and is designed to receive the torque from the motor and rotate around an axis thereof; a nut that is coupled to the threaded spindle via a ball and is designed to move back and forth in an axial direction of the threaded spindle according to a direction of rotation of the threaded spindle; a piston that is coupled to the nut and designed to move together with the nut; a sleeve that is arranged in the cylinder and is designed to guide the movement of the piston inserted into the sleeve; and a damper that is coupled to the threaded spindle and is elastically deformable. [2] Brake device for vehicles according to claim 1, wherein the piston comprises: a rod that engages with the threads of the nut on an outer surface; and a head which is formed integrally with the rod and is designed to move back and forth in the sleeve in a longitudinal direction of the sleeve. [3] Brake device for vehicles according to claim 1 or 2, further comprising a shaft bearing arranged in the cylinder and coupled to the threaded spindle, wherein the shaft bearing is configured to absorb an axial load during the formation of hydraulic pressure in the cylinder. [4] Brake device for vehicles according to any one of claims 1 to 3, wherein the threaded spindle comprises: a screw body which is rotatably arranged in the cylinder about one of its axis; a neck section that protrudes from the screw body; a power transmission section extending from the neck section and designed to receive a rotational force from the motor; and a shaft cover that encloses the neck section and the power transmission section. [5] Brake device for vehicles according to claim 4, wherein the damper comprises a metallic material and the wave cover comprises a plastic material. [6] Braking device for vehicles according to claim 4 or 5, wherein a diameter of the power transmission section is larger than a diameter of the neck section. [7] Braking device for vehicles according to claim 6, wherein a gap is provided between the neck section and the shaft cover. [8] Braking device for vehicles according to claim 7, wherein the damper comprises: a damping body arranged between the shaft cover and the neck section and configured to enclose the neck section; and an elastic section that protrudes convexly from the damper body and is designed to elastically support the shaft cover. [9] Brake device for vehicles according to claim 8, wherein the elastic section projects from an outer circumferential surface of the damper body in a radial direction of the damper body and is formed in a circumferential direction of the damper body. [10] Brake device for vehicles according to claim 8 or 9, wherein the damper body is formed in a ring shape, with one side of its outer circumferential surface being open. [11] Brake device for vehicles, comprising: a cylinder; a motor designed to generate rotational force; a threaded spindle that is arranged in the cylinder and is designed to receive the rotational force from the motor and to rotate about an axis thereof; a nut that is coupled to the threaded spindle and is designed to move back and forth in an axial direction of the threaded spindle in accordance with a rotation of the threaded spindle; a sleeve that is arranged between the cylinder and the threaded spindle; a piston coupled to the nut and having a head that moves back and forth in the sleeve in accordance with the reciprocating motion of the nut; and a vibration damper comprising a first side supported on the threaded spindle and a second side supported on the motor, wherein the vibration damper is elastically deformable. [12] Braking device for vehicles according to claim 11, wherein the vibration damper comprises a helical spring. [13] Brake device for vehicles according to claim 12, wherein the helical spring has an interrupted ring shape. [14] Brake device for vehicles according to claim 13, wherein the helical spring comprises a metallic material. [15] Braking device for vehicles according to one of claims 11 to 14, wherein the vibration damper comprises a torsion spring. [16] Brake device for vehicles according to any one of claims 11 to 15, wherein the threaded spindle comprises: a screw body which is rotatably arranged in the cylinder about an axis thereof; a neck section that protrudes from the screw body; and a power transmission section extending from the neck section and designed to receive the rotational force from the motor, wherein the first side of the vibration damper is supported in contact with a stepped section in a connection area between the screw body and the neck section. [17] Braking device for vehicles according to one of claims 11 to 16, wherein the second side of the vibration damper is supported in contact with a conical surface of the engine. [18] Braking device for vehicles according to one of claims 11 to 17, wherein the second side of the vibration damper is arranged further away from the sleeve than the first side of the vibration damper. [19] Brake device for vehicles according to any one of claims 11 to 18, wherein the piston comprises: a rod coupled to an outer surface of the nut; and the head, which is formed integrally with the rod and is designed to move back and forth in the sleeve in a longitudinal direction of the sleeve. [20] Brake device for vehicles according to one of claims 11 to 19, further comprising a shaft bearing arranged in the cylinder and coupled to the threaded spindle, wherein the shaft bearing is designed to absorb an axial load during the formation of hydraulic pressure in the cylinder.

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