JP2018105686A - Load sensor and dynamo-electric brake device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To simply and reliably prevent relative rotation around a shaft between the flange member and support member of a load sensor.SOLUTION: A load sensor is constituted that comprises: a flange member 16A for causing flexion to occur upon receiving a load from the axial front; a support member 16B for supporting the flange member 16A from the axial rear at a position shifted in the radial direction from the point of action of the load; a magnetic target 16C for generating a magnetic flux and provided on one of the flange member 16A and the support member 16B; a magnetic sensor 16D for detecting the magnetic flux generated from the magnetic target 16C and provided on the other of the flange member 16A and the support member 16B; and a rotation prevention mechanism 34 for preventing relative rotation around a shaft between the flange member 16A and the support member 16B.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a load sensor and an electric brake device using the load sensor.

  As the electric brake device, for example, the configuration shown in FIG. 1 which is an embodiment of the present application is employed. This electric brake device transmits the rotational driving force of the electric motor 10 to the rotary shaft 11 via the speed reduction mechanism 26, and the rotation of the rotary shaft 11 is moved in the axial direction of the linear motion member 12 by the linear motion conversion mechanism 13. Convert. The friction pad 15 that moves in the axial direction together with the linear motion member 12 is pressed against the brake disc 17 to exert a braking force. In order to control the braking force to a desired magnitude, the electric brake device includes a portion that receives a reaction force of the load applied to the friction pad 15, for example, between the linear motion conversion mechanism 13 and the caliper housing 25. In many cases, a load sensor 16 for detecting the magnitude of the load due to the reaction force (braking force) is incorporated.

  As a general load sensor 100, for example, there is a configuration shown in Patent Document 1. As shown in FIGS. 10A and 10B, the load sensor 100 includes a flange member 101, a support member 102 that supports the flange member 101 from the rear in the axial direction, and a magnetic target fixed to the flange member 101. 103 and a magnetic sensor 104 fixed to the support member 102. The magnetic target 103 and the magnetic sensor 104 are installed so as to face each other in the radial direction. The magnetic sensor 104 has a function of detecting a magnetic flux generated from the magnetic target 103. When the load acts on the flange member 101, the flange member 101 is displaced in the direction of the load (see the arrow in FIG. 10B), and the relative position between the magnetic target 103 and the magnetic sensor 104 changes. Corresponding to the change in the relative position, the magnitude of the magnetic flux detected by the magnetic sensor 104 changes. The magnitude of the load can be detected from the amount of change in the magnitude of the magnetic flux.

JP 2014-16307 A

  When the load sensor 100 shown in FIGS. 10A and 10B is assembled, a thrust bearing 37 (see FIG. 1) is interposed between the linear motion conversion mechanism 13 (see FIG. 1) and the load sensor 100. The linear motion conversion mechanism 13 may be configured to freely rotate relative to the load sensor 100 around the axis. In this configuration, when a load is repeatedly applied from the linear motion conversion mechanism 13 side, the rotational force on the linear motion conversion mechanism 13 side may be slightly transmitted to the load sensor 100 side via the thrust bearing 37. Then, as shown in FIG. 11, the flange member 101 in contact with the thrust bearing 37 rotates relative to the support member 102 around the axis. When the flange member 101 and the support member 102 are relatively rotated, the magnetic target 103 and the magnetic sensor 104 are displaced from each other, and the magnetic flux density detected by the magnetic sensor 104, that is, the output value of the magnetic sensor 104 is changed. There arises a problem that the detection accuracy is reduced.

  In order to prevent this relative rotation, it is conceivable to increase the tightening allowance between the flange member 101 and the support member 102, but this is not preferable because the pressure input during assembly increases and the assemblability deteriorates.

  Therefore, an object of the present invention is to prevent relative rotation around the axis between the flange member and the support member simply and reliably.

  In order to solve this problem, according to the present invention, a flange member that is deflected by receiving a load from the front in the axial direction, and the flange member is moved rearward in the axial direction at a position shifted radially from the point of application of the load. A support member that is supported from a magnetic target that is provided on one of the flange member or the support member and generates a magnetic flux, and a magnetic target that is provided on the other of the flange member or the support member and detects the magnetic flux generated from the magnetic target. And a rotation sensor for preventing relative rotation around the axis between the flange member and the support member.

  Thus, by providing a rotation prevention mechanism, relative rotation around the axis between the flange member and the support member can be prevented simply and reliably, and a change in the output value of the magnetic sensor accompanying this relative rotation can be prevented. Can do. For this reason, the detection accuracy of the load from the linear motion conversion mechanism side can be improved.

  In the configuration, the rotation prevention mechanism has a first engagement portion formed on the flange member and a second engagement portion formed on the support member, and the first engagement portion The relative rotation can be prevented by engagement with the second engagement portion. Thus, by engaging both engaging portions, the relative rotation can be easily and reliably prevented.

  In the configuration in which the first engagement portion and the second engagement portion are formed, each engagement portion has a flat surface having a normal line perpendicular to the direction of the relative rotation, and the first engagement It is preferable that the engagement is made by surface contact between the portion and the second engagement portion. Thus, by bringing the flat surfaces of the engaging portions into surface contact, the deformation direction of the flange member and the contact surfaces of the flat surfaces are in a parallel positional relationship. Then, the frictional resistance at the contact surface is unlikely to become a hysteresis of the sensor output, and the influence of the frictional resistance on the sensor output can be reduced. For this reason, the detection accuracy by the magnetic sensor can be further improved.

  Alternatively, the rotation prevention mechanism further includes a housing that houses the flange member and the support member, and a first engagement portion formed on the flange member and a second engagement portion formed on the support member. A third engagement portion formed on the inner surface side of the housing, and the engagement between the first engagement portion and the third engagement portion, and the second engagement portion and the first engagement portion. It can also be set as the structure which prevents the said relative rotation by engagement with a three engaging part. If it does in this way, the shape of the 1st engaging part and the 2nd engaging part can be made into the same shape in the direction of an axis, and processing cost can be reduced.

  Alternatively, the rotation prevention mechanism includes a first engagement portion formed on the flange member, a second engagement portion formed on the support member, and an engagement member, and the engagement member It can also be set as the structure which prevents the said relative rotation by engaging so that it may intervene in said 1st engaging part and 2nd engaging part. As this engaging member, for example, a key member or a locking pin can be employed. In this way, the relative rotation can be reliably prevented with a simple configuration.

  The load sensor according to each of the configurations includes an electric motor, a rotation shaft that rotates around an axis by a rotational driving force of the electric motor, a linear motion member that is movable in the axial direction of the rotation shaft, and the rotation A linear motion conversion mechanism for converting the rotation of the shaft into an axial movement of the linear motion member; and an axial direction of the linear motion member along the axial direction provided in one axial direction of the linear motion member. The present invention can be employed in an electric brake device that includes a moving friction pad and a load sensor that detects a load caused by a reaction force from the friction pad.

  Since the load sensor according to the present invention includes an anti-rotation mechanism that prevents relative rotation around the axis between the flange member and the support member, the load sensor around the axis between the flange member and the support member can be simply and reliably provided. Relative rotation can be prevented, and changes in the output value of the magnetic sensor accompanying this relative rotation can be prevented. For this reason, the detection accuracy of the load from the linear motion conversion mechanism side can be improved.

The sectional view which looked at the electric brake equipment concerning this invention from the side Sectional drawing of the principal part of FIG. Sectional drawing which follows the III-III line in FIG. Sectional drawing which follows the IV-IV line in FIG. 1 shows a first embodiment of a load sensor according to the present invention, (a) is a front view, and (b) is a cross-sectional view as seen from the side. The second embodiment of the load sensor according to the present invention is shown, (a) is a front view with a part cut away, and (b) is a sectional view as seen from the side. 3 shows a third embodiment of a load sensor according to the present invention, (a) is a front view with a part cut away, and (b) is a sectional view as seen from the side. 4 shows a load sensor according to a fourth embodiment of the present invention, where (a) is a front view and (b) is a cross-sectional view as viewed from the side. 5 shows a fifth embodiment of a load sensor according to the present invention, (a) is a front view with a part cut away, and (b) is a sectional view as seen from the side. The load sensor which concerns on a prior art is shown, (a) is a front view, (b) is sectional drawing seen from the side surface The front view of the principal part which shows the state which the flange member and the support member rotated relatively around the axis in the load sensor shown in FIG.

  1 to 4 show an embodiment of an electric brake device according to the present invention. This electric brake device includes a rotary shaft 11 that rotates around an axis by the rotational driving force of the electric motor 10, a linear motion member 12 that is provided so as to be movable in the axial direction of the rotary shaft 11, and a rotary motion member that rotates the rotary shaft 11 Friction pads 14, 15 that are provided on one side in the axial direction of the linear motion member 12, and that move in the axial direction as the linear motion member 12 moves in the axial direction. The load sensor 16 that detects the load due to the reaction force from the friction pad 15 is a main component. In the following, one side in the axial direction is referred to as the front, and the other side opposite to the one direction is referred to as the rear.

  The electric brake device includes a brake disc 17 that rotates integrally with a wheel (not shown), and a pair of friction pads 14 and 15 that are opposed to each other in the axial direction with the brake disc 17 interposed therebetween. A braking force is generated by pressing the friction pads 14 and 15 against the brake disc 17 with the transmitted power.

  This electric brake device has a caliper body 21 in which a pair of facing portions 18 and 19 that face each other in the axial direction with a brake disc 17 therebetween are connected by a bridge 20 positioned on the outer diameter side of the brake disc 17. The friction pad 14 is disposed between one facing portion 18 of the caliper body 21 and the brake disk 17, and the friction pad 15 is disposed between the other facing portion 19 and the brake disk 17. The friction pads 14 and 15 are guided in the axial direction of the brake disc 17 by pad pins (not shown) attached to the caliper body 21 and slide portions (not shown) provided on the caliper bracket 22.

  The caliper body 21 is supported by a slide pin 24 (see FIG. 3) attached to a caliper bracket 22 fixed to a knuckle (not shown) that supports a wheel by a bolt 23 so as to be movable in the axial direction of the brake disc 17. ing. Accordingly, when the friction pad 15 moves forward in the axial direction and is pressed against the brake disc 17, the caliper body 21 moves rearward in the axial direction by the reaction force received from the brake disc 17, and the caliper body 21 moves. Thus, the friction pad 14 on the opposite side is also pressed against the brake disc 17.

  As shown in FIG. 1, the one facing portion 19 of the caliper body 21 is a cylindrical caliper housing 25 that is open at both front and rear ends in the axial direction. The caliper housing 25 has a rotation shaft 11, an outer ring member functioning as a linear motion member 12 disposed so as to surround the rotation shaft 11 (hereinafter, the same reference numeral as that of the linear motion member 12), and the rotation shaft 11. A planetary roller screw mechanism that functions as a linear motion converting mechanism 13 that converts the rotation of the outer ring member 12 into an axial movement of the outer ring member 12 (hereinafter, the same reference numeral as the linear motion converting mechanism 13 is attached). A friction pad 15 is disposed in front of the outer ring member 12 in the axial direction.

  The caliper housing 25 is provided with the electric motor 10. A reduction mechanism 26 is provided between the electric motor 10 and the rotary shaft 11 to reduce and transmit the rotation of the electric motor 10 to the rotary shaft 11. The speed reduction mechanism 26 is accommodated in a cover 27 provided so as to cover the end opening of the caliper housing 25 in the axial rearward direction.

  As shown in FIG. 4, the planetary roller screw mechanism 13 includes a plurality of planetary rollers 13A circumscribing the rotating shaft 11 and inscribed in the outer ring member 12, and a carrier 13B that supports the planetary rollers 13A so that they can rotate and revolve. And a spiral ridge 13C provided on the inner periphery of the outer ring member 12, and a circumferential groove 13D provided on the outer periphery of the planetary roller 13A so as to engage with the spiral ridge 13C.

The plurality of planetary rollers 13A are arranged at equal intervals in the circumferential direction. Each planetary roller 13 </ b> A is in rolling contact with the outer periphery of the rotating shaft 11 and the inner periphery of the outer ring member 12. The contact portion of the rotating shaft 11 with respect to the planetary roller 13A is a cylindrical surface. When the rotary shaft 11 is rotated, the planetary rollers 13A, while rotating about the roller shaft 13B _4, revolves around the rotating shaft 11. That is, the planetary roller 13 </ b> A rotates by the rotational force received from the outer periphery of the rotating shaft 11, and the planetary roller 13 </ b> A rolls around the inner periphery of the outer ring member 12 and revolves.

  The spiral ridge 13C on the inner periphery of the outer ring member 12 is a spiral ridge extending obliquely with respect to the circumferential direction. On the other hand, the circumferential groove 13D on the outer periphery of the planetary roller 13A is a groove extending in parallel to the circumferential direction. In this embodiment, a circumferential groove 13D having a lead angle of 0 degrees is provided on the outer periphery of the planetary roller 13A. However, instead of the circumferential groove 13D, a spiral groove having a lead angle different from that of the spiral protrusion 13C may be provided. Good.

  The outer ring member 12 is supported on the inner surface of the caliper housing 25 so as to be movable in the axial direction. A contact portion of the inner surface of the caliper housing 25 with respect to the outer ring member 12 is a cylindrical surface. The outer ring member 12 has a concave portion 29 that engages with a convex portion 28 formed on the back surface of the friction pad 15, and is prevented from rotating with respect to the caliper housing 25 by the engagement of the convex portion 28 and the concave portion 29. .

The carrier 13B extends in the axial direction between a pair of carrier plates 13B ₁ and 13B ₂ facing in the axial direction with the planetary roller 13A interposed therebetween, and the planetary rollers 13A adjacent in the circumferential direction, and is formed in the carrier plate 13B ₁ and 13B _2. having a connecting portion 13B ₃ for connecting to each other, and a roller shaft 13B ₄ which rotatably supports the respective planetary rollers 13A. Each of the carrier plates 13B ₁ and 13B ₂ is formed in an annular shape that penetrates the rotating shaft 11, and a sliding bearing 30 that is in sliding contact with the outer periphery of the rotating shaft 11 is mounted on the inner periphery thereof.

Both end portions of the roller shaft 13B ₄ is movably supported in the radial direction of the outer ring member 12 in the long hole 31 formed on a pair of carrier plate _13B 1, 13B _2. Further, at both ends of the roller shaft 13B _4, the elastic ring 32 so as to circumscribe the roller shaft 13B ₄ of all of the planetary rollers 13A in the circumferential direction spaced is stretched. The elastic ring 32 prevents slipping between the planetary roller 13 </ b> A and the rotary shaft 11 by pressing each planetary roller 13 </ b> A against the outer periphery of the rotary shaft 11.

  A magnetic load sensor 16 according to the first embodiment of the present invention shown in FIGS. 5A and 5B is provided behind the outer ring member 12 in the axial direction. The load sensor 16 has a function of receiving the reaction force from the friction pad 15 from the linear motion conversion mechanism (planetary roller screw mechanism) 13 side and detecting the magnitude of the load caused by the reaction force (braking force of the brake). doing. The load sensor 16 includes a flange member 16A that generates a deflection when a load is input from the front in the axial direction, and a support member 16B that supports the flange member 16A from the rear in the axial direction at a position shifted radially from the point of application of the load. And a magnetic target 16C that generates magnetic flux and a magnetic sensor 16D that detects the magnetic flux generated by the magnetic target 16C.

  The flange member 16A is a ring-shaped member formed of a metal such as iron. The support member 16B is formed of a metal such as iron and is fitted on the outer peripheral edge of the flange member 16A. The outer peripheral edge of the support member 16B is supported by the inner surface of the caliper housing 25 so as not to move. A cylindrical portion 16E is continuously provided on the inner peripheral side of the support member 16B so as to face the inner diameter side of the flange member 16A. A plurality of bearings 33 are mounted on the inner periphery of the cylindrical portion 16E at intervals in the axial direction, and the rotary shaft 11 and the load sensor 16 can be rotated relative to each other around the shaft. The magnetic target 16C is fixed to the inner periphery of the flange member 16A. The magnetic sensor 16D is fixed to the outer periphery of the cylindrical portion 16E of the support member 16B so as to face the magnetic target 16C in the radial direction.

  The flange member 16A and the support member 16B are provided with an anti-rotation mechanism 34 that prevents the members 16A and 16B from rotating relative to each other around the axis (see FIG. 5). The rotation prevention mechanism 34 includes a first engagement portion 34A formed on the outer peripheral surface of the flange member 16A and a second engagement portion 34B formed on the inner peripheral surface of the support member 16B to which the flange member 16A is fitted. It consists of. Each of the first engagement portion 34A and the second engagement portion 34B is a flat surface having a normal line perpendicular to the direction of relative rotation (tangential direction). The first engaging portion 34A and the second engaging portion 34B are in surface contact with each other. By this surface contact, the flange member 16A and the support member 16B are engaged, and relative rotation around the axis is prevented.

Between each planetary roller 13A and the carrier plate 13B ₂ of the axially rearward thrust bearing 35 which rotatably supports the planetary rollers 13A is incorporated. Between the planetary roller 13A in the axial direction behind the carrier plate 13B ₂ and the load sensor 16 (the flange member 16A), a thrust plate 36 which revolves together with the carrier plate 13B _2, revolve in the thrust plate 36 A supporting thrust bearing 37 is incorporated.

The load sensor 16, the thrust plate 36, via the thrust bearing 37, by supporting the carrier plate 13B ₂ in the axial direction, and restrict the movement of the axially rearward of the carrier 13B. The carrier plate 13B ₁ of the axial forward movement of the axially forward is restricted by the stop ring 38 attached to the axial forward end of the rotary shaft 11. Therefore, the carrier 13B is restricted from moving in the axially forward and axially backward directions, and the planetary roller 13A held by the carrier 13B is also restricted from moving in the axial direction.

  A seal cover 39 that closes the opening at the front end in the axial direction of the outer ring member 12 is attached to an end portion in the axial direction of the outer ring member 12. The seal cover 39 prevents foreign matter from entering the outer ring member 12. Further, one end of a cylindrical bellows 40 formed to be extendable and contractible in the axial direction is fixed to an axially forward end portion of the outer ring member 12, and the other end of the bellows 40 is an opening in the axially forward direction of the caliper housing 25. It is fixed to the edge. The bellows 40 prevents foreign matter from entering between the sliding surfaces of the outer ring member 12 and the caliper housing 25.

  When the planetary roller screw mechanism 13 rotates the electric motor 10, the rotation of the electric motor 10 is input to the rotary shaft 11 via the speed reduction mechanism 26, and the planetary roller 13A revolves while rotating (see FIG. 4). At this time, the outer ring member 12 and the planetary roller 13A relatively move in the axial direction due to the difference in the lead angle between the spiral protrusion 13C and the circumferential groove 13D, but the planetary roller 13A is restricted from moving in the axial direction together with the carrier 13B. Therefore, the planetary roller 13A does not move in the axial direction, and the outer ring member 12 moves in the axial direction. Here, when the rotation in the direction in which the outer ring member 12 moves forward in the axial direction is input from the electric motor 10 to the rotation shaft 11, the outer ring member 12 presses the friction pad 15, thereby causing the friction pad shown in FIG. 14 and 15 are pressed against the brake disc 17, and a braking force is applied to the wheels that rotate integrally with the brake disc 17. When the rotation in the direction in which the outer ring member 12 moves rearward in the axial direction is input from the electric motor 10 to the rotary shaft 11, the friction pads 14 and 15 shown in FIG. The braking force is released.

When the outer ring member 12 moves forward in the axial direction and the brake disc 17 is pressed by the friction pads 14 and 15, the rearward in the axial direction is applied to the flange member 16 </ _b > A of the load sensor 16 via the carrier plate 13 </ _b > B ₂ and the thrust bearing 37. A load due to the reaction force toward is applied. With this load, the flange member 16A is deflected in the axial direction (see the arrow in FIG. 5B), and the magnetic target 16C and the magnetic sensor 16D are relatively displaced in the axial direction along with this deflection. Then, the output signal of the magnetic sensor 16D changes corresponding to this relative displacement. By grasping in advance the relationship between the magnitude of the output signal and the magnitude of the axial load input to the flange member 16A, the axial load applied to the flange member 16A is determined based on the output signal of the magnetic sensor 16D. The size can be detected.

  By interposing the thrust bearing 37 between the linear motion conversion mechanism 13 and the load sensor 16 as described above, the load sensor 16 (flange member 16A) rotates around the axis as the linear motion conversion mechanism 13 operates. However, when a repeated load is applied from the linear motion conversion mechanism 13 side, the rotational force from the linear motion conversion mechanism 13 side is slightly transmitted to the load sensor 16 side through the thrust bearing 37. May be. Even if the rotational force is transmitted in this way, by providing the rotation prevention mechanism 34 as described above, it is possible to prevent the flange member 16A receiving the rotational force from the thrust bearing 37 and the support member 16B from rotating relative to each other. High detection accuracy by the load sensor 16 can be ensured.

  Further, by bringing the flat surfaces of the first engagement portion 34A and the second engagement portion 34B into surface contact, the deformation direction of the flange member 16A (see the arrow in FIG. 5B) and the contact surface between the flat surfaces. Are parallel to each other. Then, the frictional resistance on the contact surface is unlikely to become a hysteresis of the sensor output, and the influence of the frictional resistance on the sensor output can be reduced as much as possible. For this reason, the detection accuracy by the load sensor 16 can be further improved.

  6A and 6B show a second embodiment of the load sensor 16 according to the present invention. The load sensor 16 is the same as the load sensor 16 according to the first embodiment in that it includes a flange member 16A, a support member 16B, a magnetic target 16C, and a magnetic sensor 16D, but the load according to the first embodiment. Unlike the sensor 16, the support member 16B is not directly fitted into the flange member 16A, but both the flange member 16A and the support member 16B are fitted into the inner diameter side of the housing 16F that houses the flange member 16A and the support member 16B. Is different.

  The rotation prevention mechanism 34 according to the second embodiment includes a first engagement portion 34A formed on the outer peripheral surface of the flange member 16A, a second engagement portion 34B formed on the outer peripheral surface of the support member 16B, and a housing 16F. And a third engagement portion 34C formed on the inner peripheral surface of the first engagement portion 34C. Each of the first engaging portion 34A, the second engaging portion 34B, and the third engaging portion 34C is a flat surface having a normal line perpendicular to the relative rotation direction (tangential direction).

The first engaging portion 34A and the third engaging portion 34C, and the second engaging portion 34B and the third engaging portion 34C are in surface contact with each other. By this surface contact, the flange member 16A and the housing 16F, and the support member 16B and the housing 16F are engaged with each other, and relative rotation about the axes of the flange member 16A and the support member 16B is prevented via the housing 16F. . The outermost diameter portion of the support member 16B is abutment portion 16B ₁ facing the flange member 16A is extended. The abutment portion 16B ₁ has a function as a spacer to maintain the axial position of the flange member 16A and the support member 16B to a predetermined value.

  Thus, by engaging the flange member 16A and the housing 16F, and the support member 16B and the housing 16F, respectively, the shapes of the outermost diameter portions of the first engagement portion 34A and the second engagement portion 34B are changed in the axial direction. Thus, the same shape can be obtained, and the processing cost can be suppressed.

7A and 7B show a third embodiment of the load sensor 16 according to the present invention. The load sensor 16 is the basic structure is the same as load sensor 16 according to the second embodiment, the abutment portion 16B ₁ of the support member 16B constituting the load sensor 16 according to the second embodiment, the support It differs from the member 16B in that it is a bumping member 16G which is a separate member.

  The rotation prevention mechanism 34 according to the third embodiment includes a first engagement portion 34A formed on the outer peripheral surface of the flange member 16A, a second engagement portion 34B formed on the outer peripheral surface of the support member 16B, and the housing 16F. The third engaging portion 34C is formed on the inner peripheral surface of the first member, and the striking member 16G is provided between the flange member 16A and the support member 16B. Each of the first engaging portion 34A, the second engaging portion 34B, and the third engaging portion 34C is a flat surface having a normal line perpendicular to the relative rotation direction (tangential direction).

  The first engaging portion 34A and the third engaging portion 34C, and the second engaging portion 34B and the third engaging portion 34C are in surface contact with each other. By this surface contact, the flange member 16A and the housing 16F, and the support member 16B and the housing 16F are engaged with each other, and relative rotation about the axes of the flange member 16A and the support member 16B is prevented via the housing 16F. . The abutting member 16G has an annular shape, and the outer diameter thereof is the same as the inner diameter of the central portion in the circumferential direction of the second engaging portion 34C formed on the support member 16B. Thus, by using the support member 16B and the impact member 16G as separate members, the shape of the support member 16B can be simplified, and the processing cost can be reduced.

  A fourth embodiment of the load sensor 16 according to the present invention is shown in FIGS. The load sensor 16 is common to the load sensor 16 according to the first to third embodiments in that it includes a flange member 16A, a support member 16B, a magnetic target 16C, and a magnetic sensor 16D. The configuration of 34 is different.

  The rotation prevention mechanism 34 according to the fourth embodiment includes a groove-shaped first engagement portion 34A extending in the rotation axis direction formed on the outer peripheral surface of the flange member 16A and a rotation formed on the inner peripheral surface of the support member 16B. A groove-like second engaging portion 34B facing the first engaging portion 34A extending in the axial direction, and a rod-like engaging member inserted into a hole formed by the first engaging portion 34A and the second engaging portion 34B (Key member) 41. The engaging member 41 engages with the inner surface of the first engaging portion 34A and the inner surface of the second engaging portion 34B, respectively, and relative to the flange member 16A and the supporting member 16B around the axis via the engaging member 41. Rotation is prevented.

  FIGS. 9A and 9B show a fifth embodiment of the load sensor 16 according to the present invention. The load sensor 16 is formed by penetrating radially outwardly from a radially engaging hole-shaped first engagement portion 34A formed on the outer peripheral surface of the flange member 16A and the inner peripheral surface of the support member 16B. The cut-out second engaging portion 34B and the first engaging portion 34A and the rod-like engaging member (locking pin) 42 inserted into the second engaging portion 34B are configured. The engaging member 42 is engaged with the inner surface of the first engaging portion 34A and the inner surface of the second engaging portion 34B, respectively, and the flange member 16A and the supporting member 16B are arranged relative to each other around the axis through the engaging member 42. Rotation is prevented.

  The electric brake device and the load sensor 16 according to each of the above embodiments are merely examples, and it is an object of the present invention to prevent relative rotation around the axis between the flange member 16A and the support member 16B simply and reliably. As long as the above can be solved, the shape, number, arrangement, material, and the like of each member constituting the electric brake device including the load sensor 16 can be appropriately changed. For example, in each of the embodiments described above, the rotation prevention mechanism 34 is provided only at one circumferential position such as the flange member 16A. However, a plurality of circumferential positions (for example, a two-face width is formed on the flange member 16A). ).

DESCRIPTION OF SYMBOLS 10 Electric motor 11 Rotating shaft 12 Linear motion member (outer ring member)
13 Linear motion conversion mechanism (planetary roller screw mechanism)
15 friction pad 16 load sensor 16A flange member 16B support member 16C magnetic target 16D magnetic sensor 16F housing 34 anti-rotation mechanism 34A first engagement portion 34B second engagement portion 34C third engagement portion 41 engagement member (key member)
42 Engagement member (locking pin)

Claims (6)

A flange member (16A) that generates a deflection by receiving a load from the front in the axial direction;
A support member (16B) for supporting the flange member (16A) from the rear in the axial direction at a position shifted in the radial direction from the point of application of the load;
A magnetic target (16C) that is provided on one of the flange member (16A) or the support member (16B) and generates magnetic flux;
A magnetic sensor (16D) provided on the other of the flange member (16A) or the support member (16B) and detecting a magnetic flux generated from the magnetic target (16C);
An anti-rotation mechanism (34) for preventing relative rotation about an axis between the flange member (16A) and the support member (16B);
Load sensor with The rotation prevention mechanism (34)
A first engaging portion (34A) formed on the flange member (16A);
A second engagement portion (34B) formed on the support member (16B);
The load sensor according to claim 1, wherein the relative rotation is prevented by engagement of the first engagement portion (34 </ b> A) and the second engagement portion (34 </ b> B).   The first engagement portion (34A) and the second engagement portion (34B) have a flat surface having a normal line perpendicular to the direction of the relative rotation, and the first engagement portion (34A) and the The load sensor according to claim 2, wherein the engagement is performed by surface contact of the second engagement portion (34 </ b> B). The rotation prevention mechanism (34)
A housing (16F) for housing the flange member (16A) and the support member (16B);
A first engaging portion (34A) formed on the flange member (16A);
A second engagement portion (34B) formed on the support member (16B);
A third engagement portion (34C) formed on the inner surface side of the housing (16F);
The first engagement portion (34A) and the third engagement portion (34C), and the second engagement portion (34B) and the third engagement portion (34C). The load sensor according to claim 1, wherein the relative rotation is prevented by engagement. The rotation prevention mechanism (34)
A first engaging portion (34A) formed on the flange member (16A);
A second engagement portion (34B) formed on the support member (16B);
Engaging members (41, 42);
The relative rotation is prevented by engaging the engaging member (41, 42) so as to be interposed in the first engaging portion (34A) and the second engaging portion (34B). The load sensor according to 1. An electric motor (10);
A rotating shaft (11) that rotates about an axis by the rotational driving force of the electric motor (10);
A linear motion member (12) movably provided in the axial direction of the rotation shaft (11);
A linear motion conversion mechanism (13) for converting the rotation of the rotary shaft (11) into an axial movement of the linear motion member (12);
A friction pad (15) provided on one axial side of the linear motion member (12) and moving in the axial direction along with the axial movement of the linear motion member (12);
The load sensor (16) according to any one of claims 1 to 5, wherein a load caused by a reaction force from the friction pad (15) is detected.
Electric brake device with

Images