JP2012202983A - Torque measurement unit for brake dynamometer - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a torque measurement unit for a brake dynamometer, capable of accurately measuring a drag torque in a brake including a rotation body and a pressure body to be pressurized against the rotation body.SOLUTION: A torque measurement unit 100 includes a first rocking shaft 111 for supporting a caliper 92 of a disk brake 90. The first rocking shaft 111 is rockably supported with respect to a cylindrically formed second rocking shaft 106. The second rocking shaft 106 is supported onto a support base 103 so as to be rockable around an axial line. A front lock mechanism 112 and a rear lock mechanism 118 are arranged at the both ends of the second rocking shaft 106 so as to allow the first rocking shaft 111 to be removably fixed. A first rocking shaft torque detector constituted by a first rocking shaft load cell 120 and a load cell pressure part 122 is arranged between the first rocking shaft 111 and the second rocking shaft 106, thereby to measure a drag torque.

Description

  The present invention relates to a torque measuring unit for a brake dynamometer that measures torque generated in a pressing body in a brake including a rotating body and a pressing body that presses against the rotating body.

  2. Description of the Related Art Conventionally, there is a brake dynamometer as a test apparatus that performs a performance test of a brake including a rotating body (for example, a rotating disk) and a pressing body (for example, a caliper) that presses against the rotating body. In general, a brake dynamometer is provided with a torque measurement unit for measuring braking torque and drag torque generated in a pressing body in a brake. In such a brake dynamometer torque measuring unit, the braking torque (for example, 3000 Nm) generated in the pressing body during braking with the pressing body sandwiching the rotating body, and the drag torque generated in non-braking when the pressing body releases the rotating body are included. Some (for example, 1 Nm or less) can be measured by one measuring unit.

  For example, in Patent Document 1 below, an outer swing shaft is disposed outside an inner swing shaft that supports a caliper (corresponding to the pressing body) in a disc brake, and these inner swing shaft and outer swing shaft are arranged. And a brake dynamometer torque measuring unit configured to be detachably connected to each other. In this brake dynamometer torque measuring unit, the inner swing shaft and the outer swing shaft are disconnected and the drag torque is measured by swinging only the inner swing shaft. The braking torque is measured by rocking the inner and outer rocking shafts together with the outer rocking shaft and the outer rocking shaft connected.

Japanese Patent Laid-Open No. 08-247864

  However, in the torque measurement unit for a brake dynamometer described in Patent Document 1, the other end of the inner rocking shaft through which the torque meter that measures extremely small drag torque compared with the braking torque passes through the outer rocking shaft. Therefore, there is a problem that the loss of the drag torque generated in the caliper until it is transmitted to the torque meter is large and the measurement accuracy is low.

  The present invention has been made to cope with the above problem, and its purpose is to measure torque for a brake dynamometer capable of accurately measuring drag torque in a brake having a rotating body and a pressing body that is pressed against the rotating body. To provide a unit.

  In order to achieve the above object, a feature of the present invention according to claim 1 is that the shaft is configured to support a pressing body that presses against the rotating body in the brake and the rotational force along the circumferential direction of the rotating body that the pressing body receives. The first oscillating shaft that oscillates around the axis of the shaft body and a second shaft body that is different from the shaft body, and oscillates around the axis of the second shaft body by the rotational force received by the pressing body. A second oscillating shaft that moves, lock means for detachably fixing the first oscillating shaft to the second oscillating shaft so that the first oscillating shaft can be integrally oscillated, a pressing body in the brake, and a second oscillating shaft A first swing shaft torque detector for detecting the rotational force of the first swing shaft, and a second swing shaft for detecting the rotational force of the second swing shaft. A torque detector.

  According to the first aspect of the present invention configured as described above, the brake dynamometer torque measurement unit is detachably coupled to the brake pressing body supported by the first swing shaft and the first swing shaft. A first swing shaft detector is provided for the first swing shaft between the second swing shaft. Therefore, the brake dynamometer torque measuring unit can measure the drag torque generated in the brake pressing body by the first swing shaft detector provided between the press body and the second swing shaft. That is, since the brake dynamometer torque measurement unit measures the drag torque at a position closer to the pressing body than the first swing shaft, the torsional natural frequency (primary torsional frequency) of the first swing shaft is measured. The drag torque can be accurately measured while suppressing the influence.

  According to another aspect of the present invention according to claim 2, in the torque measurement unit for a brake dynamometer, the first swing shaft torque detector is between the first swing shaft and the second swing shaft. It is in that it is provided.

  According to another aspect of the present invention according to claim 2 configured as described above, the torque measurement unit for a brake dynamometer includes a first swing shaft torque detector and a second swing shaft as a first swing shaft torque detector. Between. As a result, the brake dynamometer is compared with a conventional torque measuring unit for a brake dynamometer provided with a torque detector for measuring drag torque between the swing shaft and the base portion supporting the swing shaft. The torque measuring unit can be easily and compactly configured.

  According to another aspect of the present invention according to claim 3, in the torque measurement unit for a brake dynamometer, the second swing shaft is formed of a cylindrical body that covers a part of the outer periphery of the first swing shaft. There is to be.

  According to another aspect of the present invention according to claim 3 configured as described above, the torque measurement unit for a brake dynamometer includes a second swing shaft in which at least a part of the first swing shaft is formed in a cylindrical shape. It is arranged inside. Thereby, the torque measurement unit for brake dynamometers can be configured easily and compactly.

  According to another aspect of the present invention according to claim 4, in the torque measurement unit for a brake dynamometer, the first swing shaft torque detectors are arranged opposite to each other on both side surfaces of the first swing shaft. To be a load cell.

  According to another aspect of the present invention related to claim 4, the torque measurement unit for brake dynamometer has a torque detector for first oscillating shaft opposed to both sides on the side surface of the first oscillating shaft. It is composed of arranged load cells. Therefore, the brake dynamometer torque measuring unit can measure the drag torque by applying a compressive load to each load cell provided on both side surfaces of the first swing shaft. In other words, the brake dynamometer torque measurement unit can have a simple configuration for the first swing axis torque detector, which can reduce the maintenance burden such as clearance adjustment for the load cell and reduce mechanical loss during torque measurement. The drag torque can be accurately measured while being suppressed.

  According to another aspect of the present invention according to claim 5, in the torque measurement unit for a brake dynamometer, the first swing shaft is a portion between the pressing body and the first swing shaft torque detector. The second rocking shaft side of the first rocking shaft torque detector is made of a material having low rigidity.

  According to another aspect of the present invention according to claim 5 configured as described above, the first swing shaft in the brake dynamometer torque measuring unit is provided between the pressing body and the first swing shaft torque detector. The portion on the second rocking shaft side with respect to the first rocking shaft torque detector is made of a material having low rigidity. That is, the first swing shaft is configured by a material having a rigidity necessary for torque transmission at a torque transmission portion between the pressing body and the first swing shaft torque detector, and the first swing shaft torque detection. The part after the machine is made of a material that is less rigid than the torque transmission part. As a result, the portion of the first swing shaft after the first swing shaft torque detector can be made of a material having low rigidity against twisting torque, and the first swing shaft can be reduced in weight. As a result, the drag torque can be reduced. It can measure with high accuracy.

It is a side view which shows roughly the whole structure of the torque measurement unit as a torque measurement unit for brake dynamometers which concerns on this invention. FIG. 2 is a side partial cross-sectional view schematically showing an outline of a cross section at a center line (not shown) of the torque measurement unit shown in FIG. 1. It is sectional drawing which shows typically the cross section of the torque measurement unit seen from the AA line shown in FIG. It is sectional drawing which shows typically the cross section of the torque measurement unit seen from the BB line shown in FIG. It is sectional drawing which shows typically the cross section of the torque measurement unit seen from the CC line | wire shown in FIG. It is sectional drawing which shows typically the cross section of the torque measurement unit seen from the DD line | wire shown in FIG.

  Hereinafter, an embodiment of a torque measurement unit for a brake dynamometer according to the present invention will be described with reference to the drawings. FIG. 1 is a side view schematically showing an overall configuration of a brake dynamometer torque measuring unit 100 (hereinafter simply referred to as “torque measuring unit 100”) according to the present invention. FIG. 2 is a side partial cross-sectional view schematically showing an outline of a cross section at a center line (not shown) of the torque measurement unit 100. Note that each drawing referred to in the present specification is schematically represented by exaggerating some of the components in order to facilitate understanding of the present invention. For this reason, the dimension, ratio, etc. between each component may differ. In each figure, portions not directly related to the present invention are appropriately omitted.

  The torque measuring unit 100 is a measuring device that measures braking torque and drag torque generated in the caliper 92 in the disc brake 90, and constitutes a part of a brake dynamometer as a test device that tests the performance of the disc brake 90. The disc brake 90 is a braking device used for automobiles and motorcycles. The disc brake 90 is mainly formed in a disc shape and sandwiches the rotating disc 91 as a rotating body that rotates together with the wheels from both sides. And a caliper 92 as a pressing body that stops rotating when pressed. The braking torque is a rotational moment along the circumferential direction of the rotary disk 91 that is generated in the caliper 92 when the caliper 92 stops the rotation of the rotary disk with the rotary disk 91 interposed therebetween. In this embodiment, it is assumed that a braking torque of about 5000 Nm is measured. The drag torque is a rotational moment along the circumferential direction of the rotary disk 91 that is generated in the caliper 92 when the caliper 92 contacts the rotary disk 91 in a non-braking state where the rotary disk 91 is not sandwiched. In the present embodiment, a drag torque in the range of 0.05 to 100 Nm is assumed. Note that the magnitudes of the braking torque and drag torque measured by the torque measuring unit 100 are appropriately determined according to the specifications of the disc brake 90. Therefore, it is natural that the torque measuring unit 100 may be configured to measure a braking torque of 5000 Nm or less and a drag torque of 0.05 to 100 Nm or less or more.

(Configuration of torque measurement unit 100)
The torque measurement unit 100 includes a common base 101. The common base 101 is a base portion for supporting the torque measuring unit 100 on the floor surface in a state displaceable in the left-right direction in the figure, and is constructed by assembling steel materials in a rectangular frame shape having the left-right direction in the figure as a long side Has been. A support base 103 is supported on the upper surface of the common base 101 via a linear bearing (also referred to as a linear motion guide or an LM guide) 102. The linear motion bearing 102 is a so-called linear motion system in which a block 102 b that supports a support base 103 is slidably assembled to a rail 102 a that extends along the longitudinal direction of the common base 101. The support base 103 is a plate-like base member to which substantial components of the torque measurement unit 100 are assembled, and is formed by forming a steel plate into a rectangular shape extending in the horizontal direction in the figure.

  A front support column 104 and a rear support column 105 are provided on the upper surface of the support base 103 so as to extend in the vertical direction in the figure. The front strut 104 and the rear strut 105 are columnar members for supporting various members assembled or supported on the second swing shaft 106 and the second swing shaft 106 on the support base 103. The steel plate materials are fixed in a state where they are erected on the support base 103. Of these front struts 104 and rear struts 105, the front struts 104 are formed thicker than the rear struts 105 and are configured with higher rigidity than the rear struts 105. The front column 104 and the rear column 105 are formed with through-holes coaxially with each other, and the second swing shaft 106 is rotated around the axis via the angular bearings 104a and 105a in the respective through-holes. Are supported in a swingable manner.

  The second oscillating shaft 106 is a member that oscillates by the braking torque generated in the caliper 92 of the disc brake 90, and is configured by a shaft body that is formed of a steel material having a rigidity capable of withstanding torsional torque caused by the braking torque. ing. The inner diameter of the second swing shaft 106 is formed to be an inner diameter that can cover the outside of the first swing shaft 111 described later. A front arm body 107 is provided on the outer peripheral portion of the second swing shaft 106 between the front column 104 and the rear column 105. The front arm body 107 is formed in a cylindrical shape covering the outer peripheral portion of the second swing shaft 106, and extends from the cylindrical portion to both sides of the torque measurement unit 100 (the depth direction shown in FIG. 1). 107a is provided. A second swing shaft load cell 108 is connected to one end (downward in the drawing) of the two protruding arm portions 107a of the front arm body 107.

  The second rocking shaft load cell 108 is a dynamic load measuring sensor for measuring the braking torque generated in the caliper 92 of the disc brake 90. In the present embodiment, the second rocking shaft load cell 108 is configured by a sensor capable of measuring a compression load and a tensile load received from the front arm body 107, respectively. One end (upper side in the figure) of the second swing shaft load cell 108 is connected to the second swing shaft 106 via the front arm body 107, and the other end (lower side in the figure) is front. It is detachably connected to the support base 103 via a detector attaching / detaching mechanism 109.

  The front detector attaching / detaching mechanism 109 is for detachably fixing the second rocking shaft load cell 108 to the support base 103, and is fixedly provided on the upper surface of the support base 103. The front detector attaching / detaching mechanism 109 makes the second swing shaft load cell 108 fixed or non-fixed to the support base 103 through operation of an air compressor unit 131 controlled by a control device 130 described later.

  Three hydrostatic bearings 110a, 110b, and 110c are provided inside the second rocking shaft 106, and the first rocking shaft 111 is rotated about the axis via these hydrostatic bearings 110a, 110b, and 110c. Are supported in a swingable manner. The static pressure bearings 110 a, 110 b, and 110 c receive the supply of air pressure from the air compressor unit 131 whose operation is controlled by the control device 130, so that the first swing shaft 111 is moved with respect to the inner peripheral surface of the second swing shaft 106. Support in a non-contact state, levitated.

  The first swing shaft 111 is a member that swings by dragging torque and braking torque generated in the caliper 92 of the disc brake 90, and is configured by a shaft body in which a steel material is formed in a cylindrical shape. The first swing shaft 111 is mainly configured by an inner cylinder shaft 112, a front lock flange 113, a connection flange 114, a torque transmission shaft 115, a rear lock flange 123, and a boss 124.

  Among these, the inner cylindrical shaft 112 is a steel cylindrical member that is accommodated in the second swing shaft 106 and is rotatably held by the static pressure bearings 110a, 110b, and 110c. A front lock flange 113 is assembled to one end (right side in the figure) of the inner cylinder shaft 112. The front lock flange 113 is a member formed by forming a steel material in a substantially cylindrical shape. The front lock flange 113 constitutes a first swing shaft 111 and a front lock mechanism 116 described later. In the front lock flange 113, four hole-shaped fitting portions 113a extending in the horizontal direction in the figure corresponding to the six front hydraulic cylinders 118 constituting the front lock mechanism 116 and a pin member are arranged in the vertical direction. Two press receiving portions 113b are provided. A torque transmission shaft 115 is assembled to one end (right side in the figure) of the front lock flange 113 via a connecting flange 114.

  The connecting flange 114 is a member for connecting the torque transmission shaft 115 to the front lock flange 113, and is formed by forming a steel material in a substantially disk shape. The torque transmission shaft 115 is a shaft-like member for detachably holding the caliper 92 of the disc brake 90 to be measured for braking torque and drag torque and for transmitting the brake torque and drag torque generated in the caliper 92. The steel material is formed in a bottomed cylindrical shape. That is, the caliper 92 is supported by the first swing shaft 111 via the torque transmission shaft 115. The right side in the figure where the caliper 92 is held with respect to the first swing shaft 111 is the front side of the torque measuring unit 100, and the opposite side of the front swing side via the first swing shaft 111 (shown in the figure). The left side is the rear side of the torque measurement unit 100.

  As shown in detail in FIGS. 3 and 4, the front lock mechanism 116 is a mechanical device for removably fixing the first swing shaft 111 to one end (right side in the drawing) of the second swing shaft 106. In addition to the front lock flange 113, the front support frame 117 and the front hydraulic cylinder 118 are mainly used. The front support frame 117 is a steel frame-like member for supporting the front hydraulic cylinder 118 in a state of being opposed to the front lock flange 113 on one end (right side in the drawing) of the second swing shaft 106. The second rocking shaft 106 is fixedly assembled to one end (right side in the figure).

  The front hydraulic cylinder 118 is an actuator in which the lock pin 118 a is advanced and retracted by the operation of the hydraulic pump unit 132 controlled by the control device 130. The front hydraulic cylinder 118 has two front hydraulic cylinders 118 with a lock pin 118a moving forward and backward facing each other in the illustrated horizontal direction with respect to the front support frame 117. A pair of two front hydraulic cylinders 118 in which the lock pins 118a are advanced and retracted so as to face each other in the direction are arranged at the center of the front support frame 117. Of these front hydraulic cylinders 118, the lock pins 118a in the four front hydraulic cylinders 118 arranged in the horizontal direction in the drawing are fitted into the fitting portions 113a of the front lock flange 113 and in the vertical direction. Each lock pin 118a in the two front hydraulic cylinders 118 disposed presses the pressure receiving portion 113b of the front lock flange 113.

  That is, the front lock mechanism 116 is configured such that the lock pin 118a of the front hydraulic cylinder 118 fixed to the second swing shaft 106 via the front support frame 117 is fitted to the front lock flange 113 that constitutes the first swing shaft 111. The first swing shaft 111 is fixed to the second swing shaft 106 by fitting and pressing the joint portion 113a and the press receiving portion 113b, respectively.

  Further, on both side surfaces of the front support frame 117, a first swing shaft load cell 120 and a stopper 121 are provided side by side. The first swing shaft load cell 120 is a dynamic load measuring sensor for measuring drag torque generated in the caliper 92 of the disc brake 90. In the present embodiment, the first rocking shaft load cell 120 is configured by a sensor that can measure the compressive load received from the load cell pressing portion 122 provided on the front lock flange 113. On the other hand, the stopper 121 is a steel for preventing a transient pressing of the load cell pressing portion 122 to the first swing shaft load cell 120 by restricting the displacement of the load cell pressing portion 122 by a predetermined amount or more downward in the figure. It is a block body made.

  As shown in FIG. 5, a load cell pressing portion 122 is provided above the first swing shaft load cell 120 and the stopper 121 in a state of being fixed to the front lock flange 113. The load cell pressing part 122 is a part mainly for pressing the first rocking shaft load cell 120 by the rotation of the first rocking shaft 111, and a support block 122a fixed to both side surfaces of the front lock flange 113; The support block 122a is composed of pressing rods 122b and 122c penetrating both ends (left and right ends in FIG. 1) in the vertical direction in the figure.

  Among these, the support block 122a is a steel part for supporting the pressing rods 122b and 122c, and is formed in a rectangular parallelepiped shape extending in the horizontal direction in the drawing between the front lock flange 113 and the front support frame 117. Yes. The pressing rods 122b and 122c are rod-shaped parts that respectively press the first swing shaft load cell 120 and the stopper 121, and are attached to the support block 122a in a state in which the amount of protrusion can be adjusted from the lower surface of the support block 122a. It has been. In the present embodiment, the pressing rods 122b and 122c are each composed of a bolt and a nut.

  On the other hand, a boss 124 is assembled to the other end (the left side in the figure) of the inner cylinder shaft 112 via a rear lock flange 123. The rear lock flange 123 is a member formed by forming a steel material in a substantially cylindrical shape, and constitutes a first rocking shaft 111 and a rear lock mechanism 125 described later. In the rear lock flange 123, three fitting holes 123a corresponding to the three hydraulic cylinders 127 constituting the rear lock mechanism 125 are formed at substantially equal intervals along the circumferential direction.

  The boss 124 is a shaft body that protrudes and extends from the left end portion of the second swing shaft 106 in the figure, and is configured by forming a steel material into a cylindrical shape. One end (right side in the figure) of the boss 124 is fixed to the rear lock flange 123, and the other end (left side in the figure) is supported by an axial fixing base 128.

  As shown in FIG. 6, the rear lock mechanism 125 is a mechanical device for removably fixing the first swing shaft 111 to the other end (left side in the drawing) of the second swing shaft 106. In addition to the flange 123, it is mainly constituted by a rear support frame 126 and a rear hydraulic cylinder 127. The rear support frame 126 is a substantially ring-shaped member made of steel for supporting the rear hydraulic cylinder 127 in a state where the rear hydraulic cylinder 127 is opposed to the rear lock flange 123 at the rear end portion of the second swing shaft 106. The shaft 106 is fixedly assembled to the rear end portion. The rear hydraulic cylinder 127 is an actuator in which the lock pin 127 a is advanced and retracted by the operation of the hydraulic pump unit 132 controlled by the control device 130. The three rear hydraulic cylinders 127 are arranged on the outer periphery of the rear lock flange 123 substantially equally in a direction in which the lock pins 127a advance and retreat toward the axis of the rear lock flange 123.

  That is, the rear lock mechanism 125 is configured such that the lock pin 127 a of the rear hydraulic cylinder 127 fixed to the second swing shaft 106 via the rear support frame 126 is inserted into the rear lock flange 123 that constitutes the first swing shaft 111. The first swing shaft 111 is fixed to the second swing shaft 106 by being fitted into the hole 123a.

  The axial fixing base 128 is a bearing device for preventing the displacement (displacement) of the first swing shaft 111 in the axial direction (axial direction). The axial fixing base 128 is supported in a substantially cylindrical housing 128a by sandwiching and supporting an axial plate 128b that supports the rear end of the boss 124 between two static pressure bearings 128c and 128d. Prevents displacement in the axial direction. In this case, the static pressure bearings 128c and 128d receive the supply of air pressure from the air compressor unit 131 whose operation is controlled by the control device 130 and support the axial plate 128b. The axial fixing base 128 is fixed on the support base 103 via bearing support columns 129.

  The control device 130 is configured by a microcomputer including a CPU, a ROM, a RAM, and the like. The control device 130 executes a control program (not shown) in accordance with an instruction from an operator, whereby the second swing shaft load cell 108, the first swing shaft, and the like. By controlling the operation of the caliper 92 of the shaft load cell 120, the air compressor unit 131, the hydraulic pump unit 132, the disc holding mechanism 140, and the disc brake 90, the braking torque and the drag torque in the disc brake 90 are measured. The control device 130 includes an input device (not shown) for inputting support from the operator, and a display device (not shown) for displaying the operating state of the control device 130 and the measurement results of braking torque and drag torque. Yes.

  The air compressor unit 131 is a mechanical device that supplies air pressure to the front detector attaching / detaching mechanism 109 and the static pressure bearings 110a, 110b, 110c, 128c, and 128d under the control of the control device 130, and is mainly a compression (not shown). And a relay valve. The hydraulic pump unit 132 is a mechanical device that controls the operation of the control device 130 and supplies hydraulic pressure to the front front hydraulic cylinder 118 and the rear hydraulic cylinder 127, and is mainly configured by a pump and a relay valve (not shown). ing.

  The torque measuring unit 100 also includes a disk holding mechanism 140 (only a part of which is shown in FIGS. 1 and 2) that detachably holds the rotating disk 91 in the disk brake 90 and rotates the held rotating disk 91. Yes. The disk holding mechanism 140 is a flywheel (not shown) that reproduces the inertia of the vehicle to which the drive motor (not shown) that rotates the rotating disk 91 and the disk brake 90 are mounted, the operation of which is controlled by the control device 130. ) And the like.

  The torque measuring unit 100 also includes a brake hydraulic pump unit (not shown) that supplies the caliper 92 with hydraulic pressure for sandwiching the rotating disk 91 in the caliper 92 of the disk brake 90. The operation of the brake hydraulic pump unit is controlled by the control device 130. That is, the caliper 92 of the disc brake 90 sandwiches or releases the rotating disc 91 by the operation control by the control device 130.

(Operation of torque measuring unit 100)
Next, the operation of the torque measurement unit 100 configured as described above will be described. First, an operator who measures the braking torque and drag torque of the disc brake 90 using the torque measurement unit 100 prepares the disc brake 90 to be measured and operates the control device 130 to operate the torque measurement unit 100. Turn on the power. In response to this operation, the control device 130 executes a control program (not shown) so that each unit, specifically, the second swing shaft load cell 108, the first swing shaft load cell 120, the air compressor unit 131, After the hydraulic pump unit 132, the disc holding mechanism 140, and the brake hydraulic pump unit (not shown) are activated, a standby state is waited for an instruction to start measurement from the operator. In this case, the control device 130 operates the air compressor unit 131 to increase the air pressure in the static pressure bearings 110a, 110b, 110c, 128c, and 128d to support the first swing shaft 111 in a floating state. .

  Next, the operator sets the disc brake 90 on the torque measurement unit 100. Specifically, the operator holds the rotary disc 91 in the disc brake 90 on the disc holding mechanism 140 and holds the caliper 92 on the caliper holder 117. Next, the worker performs a measurement operation of the drag torque of the disc brake 90. Specifically, the operator instructs the control device 130 to execute a drag torque measurement process for the disc brake 90.

  In response to this instruction, the control device 130 starts executing the drag torque measurement process of the disc brake 90. Specifically, the control device 130 controls the operation of the hydraulic pump unit 132 to move the lock pins 118a and 127a in the front hydraulic cylinder 118 and the rear hydraulic cylinder 127 backward, thereby causing the front lock flange 113 and the rear lock flange 123 to move. The lock pins 118a and 127a are in a separated state where they are not fitted and pressed. As a result, the first swing shaft 111 is in a non-fixed state with respect to the second swing shaft 106 and is in a state of rotational displacement (swing) alone. In other words, the second swing shaft 106 is not swung by the swing displacement of the first swing shaft 111.

  Further, in this case, the control device 130 controls the operation of the front detector attaching / detaching mechanism 109 by the operation control of the air compressor unit in conjunction with the non-fixing process for setting the first swing shaft 111 in the non-fixed state. The swing axis load cell 108 is separated from the support base 103 to be in a non-fixed state. As a result, the torque cannot be detected by the second rocking shaft load cell 108.

  Next, the control device 130 controls the operation of the disk holding mechanism 140 to rotate the rotating disk 91. As a result, drag torque due to contact with the rotary disk 91 is generated in the caliper 92 in the disk brake 90. The drag torque generated in the caliper 92 is detected by the first swing shaft load cell 120 via the torque transmission shaft 115, the connecting flange 114, and the front lock flange 113 constituting the first swing shaft 111. That is, when the front lock flange 113 constituting the first swing shaft 111 is rotationally displaced by the drag torque generated in the caliper 92, one of the two load cell pressing portions 122 provided on the front lock flange 113 is The first rocking shaft load cell 120 on the side corresponding to the one provided on the front support frame 117 is pressed.

  In this case, the first rocking shaft load cell 120 is supported by the second rocking shaft 106 having a mass sufficient for the drag torque via the front support frame 117 and the first rocking shaft 111. Is not fixed to the second swing shaft 106, and the second swing shaft 106 is not rotationally displaced (swinged). Therefore, the first swing shaft load cell 120 detects the drag torque without being displaced by the pressing of the load cell pressing portion 122 and outputs an electric signal corresponding to the detected drag torque to the control device 130. . As a result, the control device 130 calculates the drag torque value corresponding to the detection signal input from the first swing axis load cell 120 and acquires the drag torque value generated in the caliper 92. That is, the load cell pressing portion 122 provided on the front lock flange 113 and the first swing shaft load cell 120 provided on the front support frame 117 correspond to the first swing shaft torque detector according to the present invention. .

  In this drag torque measurement process, the second rocking shaft load cell 108 for detecting the rocking of the second rocking shaft 106 is in a non-fixed state with respect to the support base 103, and therefore the second rocking shaft. The swing of 106 is not detected. Further, the first rocking shaft 111 has a rear end portion on the left side of the figure fixed to an axial fixing base 128 via a boss 124 to restrict displacement in the axial direction. Thus, the first swing shaft 111 is not displaced (shifted) in the axial direction by the axial force that the caliper 92 receives by contact with the rotary disk 91. Thereby, the first swing shaft load cell 120 can detect the drag torque generated in the caliper 92 with higher accuracy.

  Next, the operator performs a measurement operation of the braking torque of the disc brake 90. Specifically, the operator instructs the control device 130 to execute a process for measuring the braking torque of the disc brake 90. In response to this instruction, the control device 130 starts executing the measurement process of the braking torque of the disc brake 90. Specifically, the control device 130 controls the operation of the hydraulic pump unit 132 to advance the lock pins 118a and 127a in the front hydraulic cylinder 118 and the rear hydraulic cylinder 127, thereby causing the front lock flange 113 and the rear lock flange 123 to move forward. It is assumed that the lock pins 118a and 127a are joined and pressed. As a result, the first swing shaft 111 is fixed with respect to the second swing shaft 106. That is, the second rocking shaft 106 is rocked depending on the rocking displacement of the first rocking shaft 111.

  Further, in this case, the control device 130 controls the operation of the front detector attaching / detaching mechanism 109 by the operation control of the air compressor unit in conjunction with the fixing process for fixing the first swing shaft 111 to the second swing shaft 111. The shaft load cell 108 is fixedly connected to the support base 103. As a result, the torque can be detected by the second rocking shaft load cell 108.

  Next, the control device 130 puts the disc brake 90 in a braking state by sandwiching the rotating disc 91 in a rotating state with a caliper 92 through operation control of a brake hydraulic pump unit (not shown). As a result, the braking torque generated in the caliper 92 of the disc brake 90 is transmitted to the torque transmission shaft 115, the connecting flange 114, the front lock flange 113, the inner cylinder shaft 112, the rear lock flange 123, and the boss constituting the first swing shaft 111. 124 respectively.

  In this case, the first swing shaft 111 is fixed to the second swing shaft 106 by the front lock mechanism 116 and the rear lock mechanism 125 and integrated with the second swing shaft 106. Therefore, the braking torque transmitted to the integrated second swing shaft 106 and first swing shaft 111 is transmitted to the second swing shaft load cell 108 via the front arm body 107. That is, the braking torque generated in the caliper 92 of the disc brake 90 is detected by the second rocking shaft load cell 108. Therefore, the control device 130 inputs an electrical signal corresponding to the magnitude of the braking torque detected by the second swing shaft load cell 108, calculates a braking torque value corresponding to the input detection signal, and calculates the caliper. The value of the braking torque generated at 92 is acquired. That is, the second rocking shaft load cell 108 provided between the front arm body 107 and the support base 103 corresponds to the second rocking shaft torque detector according to the present invention.

  In this braking torque measurement process, the front lock flange 113 and the front support frame 117 are integrally rotationally displaced (oscillated), so that the braking torque is detected by the first oscillation axis load cell 120. There is no. Further, the first rocking shaft 111 has a rear end portion on the left side of the figure fixed to an axial fixing base 128 via a boss 124 to restrict displacement in the axial direction. Accordingly, the second swing shaft 106 integrated with the first swing shaft 111 is not displaced (shifted) in the axial direction by the axial force that the caliper 92 receives by contact with the rotary disk 91. Thereby, the second swing shaft load cell 108 can detect the drag torque generated in the caliper 92 with higher accuracy.

  Then, the operator who has finished measuring the drag torque and the braking torque generated in the caliper 92 removes the rotary disc 91 and the caliper 92 from the disc holding mechanism 140 and the caliper holder 117, and then finishes the measurement process for the control device 130. Instruct. In response to this instruction, the control device 130, the second rocking shaft load cell 108, the first rocking shaft load cell 120, the air compressor unit 131, the hydraulic pump unit 132, the disc holding mechanism 140 and the brake hydraulic pump unit (FIG. (Not shown) are stopped, and then the power is turned off. Thereby, the measurement operation of the drag torque and the braking torque with respect to the disc brake 90 is completed.

  As can be understood from the above description of operation, according to the above embodiment, the torque measuring unit 100 is detachably connected to the caliper 92 of the disc brake 90 and the first swing shaft 111 supported by the first swing shaft 111. A first oscillating shaft detector comprising a first oscillating shaft load cell 120 and a load cell pressing portion 122 is provided for the first oscillating shaft 111 between the first oscillating shaft 106 and the second oscillating shaft 106. . For this reason, the torque measurement unit 100 can measure the drag torque generated in the caliper 92 of the disc brake 90 by the first swing shaft detector provided between the caliper 92 and the second swing shaft 106. That is, since the torque measurement unit 100 measures the drag torque at a position closer to the caliper 92 than the first swing shaft 111, the influence of the torsional natural frequency (primary torsional frequency) of the first swing shaft 111. The drag torque can be accurately measured while suppressing the above.

  Furthermore, in carrying out the present invention, the present invention is not limited to the above embodiment, and various modifications can be made without departing from the object of the present invention.

  For example, in the above embodiment, the first swing shaft 111 is mainly constituted by the inner cylinder shaft 112, the front lock flange 113, the coupling flange 114, the torque transmission shaft 115, the rear lock flange 123, and the boss 124, and the second. The swing shaft 106 is supported so as to be swingable. However, the first swing shaft 111 is configured to swing around the axis line by the rotational force resulting from the torque generated by the drag torque and the braking torque generated in the caliper 92 while supporting the caliper 92 of the disc brake 90. If it is, it will not necessarily be limited to the said embodiment.

  For example, the first swing shaft 111 can be constituted by a torque transmission shaft 115, a connecting flange 114, and a front lock flange 113. In this case, the first swing shaft 111 can be configured to be directly swingably supported on the support base 103 by a support similar to the front support 104 or the rear support 105 in the above embodiment. Accordingly, the first swing shaft 111 can be reduced in size and weight, and the drag torque measurement system can be improved. Further, since the first swing shaft 111 and the second swing shaft 106 are in a serial positional relationship, the rear lock mechanism 125 is not necessary, and the configuration of the torque measurement unit 100 can be simplified. In this case, the first oscillating shaft 111 and the second oscillating shaft 106 may be formed in a hollow cylindrical shape or a solid rod shape.

  Further, for example, with respect to the torque measurement unit 100 in the above embodiment, the rear lock mechanism 125 is eliminated, and the material of the inner cylinder shaft 112 in the first swing shaft 111 is exposed from the second swing shaft 106 ( Specifically, it may be made of a material (for example, a mild steel material, an aluminum material, or a CFRP (carbon fiber reinforced plastic) material) having a lower rigidity than that of the torque transmission shaft 115, the connecting flange 114, and the front lock flange 113). it can. In other words, the first swing shaft 111 is connected to the load cell pressing portion 122 (first swing shaft load cell 120) from a portion between the caliper 92 and the load cell pressing portion 122 (first swing shaft load cell 120). On the other hand, the portion on the second swing shaft 106 side can be made of a material having low rigidity. That is, the first swing shaft 111 is configured with a material having a rigidity necessary for torque transmission at a torque transmission portion between the caliper 92 and the load cell pressing portion 122 (first swing shaft torque detector). The portion after the load cell pressing portion 122 can be made of a material having rigidity lower than that of the torque transmitting portion. As a result, the portion after the load cell pressing portion 122 (first rocking shaft load cell 120) in the first rocking shaft 111 can be made of a material having low rigidity against twisting torque, and the weight of the first rocking shaft 111 can be reduced. As a result, the drag torque can be accurately measured as a result.

  In the above embodiment, the first swing shaft 111 is fixed to both ends of the second swing shaft 106 by the front lock mechanism 116 and the rear lock mechanism 125, respectively. That is, the front lock mechanism 116 and the rear lock mechanism 125 correspond to the lock means according to the present invention. However, the first swing shaft 111 may be configured to be fixed to at least one end portion of both end portions of the second swing shaft 106. That is, the locking means can be configured only by the front lock mechanism 116 or the rear lock mechanism 125. Further, the front lock mechanism 116 and the rear lock mechanism 125 are not necessarily limited to the above embodiment as long as the first swing shaft 111 can be detachably fixed to the second swing shaft 106. For example, the first oscillating shaft 111 can be detachably fixed to the second oscillating shaft 106 by using a coupling, bolt and nut tightening, or the like.

  In the above-described embodiment, the first swing shaft 111 is supported by the static pressure bearings 110 a, 110 b, 110 c using air pressure with respect to the second swing shaft 106. However, the first oscillating shaft 111 is another type of bearing relative to the second oscillating shaft 106, for example, a fluid bearing such as a hydraulic static pressure bearing, a steel ball or a needle (a roller such as a cylinder or a cone). Rolling bearings such as ball bearings and roller bearings, and magnetic bearings.

  In the above embodiment, the drag torque generated in the caliper 92 includes the load cell pressing portion 122 and the first swing shaft load cell provided between the first swing shaft 111 and the second swing shaft 106. It is detected by the first swing axis torque detector. However, the first swing shaft torque detector is not necessarily limited to the above embodiment as long as it is provided on the first swing shaft 111 between the caliper 92 and the second swing shaft 106. . For example, the torque transmission shaft 115 in the first swing shaft 111 is provided with a front arm body similar to the front arm body 107 in the above embodiment, and the first swing shaft is provided between the front arm body and the support base 103. The load cell 120 may be provided as a first swing axis torque detector.

  In the above embodiment, the load cell pressing portion 122 is provided on the front lock flange 113, and the first swing shaft load cell 120 is provided on the front support frame 117. However, the first rocking shaft load cell 120 may be provided on the front lock flange 113, and the load cell pressing portion 122 may be provided on the front support frame 117 to constitute a first rocking shaft torque detector.

  In the above-described embodiment, the first swing shaft torque detector is provided on both sides of the side surface portion of the first swing shaft 111 and dragged via a compressive load acting on the first swing shaft load cell 120. It was configured to measure torque. However, the drag torque can also be measured by providing only one first swing shaft torque detector on the outer periphery of the first swing shaft 111. In this case, the first oscillating shaft torque detector measures the drag torque via the compression load and the tensile load acting on the first oscillating shaft load cell 120.

  Further, in the above embodiment, the braking torque generated in the caliper 92 is detected by the second rocking shaft load cell 108. That is, the second rocking shaft load cell 108 corresponds to the second rocking shaft torque detector according to the present invention. However, the second swing shaft torque detector may be another type of sensor as long as it can detect the rotational force of the second swing shaft 106 caused by the braking torque generated in the caliper 92, for example, A torque meter or the like may be used.

  In the above embodiment, the control device 130 controls the operation of the front detector attaching / detaching mechanism 109 and interlocks with the fixing process and the non-fixing process of the first swing shaft 111 to the second swing shaft 106. The second swing axis load cell 108 is fixed to the support base 103 and is not fixed. However, when the first swing shaft 111 is not fixed to the second swing shaft 106, the second swing shaft 106 does not swing, so the second swing shaft load cell 108 is not necessarily supported by the support base. 103 is not required to be in a non-fixed state. That is, the torque measurement unit 100 can be configured by omitting the front detector attaching / detaching mechanism 109 and omitting the fixing process and the non-fixing process of the second swing shaft load cell 108 in the control device 130.

  In the above embodiment, the torque measuring unit 100 measures the braking torque and drag torque generated in the caliper 92 of the disc brake 90. However, the torque measuring unit for a brake dynamometer according to the present invention is capable of measuring braking torque and drag torque generated in a pressing body in a brake having a rotating body and a pressing body pressed against the rotating body, and is not necessarily a disc brake. It is not limited to 90. That is, the torque measurement unit for a brake dynamometer according to the present invention can measure the braking torque and drag torque in a brake other than the disc brake 90. For example, the braking torque and the drag torque in the drum brake (not shown) can be measured by the torque measurement unit 100 in the above embodiment. In this case, in the torque measurement unit 100, the torque transmission shaft 115 holds a brake shoe as a pressing body instead of the caliper 92, and the disk holding mechanism 140 holds a cylindrical drum as a rotating body instead of the rotating disk 91. To be configured.

90 ... disc brake, 91 ... rotating disc, 92 ... caliper,
DESCRIPTION OF SYMBOLS 100 ... Torque measurement unit, 101 ... Common base, 102 ... Linear bearing, 103 ... Support base, 104 ... Front support | pillar, 104a ... Angular bearing, 105 ... Rear support | pillar, 105a ... Angular bearing, 106 ... 2nd rocking shaft, 107 DESCRIPTION OF SYMBOLS ... Front arm body, 107a ... Arm part, 108 ... Second rocking load cell, 109 ... Front detector attaching / detaching mechanism, 110a, 110b, 110c ... Static pressure bearing, 111 ... First rocking shaft, 112 ... Inner cylinder shaft, DESCRIPTION OF SYMBOLS 113 ... Front lock flange, 113a ... Fitting part, 113b ... Press receiving part, 114 ... Connection flange, 115 ... Torque transmission shaft, 116 ... Front lock mechanism, 117 ... Front support frame, 118 ... Front hydraulic cylinder, 118a ... Lock Pin, 120 ... load cell for first swing axis, 121 ... Topper, 122 ... load cell pressing part, 122a ... support block, 122b, 122c ... pressing bar, 123 ... rear lock flange, 123a ... insertion hole, 124 ... boss, 125 ... rear lock mechanism, 126 ... rear support frame, 127 ... rear Hydraulic cylinder, 127a ... lock pin, 128 ... axial fixing base, 128a ... housing, 128b ... axial plate, 128c, 128d ... static pressure bearing, 129 ... bearing post,
130 ... Control device, 131 ... Air compressor, 132 ... Hydraulic pump unit,
140: Disc holding mechanism.

Claims (5)

A first swing shaft configured by a shaft body that supports a pressing body that presses against a rotating body in a brake and swings about an axis of the shaft body by a rotational force that is received by the pressing body along a circumferential direction of the rotating body. When,
A second rocking shaft that is composed of a second shaft body different from the shaft body and rocks around the axis of the second shaft body by the rotational force received by the pressing body;
Lock means for detachably fixing the first swing shaft in a state in which the first swing shaft can swing integrally with the second swing shaft;
A first swing shaft torque detector provided on the first swing shaft between the pressing body and the second swing shaft in the brake and detecting the rotational force of the first swing shaft; ,
A torque measurement unit for a brake dynamometer, comprising: a torque detector for a second oscillation shaft that detects the rotational force of the second oscillation shaft. In the torque measurement unit for brake dynamometer according to claim 1,
The torque measurement unit for a brake dynamometer, wherein the torque detector for the first swing shaft is provided between the first swing shaft and the second swing shaft. In the torque measurement unit for a brake dynamometer according to claim 1 or 2,
The torque measuring unit for a brake dynamometer, wherein the second swing shaft is formed of a cylindrical body that covers a part of the outer periphery of the first swing shaft. In the torque measurement unit for a brake dynamometer according to any one of claims 1 to 3,
The torque measuring unit for a brake dynamometer, wherein the torque detector for the first oscillating shaft is a load cell disposed opposite to each other on both side surfaces of the first oscillating shaft. In the torque measurement unit for a brake dynamometer according to any one of claims 1 to 4,
The first swing shaft is a portion on the second swing shaft side with respect to the first swing shaft torque detector from a portion between the pressing body and the first swing shaft torque detector. Torque measurement unit for brake dynamometer, characterized in that is made of material with low rigidity.

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