JP2006119063A - Vibration measuring device and vibration measuring method of auto tensioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To install without restriction even in an engine room of an automobile by realizing space saving of a device for measuring vibration of an auto tensioner. <P>SOLUTION: A plate spring member 34 which is curvedly deformable following rocking of an arm 14 of a rocking member 10 is hooked over between a fixing member 3 and the arm 14 of the rocking member 10 in the auto tensioner 1. Strain of the plate spring member 34 is detected by a strain gage 40, and vibration of the arm 14 of the rocking member 10 is measured on the basis of the detected value. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a vibration measuring device and a vibration measuring method for measuring the vibration of a movable part that pivotally supports a tension pulley in an auto tensioner.

  Conventionally, for example, in a belt-type auxiliary machine drive system for an automobile engine, while applying tension to the belt, damping the tension application operation suppresses vibration (flapping) of the belt so that stable torque transmission can be performed. Autotensioners that have been made known are known.

  Specifically, the auto tensioner is supported by being fixedly attached to an engine, for example, and a spindle portion (shaft portion) of the fixing member that is rotatably fitted and supported at a boss portion. A movable part having a tension pulley rotatably supported at the tip part and a boss part of the movable part are arranged around the boss part, and one end part is locked to the fixed member and the other end part is locked to the movable part. A torsion coil spring that urges the movable portion to rotate in the direction in which the tension pulley presses the belt against the fixed member, and a damping means that attenuates the swing of the movable portion.

  By the way, in order to evaluate the performance of the belt drive system including such an auto tensioner, it is necessary to evaluate the performance of the auto tensioner in addition to the fluctuation of the belt tension. In order to evaluate the performance of the auto tensioner, it is necessary to accurately measure the vibration of the movable part including the tension pulley.

When measuring such vibration of the auto tensioner, conventionally, as shown in Patent Document 1 or the one that measures the rotation angle of the movable part of the auto tensioner with the output resistance value of the potentiometer, A laser displacement meter is arranged for the auto tensioner, and the fluctuation of the distance of the movable part is measured from the reflected light when the laser is applied to the movable part of the auto tensioner to measure the vibration of the movable part (Prior Art 2). It has been known.
JP 2003-42838 A

  However, in the above prior art 1, there is a space for mounting and fixing the potentiometer body to the fixed part of the auto tensioner, and a movable part for oscillating and connecting to the input part (rotating part) of the potentiometer. For example, a jig space is required in a direction along the swing center of the movable portion.

  On the other hand, the latter prior art 2 requires a space for mounting the laser irradiation unit attached at a position away from the auto tensioner.

  That is, in any case, a large installation space is required. For example, for an auto tensioner mounted in an engine accessory drive system mounted on an automobile, the installation space is secured in a narrow space in the engine room. There is a problem that it is difficult to do so and a great restriction is imposed on its installation.

  The present invention has been made in view of such a point, and an object of the present invention is to specify the structure of a system for measuring vibration of a movable part of an auto tensioner, thereby saving the space of the measurement system and It is to be able to be attached without restriction in a room or the like.

  In order to achieve the above object, in the present invention, a deformable flexible member is disposed between the movable portion and the fixed portion of the auto tensioner, and by detecting the distortion accompanying the deformation of the flexible member, The vibration of the movable part was measured.

  Specifically, in the first aspect of the invention, the movable member is supported by the fixed member so as to be swingable, and the pulley is rotatably supported at a portion offset from the swing center, and the pulley presses the belt. An oscillating means for urging the movable part in the direction and an attenuating means for attenuating the swing of the movable part, and measuring the vibration of the movable part with respect to an auto tensioner that automatically adjusts the belt tension. The target is an automatic tensioner vibration measurement device.

  Then, a flexible member that is stretched between the fixed member and the movable portion and can be deformed in a curved manner according to the movement of the movable portion, a strain detecting means for detecting strain of the flexible member, and the strain detecting means And a measuring unit that measures the vibration of the movable part based on the detected value.

  According to the above configuration, when the movable portion supported by the fixing member of the auto tensioner is urged by the urging means, the pulley presses the belt and tension is applied to the belt. Further, when the belt tension changes due to the load variation and the pulley moves with respect to the fixed member together with the movable portion, the movement is attenuated by the attenuating means. As a result, vibrations and fluttering of the belt are suppressed, and stable torque transmission is performed.

  Then, when the movable part moves relative to the fixed part as described above, the flexible member stretched between the fixed member and the movable part is curved and deformed in accordance with the movement of the movable part, and the flexible member Distortion occurs. This distortion is detected by a distortion detection hand, and the measurement part measures the vibration of the movable part based on the detection value of the distortion detection means.

  In this way, the flexible member is spanned between the fixed member and the movable portion, and the deformation distortion is detected and the vibration of the movable portion is measured. Therefore, it is only necessary to provide the flexible member and the strain detecting means for the auto tensioner. Their mounting space is very small, and the vibration measuring device for the auto tensioner can be mounted without restriction even in the engine room of an automobile. Moreover, it can be manufactured at a lower cost than a vibration measuring device using a laser displacement meter.

  In the invention of claim 2, the flexible member is a leaf spring material. This leaf spring material has resilience even if it is deformed, and a desirable flexible member can be easily obtained. In addition, it is good for this leaf | plate spring material to have a spring force of the grade which does not affect the biasing force of the said biasing means.

  According to a third aspect of the present invention, the flexible member is stretched between the fixed member and the movable portion while being fixed to one of the fixed member or the movable portion and held on the other. Thus, the flexible member is not constrained as in the case where the flexible member is fixed to both the fixed member and the movable portion, and the flexible member can be smoothly deformed to accurately measure the vibration of the movable portion.

  According to a fourth aspect of the present invention, the measurement unit sets in advance a characteristic representing the relationship between the detection value of the strain detection unit and the vibration of the movable unit, and based on the characteristic, the measurement value of the movable unit Suppose that it is comprised so that a vibration value may be calculated. Thus, the vibration measurement of the movable part is performed smoothly.

  In the fifth aspect of the invention, the movable portion includes an arm whose base end portion is swingably supported by the fixed member, and whose pulley is pivotally supported at the distal end portion. As a result, space saving and cost reduction of the vibration measuring device of the arm type auto tensioner can be achieved.

  According to a sixth aspect of the present invention, there is provided a movable portion that is supported by a fixed member so as to be swingable, a pulley that is rotatably supported at a portion that is offset from the swing center, and the movable portion in a direction in which the pulley presses the belt. A method of measuring the vibration of the movable part with respect to an auto tensioner that automatically adjusts the tension of the belt. In this invention, the distortion of the flexible member that is stretched between the fixed member and the movable portion and can be bent and deformed according to the movement of the movable portion is detected, and the vibration of the movable portion is detected based on the detected value. It is characterized by measuring. This invention can achieve the same effects as those of the invention of the first aspect.

  As described above, according to the first and sixth aspects of the present invention, a flexible member that can be bent and deformed is disposed between the fixed member and the movable portion of the auto tensioner, and the movable portion is deformed based on the distortion of the flexible member. By measuring the vibration, it is possible to reduce the mounting space of the measuring device for the auto tensioner, to facilitate the mounting to the engine room of the automobile, and to reduce the price of the vibration measuring device. .

  According to the second aspect of the present invention, since the flexible member is a leaf spring material, a desirable flexible member can be easily obtained.

  According to the invention of claim 3, by fixing the flexible member to one of the fixed member or the movable portion and holding it on the other, the flexible member can be smoothly deformed to accurately measure the vibration of the movable portion. Can do.

  According to the invention of claim 4, the measurement unit that measures the vibration of the movable part based on the detection value of the flexible member has previously set a characteristic that represents the relationship between the detection value of the strain detection means and the vibration of the movable part. Thus, by calculating the vibration value of the movable part from the detection value of the strain detection means based on the characteristics, vibration measurement of the movable part can be performed smoothly.

  According to the fifth aspect of the present invention, the movable portion has an arm-type auto that has a base end portion swingably supported by the fixed member and a tip end portion on which a pulley is pivotally supported. Space saving and cost reduction of the tensioner vibration measuring device can be achieved.

  Hereinafter, the best embodiment of the present invention will be described in detail with reference to the drawings. The following description of the preferred embodiments is merely exemplary in nature and is in no way intended to limit the invention, its application, or its application.

  1 and 2, reference numeral 1 denotes an auto tensioner according to an embodiment of the present invention, and the auto tensioner 1 is used in an auxiliary drive system of an automobile engine as a belt transmission system.

  That is, the auxiliary machine drive system is attached to a rotating shaft of a crank pulley composed of a V-ribbed pulley, for example, an air conditioner compressor (auxiliary machine), which is not shown, but attached to a crank shaft of an engine E mounted on an automobile. The same compressor pulley, the same PS pump pulley attached to the rotating shaft of the power steering pump (auxiliary machine), the same alternator pulley attached to the rotating shaft of the alternator (auxiliary machine), the same idler pulley, and A fan pulley composed of a flat pulley for rotationally driving the cooling fan is provided, and a transmission belt B composed of a V-ribbed belt (shown in phantom lines in FIG. 1) is provided between these pulleys in each pulley composed of the V-ribbed pulley. Is a forward-bending state where the inner surface of the belt is in contact with the pulley, and a flat pulley. The belt is wound in a reverse bending state in which the outer surface of the belt is in contact with the pulley, and is wound in a so-called serpentine layout. The machine is driven.

  In the belt B, the arm type auto tensioner 1 is disposed on the slack side span on the side coming out of the crank pulley, and the auto tensioner 1 automatically presses the slack side span from the belt outer surface side to automatically adjust the belt tension. I try to adjust it.

  As shown in FIG. 3, the auto tensioner 1 includes a fixed member 3 that is attached and fixed to the engine E, a swinging member 10 that is swingably supported by the fixed member 3, and the swinging member 10. A tension pulley 17 comprising a flat pulley that is rotatably supported by a portion offset from the swing center of the moving member 10 (a tip portion of an arm 14 to be described later) and presses the belt B in a reverse bending state, and a torsion torque A torsion coil spring 20 as urging means for urging the oscillating member 10 in the belt pressing direction in which the tension pulley 17 presses the belt B, and three damping means for attenuating the oscillation of the oscillating member 10. It has.

  The fixing member 3 is made of a metal made of, for example, an aluminum alloy, and has a bottomed cylindrical (cup-shaped) fixing member body 4 that opens at one end (the left end in FIG. 3), and a bottom portion of the fixing member body 4 A spindle portion 5 (shaft portion) having a tapered shape, which is concentrically integrated and protrudes from an opening of the fixing member main body 4. A plurality of mounting brackets 6, 6,... Protrude from the outer peripheral surface of the bottom of the fixing member main body 4. In each of the mounting brackets 6, the fixing member 3 is mounted and fixed to the engine E by mounting bolts not shown. I have to.

  Although not shown in the drawings, a spring locking portion including a notch or a through hole cut out from the opening side is formed on the side wall of the fixing member main body 4.

  On the other hand, the oscillating member 10 is made of a metal made of, for example, an aluminum alloy, like the fixed member 3, and includes a bottomed cylindrical oscillating member main body 11 that opens at one end (the right end in FIG. 3). The swing member main body 11 has an outer diameter substantially the same as that of the fixed member main body 4. On the side wall of the swing member main body 11, a spring locking portion (not shown) formed by a notch or a through hole notched from the opening side is formed.

  A cylindrical boss portion 12 is provided on the bottom of the swing member main body 11 so as to project concentrically so as to protrude from the opening of the swing member main body 11. 11 is formed, and the taper angle of the taper hole 13 is substantially the same as the taper angle of the spindle part 5 of the fixing member 3. Has been. The boss portion 12 is externally fitted to the spindle portion 5 of the fixing member 3 from the front end side of the boss portion 12, whereby the oscillating member 10 is oscillated to the spindle portion 5 of the fixing member 3 by the boss portion 12. The fixed member main body 4 and the swing member main body 11 are supported so as to be movable (rotatable), and the openings of the fixed member main body 4 and the swinging member main body 11 are arranged to face each other to form a substantially sealed cylindrical shape.

  A substantially plate-like arm 14 extending outward in the radial direction protrudes from the outer peripheral portion on the bottom wall side of the swing member main body 11, and the tip of the arm 14 is the same as the protruding side of the boss portion 12 with respect to the arm 14. A pulley shaft portion 15 projecting so as to extend in parallel to the axis of the boss portion 12 is formed integrally with the pulley shaft portion 15, and the tension pulley 17 is rotatably supported by the pulley shaft portion 15 via a bearing portion 18. Has been. That is, the tension pulley 17 is supported at a position on the pulley shaft portion 15 that is eccentric from the boss portion 12.

  The torsion coil spring 20 is disposed around the boss portion 12 of the swing member 10 with both end portions (tangs) protruding outward in the radial direction. This one end is locked to the spring locking portion of the fixing member main body 4 and the other end is locked to the spring locking portion of the swinging member main body 11. Further, the torsion coil spring 20 is interposed between the fixed member main body 4 and the swing member main body 11 while being compressed in the axial direction, and the torsion torque in the direction in which the coil diameter of the torsion coil spring 20 is expanded, The swing member 10 is urged to rotate in a belt pressing direction (counterclockwise direction in FIG. 1) in which the tension pulley 17 presses the belt B.

  Further, three damping means for damping the swing of the swing member 10 will be described. First, a tapered cylindrical resin is provided between the spindle portion 5 of the fixed member 3 and the boss portion 12 of the swing member 10. An insert bearing 22 made of metal is interposed. The insert bearing 22 is locked and fixed to the spindle portion 5 so as not to rotate. The outer peripheral surface of the insert bearing 22 is in sliding contact with the inner peripheral surface of the boss portion 12 so as to attenuate the rotation of the swing member 10. I have to.

  A resin spring support 23 as a second damping means is disposed around the boss portion 12 of the swing member 10. The spring support 23 is disposed between the boss portion 12 and the torsion coil spring 20, and has a substantially cylindrical sliding contact portion 23a that is pressed against the outer peripheral surface of the boss portion 12 by the reaction force of the torsion torque of the torsion coil spring 20. It has a flange portion 23b that protrudes radially outward from the end of the boss portion 12 on the distal end side of the slidable contact portion 23a, is pressed in the axial direction by the torsion coil spring 20, and is pressed and fixed to the inner bottom surface of the fixing member body 4. The sliding contact portion 23a of the spring support 23 is pressed by the torsion coil spring 20 and pressed against the boss portion 12 of the swing member 10, and the boss portion 12 is also pressed and pressed against the insert bearing 22, thereby swinging. The rotation of the member 10 is attenuated.

  Further, the tip end portion of the spindle portion 5 of the fixing member 3 passes through a tapered hole 13 (bottom wall of the swinging member main body 11) in the boss portion 12 and protrudes to the outer surface side. A disk-shaped plate member 26 made of metal for preventing the moving member 10 from being fixed is fixedly secured by caulking or the like so as not to rotate. A small-diameter resin thrust washer 24 is sandwiched between the plate member 26 and the outer surface of the swinging member main body 11 (the end surface of the boss portion 12). Slidably contacts the outer surface of the swing member main body 11 to attenuate the swing of the swing member 10.

  A vibration measuring device 30 for measuring the vibration of the arm 14 of the swing member 30 is provided for the auto tensioner 1 having the above configuration. That is, a bolt screw hole 7 is formed at the center of the front end surface of the spindle portion 5 in the auto tensioner 1, and a fixing jig 32 is fixedly attached to the bolt screw hole 7 so as not to rotate. The fixing jig 32 is substantially bolt-shaped, and includes a mounting screw portion 32a that is screwed into the bolt screwing hole 7, and a head portion 32b in which the mounting screw portion 32a is integrally formed on the back surface. The head portion 32b is provided with a shaft-like attachment portion 32c integrally formed so as to protrude concentrically (also concentrically with the attachment screw portion 32a), and the head screw portion 32b is turned by bolting the attachment screw portion 32a. By screwing and fastening into the joint hole 7, the head portion 32 b and the attachment portion 32 c are integrally fixed to the spindle portion 5 in a state where the head portion 32 b protrudes from the front end surface of the spindle portion 5.

  A leaf spring fixing member 31 is attached to the attachment portion 32c of the fixing jig 32 so as not to rotate, and a leaf spring material 34 as a flexible member is fixedly supported on the leaf spring fixing member 31. That is, the leaf spring fixing member 31 is a ring-shaped member having an outer diameter substantially the same as that of the spindle portion 5, and a part of the circumferential direction thereof is cut and separated in a slit shape in the radial direction. A spring fixing portion 31a is configured. The outer peripheral surfaces of the leaf spring fixing members 31 on both sides in the circumferential direction with respect to the spring fixing portion 31a are notched in steps, and screw holes 31b are formed on the side surface of the step portion 31e on one side (left side in FIG. 1). Further, bolt insertion holes 31c are formed in the side surface of the other (right side) step portion 31e so as to extend in a direction substantially orthogonal to the spring fixing portion 31a and to continue through the spring fixing portion 31a. Yes. The leaf spring fixing member 31 has an inner peripheral surface that is substantially opposite to the spring fixing portion 31a in the diameter direction, and extends to the middle portion in the radial direction of the plate spring fixing member 31 so that the outer diameter of the plate spring fixing member 31 is increased. A slit 31 d is formed to facilitate the change, and the leaf spring fixing member 31 is externally fitted to the mounting portion 32 c of the fixing jig 32 so that the spring fixing portion 31 a substantially coincides with the direction of the arm 14. The base end portion of the leaf spring material 34 as a flexible member is sandwiched between the spring fixing portion 31a, the fixing bolt 33 is inserted into the bolt insertion hole 31c of the leaf spring fixing member 31, and the screw portion is inserted into the screw hole 31b. By screwing and fastening, the leaf spring fixing member 31 is deformed so that the outer diameter becomes small, and is fixed and fixed to the outer peripheral surface of the mounting portion 32c of the fixing jig 32 so as not to be relatively rotatable. Element And so as to clamp supports a base end portion of the leaf spring member 34 to the first spring fixing portion 31a. A hole 34a (or an opening) through which the fixing bolt 33 is inserted is formed at the base end portion of the leaf spring material 34.

  The plate spring material 34 is a thin plate (for example, thickness t = 0.3 mm) that extends linearly, and is in a predetermined direction from the plate spring fixing member 31, specifically, the auxiliary machine drive system is in a non-operational state. It extends so as to pass on a plane connecting the axis of the tension pulley 17 (pulley shaft portion 15) and the center of the spindle portion 5 when the engine is stopped.

  On the other hand, on the surface near the tip of the arm 14, bolt fastening (welding may be used) so that a leaf spring holding member 36 made of a plate material bent in a substantially L shape swings integrally with the arm 14. ). The leaf spring holding member 36 is erected so that one half projects from the arm 14, and a slit 37 extending in the length direction of the arm 14 is formed at the center in the width direction of the erected portion. A portion near the tip of the spring member 34 is inserted. As shown in detail in FIG. 4, the width d of the slit 37 is slightly larger than the thickness t of the leaf spring material 34, for example, d = 0.5 mm. The offset portion is slidably held in the slit 37. That is, the leaf spring material 34 is stretched between the spindle portion 5 and the arm 14 of the fixing member 3 while being fixed to the spindle portion 5 and held by the arm 14, and bends as the arm 14 swings. It can be deformed (see FIG. 5).

  Further, in the leaf spring material 34, an intermediate portion between a proximal end portion fitted to the spring fixing portion 31 a of the leaf spring fixing member 31 and a distal end portion portion fitted into the slit 37 of the leaf spring holding member 36. A strain gauge 40 (strain detection means) is attached and fixed to the portion. The strain gauge 40 detects a strain in the intermediate portion as a stress in the strain gauge 40 when the leaf spring material 34 is deformed to generate a strain, and outputs a voltage corresponding to the strain.

  The output of the strain gauge 40 is connected to the measurement unit 42 via the leaf spring fixing member 31 and the like. The measuring unit 42 is installed on the side of the auto tensioner 1 and measures the vibration of the arm 14 of the swing member 10 based on the output voltage (detected value) of the strain gauge 40. Specifically, the measurement unit 42 stores in advance a characteristic (for example, a calculation formula or a data map) that represents the relationship between the output voltage (detected value) of the strain gauge 40 and the vibration of the arm 14. Based on the above, the vibration value of the arm 14 is calculated from the output voltage of the strain gauge 40.

  Therefore, in this embodiment, when each auxiliary machine (air conditioner compressor, power steering pump, alternator, fan) is driven by the auxiliary drive system during operation of the engine E, the torsion coil of the auto tensioner 1 is operated. The swing member 10 is urged to rotate by the spring 20, and the tension pulley 17 at the tip of the arm 14 presses the span of the transmission belt B by this urging force, whereby the tension of the belt B is applied.

  Further, when the arm 14 of the swinging member 10 swings (vibrates) around the spindle portion 5 of the fixed member 3 together with the tension pulley 17 due to the change in the tension of the belt B, the swinging is performed by three damping means, that is, resin. Braking is attenuated by the sliding resistance of the insert bearing 22, the spring support 23, and the thrust washer 24, and the tension of the belt B is automatically adjusted.

  When measuring the vibration around the spindle portion 5 of the arm 14 of the swinging member 10 due to the change in the tension of the belt B, the measurement is performed as follows. With the vibration (swing) of the arm 14, the leaf spring fixing member 31 attached to the spindle portion 5 on the fixing member 3 side via the fixing jig 32 and the arm 14 of the swinging member 10 are attached. The leaf spring material 34 spanned between the leaf spring holding member 36 is bent and deformed in accordance with the movement of the arm 14, and as shown in FIG. When moving in the belt pressing direction and rotating counterclockwise in the figure, the tip of the leaf spring material 34 moves following the arm 14, and the leaf spring material 34 is a leaf spring fixing member in the spindle portion 5. From the base end part fixed to the spring fixing part 31a of 31 to the front end side, the curve is deformed so as to go to the left side in the figure. On the other hand, as shown in FIG. 5B, when the arm 14 moves in the direction opposite to the belt pressing direction due to, for example, an increase in belt tension and rotates clockwise in the figure, the tip of the leaf spring material 34 is Following the movement of the arm 14, the leaf spring material 34 is curved and deformed from the proximal end portion toward the distal end side and toward the right side in the drawing.

  Due to the curved deformation of the leaf spring material 34, stress is generated in the strain gauge 40 attached to the leaf spring material 34, and a voltage corresponding to the stress is output from the strain gauge 40. When the leaf spring material 34 is curved and deformed in two directions, that is, the direction shown in FIG. 5A and the direction shown in FIG. 5B, the voltage output from the strain gauge 40 is different between positive and negative. Yes.

  The output voltage from the strain gauge 40 is input to the measurement unit 42, and in the measurement unit 42, the arm 14 is based on the characteristic in which the relationship between the output voltage (detected value) of the strain gauge 40 and the vibration of the arm 14 is set in advance. The vibration value of is calculated. FIG. 6 shows the vibration of the arm 14 actually measured by the inventor based on the configuration of the above embodiment, and the vibration characteristic of the auto tensioner 1 can be accurately measured.

  In this way, the leaf spring material 34 is stretched between the fixing member 3 and the arm 14 of the swinging member 10, the deformation distortion is detected by the strain gauge 40, and the vibration of the arm 14 of the swinging member 10 is measured. It is only necessary to provide the leaf spring material 34, the fixing jig 32, the leaf spring fixing member 31, the leaf spring holding member 36, and the strain gauge 40 with respect to the tensioner 1, and the mounting space thereof can be extremely small, and the vibration of the auto tensioner 1 can be reduced. The measuring device 30 can be attached without restriction even in an engine room of an automobile. Moreover, it can be manufactured at a lower cost than a vibration measuring device using a laser displacement meter.

(Other embodiments)
In the above-described embodiment, the base end portion of the leaf spring material 34 is fixed to the spindle portion 5 of the auto tensioner 1 and the tip end portion is locked and held by the arm 14. The leaf spring material 34 may be bent and deformed according to the swing of the arm 14 by locking and holding the proximal end portion to the spindle portion 5 and fixing the portion near the distal end to the arm 14. The same effect can be obtained.

  Moreover, in the said embodiment, although the leaf | plate spring material 34 is used as a flexible member, you may use another flexible member and should just be curved and deformable according to the movement of a movable part.

  Furthermore, although the said embodiment applies this invention to the arm type auto tensioner 1, of course, this invention is applicable also to another type of auto tensioner. For example, a cylindrical sleeve is supported on a fixed shaft in a swingable manner, and a pulley shaft having a center offset from the shaft center of the fixed shaft is formed integrally with the sleeve, and a tension pulley can be freely rotated on the pulley shaft. Auto-tensioner with a sleeve type that is supported on the top, an auto-tensioner with a hydraulic damper or piston damper (multi-plate type viscous damper) as a damping means, and an auto-tensioner with a biasing means provided outside the damper, etc. Can be applied to.

  INDUSTRIAL APPLICABILITY The present invention is extremely useful in that it can save space and reduce the cost of an apparatus for measuring vibration of an auto tensioner, and its industrial applicability is high.

It is a front view which shows the vibration measuring apparatus of the auto tensioner which concerns on embodiment of this invention. It is a side view which shows the vibration measuring apparatus of an auto tensioner. It is sectional drawing which shows the internal structure of an auto tensioner. It is a front view which expands and shows the holding structure of a leaf | plate spring material. FIG. 2 is a view corresponding to FIG. 1 and showing a bending deformation of a leaf spring material accompanying an arm swing. It is a figure which shows the specific example of the vibration measurement data of an auto tensioner.

Explanation of symbols

B Transmission belt 1 Auto tensioner 3 Fixed member 10 Oscillating member (movable part)
14 Arm 17 Tension pulley 20 Torsion coil spring 22 Insert bearing (damping means)
23 Spring support (damping means)
24 Thrust washer (damping means)
30 vibration measuring device 31 leaf spring fixing member 34 leaf spring material (flexible member)
36 Leaf spring holding member 37 Slit 40 Strain gauge (strain detection means)
42 Measuring unit

Claims (6)

A movable part supported by a fixed member so as to be swingable, and a pulley rotatably supported at a portion offset from the swing center, and a biasing means for biasing the movable part in a direction in which the pulley presses the belt And an automatic tensioner that automatically adjusts the tension of the belt, and a device that measures the vibration of the movable part.
A flexible member that is spanned between the fixed member and the movable portion and is capable of bending and deforming according to the movement of the movable portion;
Strain detection means for detecting strain of the flexible member;
An automatic tensioner vibration measuring apparatus comprising: a measuring unit that measures vibration of the movable part based on a detection value of the strain detecting means. In the automatic tensioner vibration measuring device according to claim 1,
A vibration measuring device for an auto tensioner, wherein the flexible member is a leaf spring material. In the automatic tensioner vibration measuring device according to claim 1 or 2,
The automatic tensioner vibration measuring apparatus, wherein the flexible member is stretched between the fixed member and the movable portion in a state of being fixed to one of the fixed member or the movable portion and held on the other. In the vibration measuring device for an auto tensioner according to any one of claims 1 to 3,
The measurement unit is configured in advance to set a characteristic representing the relationship between the detection value of the strain detection means and the vibration of the movable part, and to calculate the vibration value of the movable part from the detection value of the strain detection means based on the characteristic. A vibration measuring device for an auto tensioner, characterized in that In the automatic tensioner vibration measuring apparatus according to any one of claims 1 to 4,
An automatic tensioner vibration measuring apparatus, wherein the movable part has an arm on which a base end is swingably supported by a fixed member and a pulley is pivotally supported at a distal end. A movable part supported by a fixed member so as to be swingable, and a pulley rotatably supported at a portion offset from the swing center, and a biasing means for biasing the movable part in a direction in which the pulley presses the belt And an automatic tensioner for automatically adjusting the belt tension, comprising a damping means for damping the swing of the movable part, and measuring the vibration of the movable part,
Detecting the distortion of the flexible member that is spanned between the fixed member and the movable part and can be deformed in accordance with the movement of the movable part;
A vibration measuring method for an auto tensioner, wherein the vibration of a movable part is measured based on the detected value.

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