JP4645558B2 - Dynamic balance testing machine - Google Patents

Description

  The present invention relates to a dynamic balance testing machine that measures an unbalance of a rotating body with high accuracy.

The dynamic balance testing machine of Patent Document 1 has a base and a rotation support member that is erected from the base and rotatably supports a rotating body that is a test target. The rotation support member has a pair of rollers each having an abutting portion that abuts on the peripheral side surface of the rotating body, and a stopper that abuts on an axial end of the rotating body and restricts the axial movement of the rotating body. . The dynamic balance testing machine detects the vibration of the rotating support member when the rotating body rotates in contact with the contact portion of the roller. The dynamic balance testing machine has a tension spring that biases the stopper toward the rotating body so as to balance the thrust force (propulsive force) of the rotating body. Since the stopper is biased by the tension spring by the tension spring, even if the rotor tries to move in the direction of the stopper during the test, the contact state between the stopper and the rotor is maintained and the influence on vibration detection is suppressed. To do.
JP 2000-28468 A

  However, in Patent Document 1, the contact between the rotating body and the stopper is held by the biasing force of the tension spring to the rotating body. The biasing force of the tension spring may be affected by minor vibrations and usage environments. For this reason, the contact between the rotating body and the stopper may not be ensured.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a dynamic balance testing machine capable of accurately and stably measuring vibration accompanying rotation of a rotating body.

Means and effects for solving the problems

  The invention that solves the above-described problems has a base, a rotation support member that rotatably supports the rotating body that is supported by the base, and a vibration detection means that detects vibrations accompanying the rotation of the rotating body. In the dynamic balance testing machine having a roller that contacts the rotating body and a stopper that prevents movement in the axial direction due to the rotation of the rotating body, the support member is inclined at a predetermined angle with respect to the rotating direction of the rotating body. It is a tilting roller that abuts.

  According to the above configuration, the roller in contact with the rotating body is a tilting roller that inclines at a predetermined angle with respect to the rotation direction of the rotating body to be tested and contacts the rotating body. For this reason, a frictional force acts on the tilting roller in a direction inclined at a predetermined angle with respect to the rotating direction of the rotating body. The frictional force rotates the tilting roller in its rotational direction and tries to move the tilting roller in its axial direction. However, since the tilting roller is fixed in the axial direction, it cannot move. Therefore, the tilting roller cancels out the force to move in the axial direction of the tilting roller by moving the rotating body in contact with the tilting roller in the axial direction. Thus, the rotating body receives a thrust force that tends to move in the axial direction from the tilting roller. Due to this thrust force, the rotating body tries to move in a certain direction and comes into contact with the stopper. Therefore, it is possible to detect the vibration accompanying the rotation of the rotating body in a state where the rotating body is shifted to the stopper. Therefore, the vibration accompanying the rotation of the rotating body can be measured stably and accurately.

  As described above, according to the present invention, it is possible to provide a dynamic balance testing machine capable of accurately and stably measuring vibrations accompanying rotation of a rotating body.

  The tilting roller is in contact with being inclined at a predetermined angle with respect to the rotation direction of the rotating body. Here, the rotation direction of the rotating body refers to a direction when the rotating body rotates in the circumferential direction around the axis.

  The rotation support member has at least one tilting roller that comes into contact with the rotation direction of the rotating body. Here, the rotation support member preferably has a pair of tilting rollers. Thereby, the rotating body is supported at two points in the rotation direction, and the rotating body can be stably held.

  It is preferable that the straight line passing between the abutting portions that abut the rotating body of the pair of tilting rollers is inclined with respect to the rotation direction of the rotating body. Thereby, the thrust force in the axial direction of the rotating body is inherited from the contact portion of one tilting roller to the contact portion of the other tilting roller, and the rotating body can be smoothly moved in the axial direction.

  It is preferable that the rotation support member is disposed at both ends in the axial direction of the rotating body. All the rotation support members arranged at both ends of the rotating body in the axial direction have tilting rollers. For this reason, a thrust force in the axial direction can be obtained from both end sides of the rotating body, and the rotating body can be stably offset.

  The rotation support member has a holding plate having a shaft hole that rotatably supports the tilting roller, and the axial direction of the shaft hole is preferably inclined at a predetermined angle with respect to the axial direction of the rotating body. By tilting the shaft hole of the holding plate in this way, the tilting roller can be tilted and brought into contact with the rotation direction of the rotating body. For this reason, by assembling a conventionally used roller in the shaft hole, the roller itself can be used as a tilting roller without changing the design.

  The part of the tilting roller that contacts the rotating body is preferably formed on a protruding curved surface that is provided on the peripheral side surface of the tilting roller and protrudes in the centrifugal direction. Thereby, the contact area between the tilting roller and the rotating body is reduced, and friction can be reduced. Therefore, the vibration of the rotating body can be detected stably.

Example 1
Hereinafter, a dynamic balance testing machine according to an embodiment of the present invention will be described in detail with reference to the drawings.

  As shown in FIG. 1, the dynamic balance testing machine includes a base 47, a rotation support member 4 that is supported by the base 47 and rotatably holds the rotating body 7 to be tested, and vibrations accompanying the rotation of the rotating body 7. And a vibration detection sensor 5 which is a vibration detection means for detecting the vibration. The rotation support member 4 has rollers 11 and 12 that abut the rotation body 7 and rotatably support the rotation body 7, and a stopper 45 that prevents axial movement caused by the rotation of the rollers 11 and 12. The rollers 11 and 12 are tilting rollers which are in contact with the rotating direction of the rotating body 7 at a predetermined angle α ′.

  The base 47 is a horizontally arranged flat plate, and a pair of rotation support members 4 and 4 are erected on the front side A (left side in FIG. 1) and the rear side B (right side in FIG. 1) thereon. Yes. The rotation support members 4 and 4 are arranged with an interval so that the shaft portion 78 of the rotating body 7 can be held from both ends thereof. The rotation support members 4 and 4 are fixed to the base 47 by a fastener such as a bolt (not shown).

  As shown in FIG. 2, the rotation support member 4 has a U-shaped frame member 41 that opens upward, and a flat plate-like upper member 42 that is fixed to the upper portion of the frame member 41 with a bolt. Inside the frame member 41, the vibration mount 2 is suspended by the leaf spring 3. As a result, the vibration mount 2 is elastically supported by the leaf spring 3 and the transmission of external vibration to the vibration mount 2 is suppressed. The leaf spring 3 is fastened with bolts at the upper part of the frame member 41 and the lower part of the vibration mount 2.

  An attachment recess 21 for attaching the holding plate 10 is provided in the upper part of the vibration mount 2. As shown in FIG. 4, the mounting recess 21 is formed by a side surface holding portion 22 that holds the side surface 107 of the holding plate 10 and a back surface holding portion 23 that holds the back surface 108 of the holding plate 10. The side surface holding part 22 and the back surface holding part 23 are formed integrally with the vibration mount 2. After the holding plate 10 is disposed inside the mounting recess 21, the holding plate 10 is fixed to the rear holding portion 23 with bolts 24.

  As shown in FIGS. 3 and 4, the holding plate 10 is fixed to the rear holding portion 23 by shaft holes 101 and 102 that rotatably hold the shaft portions 111 and 121 of the rollers 11 and 12 and bolts 24. And a fixing hole 109. A concave portion 107 is formed in the upper central portion of the holding plate 10 to allow the rotational drive portion to advance and retreat.

  The holding plate 10 has shaft holes 101 and 102 that rotatably support the rollers 11 and 12 and a roller holding surface 100 on which the rollers 11 and 12 are projected. The axial directions of the shaft holes 101 and 102 are inclined at a predetermined angle α with respect to the axial direction of the rotating body 7. In this example, the predetermined angle α is 0.17 °. Further, the roller holding surface 100 is inclined at a predetermined angle α with respect to the axial direction of the rotating body 7.

  The rollers 11 and 12 include shaft core portions 111 and 121 held by the holding plate 10, and roller main body portions 110 and 120 extending wide in the centrifugal direction on the rear side B of the shaft core portions 111 and 121. Collars 116 and 126 are fitted to the shaft core portions 111 and 121, respectively, so that a predetermined distance is provided between the roller main bodies 110 and 120 and the plate holding surface 100 of the holding plate 10. The shaft core portions 111 and 121 are fitted into the shaft holes 101 and 102 of the holding plate 10 and are rotatably held with respect to the holding plate 10 by retaining members 119 and 129.

  Semicircular convex ring portions 112 and 122 that are continuous in the circumferential direction are formed on the side surfaces of the roller main body portions 110 and 120 of the rollers 11 and 12. When the rotating body 7 to be tested is supported on the rollers 11 and 12, the convex ring portions 112 and 122 abut on the side surface 782 of the shaft portion 78 of the rotating body 7.

  As shown in FIG. 1, a stopper 45 that abuts the end 781 of the rotating body 7 at the center of the upper member 42 provided on the upper portion of the rotation holding member 4 and prevents the axial flow of the rotating body 7. Is suspended. The stopper 45 is rotatably held by a bolt 47 with respect to the upper member 42.

  The rotation holding member 4 is equipped with a vibration detection sensor 5 that detects vibration generated with the rotation of the rotating body 7. The vibration detection sensor 5 includes a sensor main body 51 fixed to the frame member 41, a sensor bar 52 extending horizontally from the sensor main body 51 so as to cross the vibration mount 2, and a connection between the sensor bar 52 and the vibration mount 2. And a transmission portion 53 that transmits the vibration of the vibration mount 2 to the sensor bar 52.

  The dynamic balance testing machine has a position reference sensor 8 that detects the rotational position of the rotating body 7. The position reference sensor 8 senses the resin portion 783 embedded in the shaft portion 78 of the rotating body 7 and exposed in a line shape on the side surface 782 of the shaft portion 78, and detects the rotational position of the rotating body 7.

  A clamp mechanism 60 that holds and releases the vibration mount 2 is mounted on the rotation holding member 4. The clamp mechanism 60 includes a clamp main body portion 62 in which a cylinder is mounted, and a grip portion 61 that can be gripped and released by the cylinder 26 when driven by the cylinder. The clamp mechanism 60 releases the vibration mount 2 when measuring the vibration of the rotating body 7, and holds the vibration mount 2 at other times.

  On the extension line in the axial direction of the rotator 7, a drive center 65 that can grip and rotate the rotator 7 is provided.

  Next, the unbalance amount accompanying rotation of the alternator mounted in a motor vehicle etc. as a rotating body is measured using a dynamic balance testing machine.

  First, as shown in FIG. 8, the rotating body 7 is disposed between the drive centers 65 with a conveyance clamp (not shown). The drive center 65 is advanced and inserted into the space between the stopper 45 and the holding plate 10 and the rollers 11 and 12. Then, both end portions 781 of the rotating body 7 in the axial direction are held by the drive center 65. The rotating body 7 is rotated by the drive center 65 to reach a predetermined rotation speed (1320 rpm in this example). The rotating direction of the rotating body 7 is the right direction (clockwise rotation). The clamp mechanism 60 holds the vibration mount 2 in advance.

  Next, as shown in FIG. 9, the drive center 65 is moved backward, and the rotating body 7 that has reached a predetermined rotational speed is placed on the rollers 11 and 12. Next, the vibration mount 2 is released by the clamp mechanism 60. Then, the rotating body 7 continues to rotate in the right direction and moves to the rear side B by the thrust force F. This mechanism will be described with reference to FIGS.

  As shown in FIGS. 4 and 5, the axial directions of the shaft holes 101 and 102 that support the rollers 11 and 12 are inclined at a predetermined angle α with respect to the axial direction of the rotating body 7. For this reason, the axial direction T of the rollers 11 and 12 is also inclined at a predetermined angle α with respect to the axial direction t of the rotating body 7. Further, due to the inclination of the angle α between the axial directions t and T, the rotation direction H of the rollers 11 and 12 is also inclined at a predetermined angle α with respect to the rotation direction h of the rotating body 7. As shown in FIGS. 3 and 7, a tangential plane (a plane including ΔP1P2P3 described later) where the contact point P1 between the roller and the rotating body exists and perpendicular to both radial directions includes a horizontal plane (ΔP1P7P6 described later). The angle α ′ between the rotation directions h and H and the inclination angle α between the axial directions t and T are different from each other.

  Here, the rollers 11 and 12 are brought into contact with the rotating body 7 at the contact portions 113 and 123 of the convex rings 112 and 122 protruding in a semicircular shape in the circumferential direction. The contact portions 113 and 123 are located on the semicircular curved surfaces of the convex rings 112 and 122. As shown in FIG. 3, the rollers 11 and 12 support the side surface 782 of the shaft portion 78 of the rotating body 7 from the obliquely lower side. As shown in FIGS. 5A and 5B, the axial direction T of one (right side) roller 11 is inclined with respect to the axial direction t of the rotating body 7 by an angle α. The contact portion 113 is located on the front side A of the curved top portion 119 of the convex ring 112 and at a portion where the tangent line in the axial direction t of the rotating body and the curved surface of the convex ring 112 are in contact. The contact portion 123 of the other roller 12 (the left side) is on the rear side B of the curved top portion 129 of the convex ring 123, and the portion where the axial tangent of the rotating body 7 and the curved surface of the convex ring 112 contact each other. To position.

  First, the contact portion 113 of one roller 11 will be described with reference to FIG. The axial direction T of the roller 11 is inclined with respect to the axial direction t of the rotating body 7 by an angle α. The rotation direction H of the roller 11 is inclined at an angle α ′ with the rotation direction h of the rotating body 7. Here, a pressing force N due to the gravity of the rotating body 7 acts on the rollers 11 and 12 in a direction perpendicular to the circumferential surface thereof. The roller 11 rotates by friction with the rotating body 7 that rotates by inertia. The frictional force M <b> 1 that the roller 11 receives from the rotating body 7 acts in the rotation direction h of the rotating body 7. Here, as shown in FIG. 6, the rotation direction H of the roller 11 is inclined at an angle α ′ with respect to the rotation direction h of the rotating body 7 at the contact portion 113. For this reason, the frictional force M1 received from the rotating body is inclined forward A with respect to the rotation direction H of the roller. As shown in FIG. 6, when the pressing force of the roller due to the gravity of the rotating body is N and the friction coefficient between the rotating body and the roller is μ, the frictional force M1 received from the rotating body can be expressed as Nμ. The frictional force M1 is decomposed into a force M11 acting in the rotation direction H of the roller 11 and a force M12 acting in a direction perpendicular to the rotation direction H, that is, the axial direction T of the roller. A force M11 acting in the rotation direction H of the roller 11 is represented by Nμcos α ′, and a force M12 acting in a direction (axial direction T) perpendicular to the rotation direction H of the roller 11 is represented by Nμsin α ′. The component M11 in the roller rotation direction H of the frictional force applied to the roller 11 rotates the roller 11. On the other hand, the component M12 in the axial direction T of the roller 11 tries to move the roller 11 to the front side A, but the roller 11 does not move in the axial direction. For this reason, the roller 11 applies a reaction force (−M12) in the opposite direction (rear side B) to the rotating body so as to reduce the force M12. The rotating body 7 receives a reaction force (-M12). The axial direction of the rotating body 7 and the roller 11 is inclined at an angle α. For this reason, the rotator 7 is moved by the force of the component in the axial direction t (−M12 cos α). This moving force is the thrust force F1. That is, the thrust force F1 in the axial direction t of the rotating body 7 is expressed as F1 = −Nμsin α ′ × cos α. Thus, as shown in FIG. 6, the thrust force F1 is directed to the rear side B of the rotating body.

Next, the angle α ′ formed by the rotation direction h of the rotating body 7 and the rotation direction H of the roller 11 is converted into an angle α formed by the axial direction t of the rotating body 7 and the axial direction T of the roller. As shown in FIG. 7, the contact portion 113 is defined as a contact P1. A point obtained by projecting the contact P1 on a horizontal plane including the central axis O of the roller 11 is defined as PP1. A point obtained by projecting the central axis O ′ of the rotating body onto the plane including ΔP1OPP1 is defined as P5. Let P2 be the intersection of the perpendicular L (including the point PP2) including the point P5 and the rotational direction H of the roller. Let P7 be the intersection of the perpendicular L including the point P5 and the plane parallel to the horizontal plane including the point P1. Let PP1 be the intersection of the perpendicular line L including the point P5 and the horizontal plane including the central axis O of the roller. Further, an intersection point between the perpendicular L including the central axis O ′ of the rotating body and the horizontal plane including the central axis O of the roller is defined as PP3. Let P3 be the intersection of the perpendicular L (including the point PP3) including the central axis O ′ of the rotating body and the rotation direction h of the rotating body. Let P6 be the intersection of the perpendicular L including the central axis O ′ of the rotating body and the horizontal plane including the contact point P1. Further, the radius of the roller is R, the radius r of the rotating body, the contact angle formed by the straight line OP1 and the vertical line L from the central axis O of the roller to the contact point P1 (contacting portion 113) is θ, and the central axis O of the rotating body. The contact angle formed by the straight line O′P1 from “′ to the contact P1 and the vertical line L is defined as φ. Then, the frictional force M1 applied to the roller circumferential surface and the component M11 of the frictional force in the roller rotation direction H act on the straight line P1P3 and the straight line P1P2, respectively. The angle formed by the force M11 (P1P2) and the force M1 (P1P3) is equal to the angle α ′ formed between the rotation directions H and h. Since M11 is a component force of M1 in the roller rotation direction, a perpendicular line P3P2 from the straight line P1P3 on which M1 acts to the straight line P1P2 on which M11 acts is perpendicular to P1P2. Therefore, the angle α ′ formed by the straight line P1P3 and the straight line P1P2 is
tanα ′ = P2P3 / P1P2 = rsinφsinα / (rsinφcosα / cosθ)
→ tanαcosθ ＝ tanα '・ ・ ・ Formula I

As shown in FIG. 3, when the distance between the axes of the rollers 11 and 12 is P / 2, the relationship between the distance P / 2 between the rollers and the contact angles θ and φ is
Rsinθ + rsinφcosα = P / 2
→ sinφ = (P-2Rsinθ) / (2rcosα) Equation II

The triangle ΔP1P2P3 is on a plane including the contact point P1 between the rotating body and the roller and the axial directions H and h. When projected onto a horizontal plane including the contact point P1, a triangle ΔP1P7P6 is created. The angle P2P1P7 is equal to the contact angle θ of the roller. From this, the straight line O′P6 is equal to the straight line P5P7 (O′P6 = P5P7),
rcosφ = rsinφcosα / tanθ
→ sinθ / cosθ = sinφcosα / cosφ = tanφcosα
∴sinθ = cosθtanφcosα ・ ・ ・ Formula III
From Equation II,
Rcosθtanφcosα + rsinφcosα = P / 2
∴cosθ = (P / 2−rsinφcosα) / (Rtanφcosα) Formula IV
Substituting Formula IV into Formula I,
tanα ′ = tanα (P / 2−rsinφcosα) / (Rtanφcosα)
α ′ = arc (tan α (P / 2−rsinφcosα) / (Rtanφcosα))... Formula V
Substituting Formula V into the formula F1 = Nμsinα ′ × cosα, F1 is
F1 = Nμsin (arc (tanα (P / 2−rsinφcosα) / (Rtanφcosα))) × cosα Formula VI
It is expressed.

  The contact portion 123 of the other (left side) roller 12 will be described with reference to FIG. Similar to the roller 11, the axial direction T of the roller 12 is inclined with respect to the axial direction t of the rotating body 7 by an angle α. The rotation direction H of the roller 12 is inclined at an angle α ′ with the rotation direction h of the rotating body 7, similarly to the roller 12. Therefore, similarly to the roller 11, the roller 12 also generates a thrust force that moves the rotating body to the rear side B in the axial direction.

  As described above, the rotating body 7 receives the thrust force (F) from the rollers 11 and 12 that respectively hold the shaft portions 78 on the front side A and the rear side B, as shown in FIG. Since the rotating body 7 is inertially rotated, coupled with the thrust force, the rotating body 7 moves to the rear side B while rotating in a spiral shape. As shown in FIG. 10, when the rotating body 7 moves at a predetermined interval in the axial direction, the end portion 782 of the shaft portion 78 comes into contact with the stopper 45, and the movement in the axial direction stops. Since a thrust force is always applied to the rotating body 7, the rotating body 7 performs inertial rotation while continuing to contact the stopper 45 on the rear side B.

  Thus, when the rotating body 7 is in a state of inertial rotation while being in contact with the stopper 45, the crank mechanism 60 is unclamped. The vibration generated by the rotation of the rotating body 7 is measured by the vibration detection sensor 5, and the rotational position of the rotating body 7 is measured by the position reference sensor 8. If the vibration tends to change beyond the allowable value at a predetermined rotational position of the rotating body, it is determined that the rotating body has a poor circumferential balance.

  As described above, the unbalance amount of the rotating body is measured by the dynamic balance testing machine.

  After the measurement, the rotating body is transported to the next process by a transport clamp. In addition, about the rotary body determined that the circumferential balance was bad and unsatisfactory, in the next step, the unbalanced rotational position is cut with a drill or a cutter to remove the unbalance.

  In this example, the rotating body 7 receives a predetermined thrust force in the axial direction from the rollers 11 and 12, and thus can keep contacting the stopper 45 stably. For this reason, it is possible to perform vibration measurement stably and without error.

  As shown in FIG. 5, the straight line 15 passing between the contact portions 113 and 123 that contact the rotating body 7 of the rollers 11 and 12 is inclined at a predetermined angle β with respect to the rotation direction h of the rotating body 7. . For this reason, the thrust force in the axial direction of the rotating body 7 is continuously inherited from the abutting portion 113 of the one roller 11 to the abutting portion 132 of the other roller 12, and the rotating body 7 is smoothly axially moved. Can be moved to.

  The rotation support members 4 arranged at both ends in the axial direction of the rotating body 7 have rollers 11 and 12, respectively. For this reason, a thrust force in the axial direction is obtained from both end sides of the rotating body 7, and the rotating body 7 can be stably offset.

  The axial directions of the shaft holes 101 and 102 provided in the holding plate 10 are inclined at a predetermined angle α with respect to the axial direction of the rotating body 7. For this reason, by assembling the conventionally used rollers in the shaft holes 101 and 102, the roller 11 is in contact with the conventional roller inclined with respect to the rotation direction of the rotating body without changing the design of the roller itself. , 12 can be used.

  The contact portions 113 and 123 of the rollers 11 and 12 are formed in convex ring portions 112 and 122 having curved surfaces that protrude in the centrifugal direction of the rollers 11 and 12 and are curved in a semicircular shape smoothly in the axial direction. For this reason, the contact area between the rollers 11 and 12 and the rotating body 7 is reduced, and friction can be reduced. Therefore, the vibration of the rotating body 7 can be detected stably.

  In the above embodiment, the rotating body is rotated clockwise, but may be rotated counterclockwise. Moreover, you may make the inclination direction of the rollers 11 and 12 into the opposite side to a present Example. In these cases, the thrust force received by the rotating body from the tilting roller is directed to the front side A. For this reason, the rotating body comes into contact with the stopper on the front side A by the thrust force.

  Moreover, in the said Example, although the holding plate 10 and the rollers 11 and 12 in the rotation support member 4 were inclined with respect to a rotating body, you may incline the rotation support member 4 whole with respect to a rotating body. .

(Example 2 to Example 5)
This example is the same as Example 1 except that the roller inclination angle α is changed. The thickness of the holding plate 10 is uniform. As shown in FIG. 11A, in the holding plate 10 on the front side A, shims 9 of various thicknesses are sandwiched between the roller 12 side (left side) end portion of the back surface 108 and the back surface holding member 23. The predetermined angle α is set. As shown in FIG. 11B, in the holding plate 10 on the rear side B, shims 9 of various thicknesses are sandwiched between the roller 11 side (right side) end portion of the back surface 108 and the back surface holding member 23. The predetermined angle α is set. The width H of the holding plate on the front side A and the rear side B is 78 mm, the interval between the shaft holes is 56 mm, and the thickness is 7.8 mm. By sandwiching the shim 9 between the back surface 108 of the holding plate 10, the plate holding surface 100 of the holding plate 10 is inclined at the inclination angle α by the thickness T of the shim 9. The axial directions of the rollers 11 and 12 are inclined at an angle α with respect to the axial direction of the rotating body. The roller abuts at an angle α with respect to the rotational direction of the rotating body.

  In Example 2, the shim thickness is 0.1 mm and the inclination angle α is 0.07 °. In Example 3, the shim thickness is 0.2 mm and the inclination angle α is 0.15 °. In Example 4, the shim thickness is In Example 5, the shim thickness is 0.4 mm and the inclination angle α is 0.30 °. The angle α ′ formed by the rotation direction h of the rotating body and the rotation direction H of the roller is a numerical value calculated by the above formula V from the angle α between the axial directions t and T.

(Comparative example)
In this example, the inclination angle α of the roller is 0 °. A shim is not sandwiched between the holding plate and the rear holding member.

(Evaluation)
For the dynamic balance testing machines of Examples 2 to 5 and the comparative example, the maximum amplitude of vibration was measured and the behavior of the rotating body was observed. The rotating body used for the test was an alternator having a weight (G) of 1800 g and was brought into contact with the roller at a rotational speed of 1320 rpm. The friction coefficient (μ) between the rotating body and the roller is 0.02. The radius r of the shaft portion 78 of the rotating body is 7.5 to 8.5 mm, and the distance (radius R) between the central axes of the rollers 11 and 12 and the contact portions 113 and 123 is 18 mm. The distance P / 2 between the roller 11 and the roller 12 is 19 mm.

  The maximum amplitude of vibration was measured using an FFT analyzer (vibration measuring device) different from the vibration detection sensor of Example 1. The FFT analyzer brought the sensor part into contact with the upper member 42 of the rotation support member 4 and detected vibration transmitted from the rotating body to the upper member. The measurement result was judged. Means best, ○ means good, Δ means almost good, and × means bad.

  The measurement results are shown in Table 1.

  From the table, in the case of Examples 2 to 5, the rotating body was offset in the axial direction. In Examples 2 to 4, the thrust force was appropriate, and the stopper contacted the stopper almost stably. Moreover, in Examples 2-4, compared with Example 5, the maximum amplitude of the frame member was as low as the comparative example. In particular, in Example 3, all the rotating bodies stably contacted the stopper, and the maximum amplitude was not significantly different from the comparative example. In Example 2, compared with Examples 3-5, the thrust force was weak and the flow direction of the axial direction of the rotary body was slow. In Example 5, the thrust force was slightly larger than in Examples 1 to 4, and the rotating body sometimes rebounded in the direction opposite to the thrust direction.

  This shows that it is preferable when the angle α formed by the axial direction T of the roller and the axial direction t of the rotating body is in the range of 0.07 to 0.22 °.

  The present invention is not limited to the above-described embodiments, and it goes without saying that various modifications can be made within the scope of the technical idea described in the claims.

  The dynamic balance testing machine of the present invention can be used for unbalance measurement of various rotating bodies including automobile parts such as alternators and starters.

1 is a perspective view of a dynamic balance testing machine of Example 1. FIG. The front view of the rotation support member of the front side in Example 1. FIG. The front view of the holding plate for demonstrating a holding plate and a roller in Example 1, and a rotary body and a contact state. FIG. 3 is a plan view of a rotation support member in the first embodiment. The top view (a) of a roller and a rotary body for explaining the direction of the frictional force which acts on the contact part of a roller and a roller in Example 1, and the direction of the contact part of the roller with respect to a rotary body are shown. Explanatory drawing (b). FIG. 3 is an explanatory diagram for explaining a frictional force that acts between the rotating body and one of the rollers in the first embodiment. Explanatory drawing for demonstrating the frictional force which acts between a rotary body and the other roller following FIG. Plane explanatory drawing of the dynamic balance testing machine which shows a state when the rotary body in Example 1 is mounted on the roller. Plane explanatory drawing of the dynamic balance testing machine which shows the state which the rotary body is moving to the axial direction in Example 1. FIG. Plane explanatory drawing of the dynamic balance testing machine which shows the state which the rotary body in Example 1 contact | abuts to the stopper. The top view (a) of the rotation support member of the front side in Examples 2-5, and the top view (b) of the rotation support member of the back side.

Explanation of symbols

10: Holding plate, 100: Plate holding surface, 101, 102: Shaft hole, 11, 12: Roller, 110, 120: Roller body, 113, 123: Contact part, 2: Vibrating frame, 3: Plate spring, 4 : Rotation support member, 41: frame member, 42: upper member, 45: stopper, 47: base, 5: vibration detection sensor, 60: clamp mechanism, 7: rotating body, 8: position reference sensor A: front side, B : Back side

Claims (3)

A base, a rotation support member that rotatably supports the rotating body that is supported by the base, and a vibration detection unit that detects vibrations associated with the rotation of the rotating body;
In the dynamic balance testing machine, the rotation support member includes a roller that contacts the rotating body, and a stopper that prevents movement in the axial direction due to rotation of the rotating body.
The dynamic balance testing machine according to claim 1, wherein the roller is a tilting roller that inclines at a predetermined angle with the rotation direction of the rotating body.   The dynamic balance testing machine according to claim 1, wherein the rotation support members are disposed at both ends in the axial direction of the rotating body.   The rotation support member has a holding plate having a shaft hole that rotatably supports the tilting roller, and the axial direction of the shaft hole is inclined at a predetermined angle with respect to the axial direction of the rotating body. The dynamic balance testing machine according to claim 1, wherein the dynamic balance testing machine is characterized by the following.

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