JP2007212143A - Dynamic balancing machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a dynamic balancing machine capable of changing the intervals between rollers with a simple configuration, measuring unbalance of a large number of types of devices under test, and performing accurate unbalance measurements. <P>SOLUTION: By raising bearing racks 5 and 6 at the same oscillating frame 4, connecting the bearing racks 5 and 6 to each other with a feed-screw shaft 26, and moving the bearing racks 5 and 6 by the movement of the feed-screw shaft 26 by a motor 29 for movement, it is possible to adjust the interval between rollers 7a and 8a and the interval between rollers 7b and 8b according to the length of a device under test 11. Since no constituent parts are arranged between the rollers 7a and 7b nor between rollers 8a and 8b in the dynamic balancing machine 1, it is possible to measure unbalance of the device under test 11 having a protrusion part 35. Since a motor 18 for drive is movable with the bearing rack 5, it is possible to accurately measure unbalance. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a dynamic balance testing machine for performing a dynamic balance test on a test object such as a crankshaft.

  2. Description of the Related Art A dynamic balance testing machine for measuring unbalance of a rotating test object such as a crankshaft is known. This type of dynamic balance testing machine is provided along a rotation axis direction of a test object, and includes a plurality of bearing mounts each including a pair of rollers, a vibration frame that supports each bearing mount, a vibration frame, And an elastic body connecting the bed. In the dynamic balance testing machine, a plurality of shaft portions in the rotation axis direction of the device under test are supported by rollers, and the vibration of the vibration frame when the device under test is rotated by the rollers is detected. Measure body disparity.

In such a dynamic balance testing machine, it is of course important to be able to accurately measure the unbalance of the DUT, but it is also important to be able to measure the unbalance of the DUT of different types (length in the rotation axis direction). is there. This is because the length of the object to be tested changes according to its type, and the position of the shaft portion supported by the roller also changes according to the object to be tested.
In Patent Documents 1, 2 and 3, in a dynamic balance testing machine having a plurality of bearing stands each provided with a pair of rollers, the distance between the bearing stands provided with the rollers in the direction of the rotation axis of the DUT can be adjusted. A device capable of measuring the unbalance of specimens having different lengths has been proposed.
Japanese Patent No. 2901987 Japanese Patent No. 2966424 Japanese Utility Model Publication No. 62-25710

However, in the dynamic balance testing machine described in Patent Document 1, vibration frames are individually provided for each pair of rollers, and each vibration frame is provided with an elasticity corresponding to each vibration frame. Since the body is connected to the bed, individual differences between the vibration frames and the elastic bodies may reduce the unbalanced measurement accuracy.
In the dynamic balance testing machine described in Patent Document 2, since a plurality of bearing mounts each provided with a pair of rollers are supported by a single vibration frame, the vibration frame and the unbalance measurement accuracy of the test object are improved. The possibility of individual differences in elastic bodies being affected is eliminated. However, the rollers facing each other in the direction of the rotation axis of the device under test are connected by the same spline shaft. Therefore, when the DUT has a portion that protrudes more than a predetermined amount in the radial direction between the opposing rollers (for example, a crank pin in the crankshaft), the protruding portion interferes with the spline shaft, Such an unbalance of the test object cannot be measured.

  In the dynamic balance testing machine described in Patent Document 3, the drive source for rotating the roller is provided not on the vibration frame but on the bed. Therefore, from the drive source that does not vibrate on the bed side to the roller that vibrates with the vibration frame. The transmission of the driving force may adversely affect the unbalanced measurement accuracy. Further, since the drive source is in the bed, the distance between the drive source and the roller is relatively long, and a complicated transmission mechanism is required between the drive source and the roller.

SUMMARY OF THE INVENTION Therefore, the present invention provides such a dynamic balance testing machine that improves such a conventional apparatus, can change the roller interval with a simpler configuration, and can measure the unbalance of various types of test objects. Main purpose.
Another object of the present invention is to provide a dynamic balance testing machine capable of accurate unbalance measurement.

  According to the first aspect of the present invention, there is provided a vibration frame held on a bed by an elastic body so as to vibrate, detection means for detecting the vibration of the vibration frame, and standing on the vibration frame, A plurality of bearing stands each provided with a pair of rollers for supporting and rotating, and a common rotating shaft pivotally supported by the plurality of bearing stands, and the vibration frame includes a movement guide Means is provided, and at least one of the plurality of bearing stands is guided by the movement guide means so as to be movable on the vibration frame, and any one of the plurality of bearing stands is provided. One bearing stand is provided with a drive source, and a first transmission mechanism for transmitting the driving force of the drive source to the roller and the rotation shaft provided in the bearing stand, and the plurality of bearing stands. The drive source of the gantry And a bearing base other than the bearing base provided with the first transmission mechanism is provided with a second transmission mechanism for transmitting the rotation of the rotary shaft to the roller provided in the bearing base, A spline or a keyway is formed on the rotation shaft, and at least one of the first transmission mechanism and the second transmission mechanism extends in the axial direction of the rotation shaft along the spline or the keyway. It is a dynamic balance testing machine characterized by being made movable.

According to a second aspect of the present invention, in the dynamic balance testing machine according to the first aspect, the drive source is fixed to the bearing mount, and is guided by the movement guide means on the vibration frame together with the bearing mount. The dynamic balance testing machine is characterized by being movable in the axial direction of the rotating shaft.
According to a third aspect of the present invention, in the dynamic balance testing machine according to the first or second aspect, the first transmission mechanism includes at least four timing pulleys and one timing belt, and the driving force of the driving source. The dynamic balance testing machine is characterized in that the rotary shaft and the roller are driven to rotate simultaneously.

  The invention according to claim 4 is the dynamic balance testing machine according to any one of claims 1 to 3, wherein the movement guide means is provided on the vibration frame and connected to the plurality of bearing stands. A longitudinal member for adjusting a distance, wherein the longitudinal member is screw-coupled to at least one of the plurality of bearing mounts, and the at least one bearing screw-coupled to the longitudinal member by rotating the longitudinal member The dynamic balance testing machine is characterized in that the coupling position with the gantry changes, whereby at least one bearing gantry can be moved.

  According to the first aspect of the present invention, since the two or more bearing mounts are erected on the same vibration frame, the individual difference between the vibration frame and the elastic body is determined in the vibration of the vibration frame detected by the detecting means. The resulting influence can be eliminated. At least one of the plurality of bearing mounts is guided by the movement guide means and can move on the vibration frame, and the roller interval can be adjusted according to the length of the test object. Further, only one of the two or more bearing mounts is provided with a drive source, and the driving force of the drive source is transmitted to the rollers of the bearing mount via the first transmission mechanism. Then, it is transmitted to the rollers of the other bearing mount via the second transmission mechanism and the rotating shaft. A spline or keyway is formed on the rotating shaft, and at least one of the first transmission mechanism and the second transmission mechanism is movable along the spline or keyway. Therefore, even if the interval between the first transmission mechanism and the second transmission mechanism changes, the coupling relationship between the first transmission mechanism or the second transmission mechanism and the rotating shaft also moves without hindrance. Therefore, the movement of the first transmission mechanism or the second transmission mechanism does not affect the accuracy of unbalance measurement. In this dynamic balance testing machine, no component is arranged between the roller provided in each bearing gantry and the roller of the bearing gantry adjacent in the rotation axis direction, so that it protrudes in the radial direction of the roller. The test object having such a portion can be supported without causing the protruding part to interfere with the components of the dynamic balance testing machine, and the unbalance of such a test object can be measured.

As a result, the roller interval can be changed with a simple configuration, and the unbalance of various types of test objects can be accurately measured.
According to the second aspect of the present invention, since the drive source is fixed to the bearing stand, the distance between the drive source and the roller can be relatively shortened, and the first transmission mechanism can be simply configured. it can. In addition, since the drive source can move in the direction of the rotation axis together with the bearing mount, errors due to the position of the drive source can be reduced in the accuracy of unbalance measurement when the bearing mount is moved.

As a result, unbalance can be accurately measured with a simple configuration.
According to the invention described in claim 3, in the first transmission mechanism, four timing pulleys corresponding to the pair of rollers, the rotation shaft, and the drive source are connected by one timing belt. Therefore, with the minimum necessary timing pulley and timing belt, that is, with a simple configuration, the driving force of the driving source can be transmitted and the rotating shaft and the roller can be simultaneously rotated.

As a result, unbalance can be accurately measured with a simple configuration.
According to the fourth aspect of the present invention, the two or more bearing mounts are connected by the longitudinal member for adjusting the distance between the bearing mounts. When the longitudinal member is rotated, the connecting position of the at least one bearing base that is screw-coupled with the longitudinal member changes, and the interval between the plurality of bearing bases changes.
As a result, the roller interval can be changed with a simple configuration.

Embodiments of the present invention will be specifically described below with reference to the drawings.
1 is a front view of a dynamic balance testing machine 1 according to an embodiment of the present invention, FIG. 2 is a view taken along the line AA in FIG. 1, and FIG. 3 is a view taken along the line BB in FIG. It is. In FIGS. 1 to 3, parts necessary for explanation are partially cut away to show the internal structure, and parts not directly related to the configuration of the invention (for example, mounting bolts and the like) are omitted. Yes.

As shown in FIG. 1, the bed 2 is brought into a fixed state as necessary, for example, by being fixed to a foundation concrete block embedded in the soil.
On the bed 2, four bar springs 3a, 3b, 3c and 3d as elastic bodies are erected, and the boat-shaped vibration frame 4 is held by the four bar springs 3a to 3d so as to be able to vibrate. Has been. The spring that holds the vibration frame 4 is not limited to a rod shape, and may be a plate shape.

Two bearing mounts 5 and 6 are erected on the vibration frame 4.
These two bearing mounts 5 and 6 are movable to the left and right with respect to the vibration frame 4 as indicated by an arrow X in the figure. The two bearing mounts 5 and 6 are provided with a pair of rollers 7a and 7b and 8a and 8b, respectively. Specifically, as shown in FIG. 2, the rollers 7a and 7b are spaced apart in the front-rear direction, and the rollers 8a and 8b are spaced apart in the front-rear direction as shown in FIG. Has been placed. As shown in FIG. 1, the rollers 7a and 8a are disposed to face each other with a space in the left-right direction, and the rollers 7b and 8b are disposed to face each other with a space in the left-right direction.

The pair of rollers 7a and 7b are rotatably held by bearings 9a and 9b, and the pair of rollers 8a and 8b are rotatably held by bearings 10a and 10b, respectively. Each roller pair 7a and 7b and 8a and 8b support a predetermined shaft portion 36 of the device under test 11 and rotate the device under test 11.
Timing pulleys 13a and 13b are integrally provided at the right ends of the pair of rollers 7a and 7b, respectively. Timing pulleys 14a and 14b are integrally provided at the left ends of the pair of rollers 8a and 8b, respectively.

The bearing stands 5 and 6 are pivotally supported at both axial (left and right) ends of the spline shaft 12 at positions equal to each other in the vertical direction below the pair of rollers 7a and 7b and 8a and 8b. is doing. A spline 15 is formed on the outer peripheral surface of the spline shaft 12.
The spline shaft 12 has both end portions in the axial direction, more specifically, between the bearing mounts 5 and 6 and both end edges in the axial direction of the spline shaft 12, and the timing pulley 16 is provided on the bearing mount 5 side. The timing pulleys 17 are arranged so as to fit the spline shafts 12 respectively. Boss corresponding to the spline 15 is formed in the timing pulleys 16 and 17, and the timing pulleys 16 and 17 can be rotated along with the rotation of the spline shaft 12 by meshing each boss with the spline 15. In addition, it is movable along the spline 15 in the axis (left-right) direction of the spline shaft 12.

The length of the spline 15 formed on the spline shaft 12 may be a required length according to the amount by which the interval between the bearing mounts 5 and 6 is changed. That is, as shown in this embodiment, the spline 15 may be formed over almost the entire length of the spline shaft 12, or the spline 15 may be formed on a part of the spline shaft 12.
In this embodiment, the timing pulleys 16 and 17 are rotated together with the spline shaft 12 by the spline 15 and moved in the axial direction of the spline shaft 12. A grooved shaft in which a key groove having the above function is formed may be used. Moreover, you may use the axis | shaft in which the axial cross section in the range of the predetermined length in the axial direction was formed in the non-circular fitting axial part.

A lower end portion of the bearing mount 5 is exposed below the vibration frame 4, and a driving motor 18 as a driving source is fixed to the exposed portion, and a timing axis is provided on a rotating shaft of the driving motor 18. A pulley 19 is fitted.
In the bearing mount 5, the timing belt 20 is wound around the timing pulleys 19, 13 a, 13 b and 16. Specifically, as shown in FIG. 2, the timing belt 20 is in contact with the lower half of the timing pulleys 16 and 19 and the upper half of the timing pulleys 13a and 13b so as to be substantially V-shaped when viewed from the right side. , Has been around. Here, the timing pulleys 13a, 13b, 16, 19 and the timing belt 20 function as a first transmission mechanism.

In the bearing mount 6, as shown in FIG. 1, a timing pulley 21 is rotatably supported by the bearing mount 6 below the timing pulley 17 that is externally fitted to the spline shaft 12.
In the bearing mount 6, the timing belt 22 is wound around the timing pulleys 21, 14 a, 14 b and 17. Specifically, as shown in FIG. 3, the timing belt 22 is in contact with the lower half of the timing pulleys 17 and 21 and the upper half of the timing pulleys 14 a and 14 b so as to be substantially V-shaped in the left side view. , Has been around. Here, the timing pulleys 14a, 14b, 17, 21 and the timing belt 22 function as a second transmission mechanism.

  Thereby, as shown in FIG. 1, the driving force of the drive motor 18 is transmitted to the timing pulleys 13a, 13b and 16 via the timing pulley 19 and the timing belt 20 in the bearing mount 5, and the timing pulley 13a, 13b is rotated at an equal speed. The driving force of the driving motor 18 is transmitted to the timing pulleys 14a, 14b and 21 via the spline shaft 12, the timing pulley 17 and the timing belt 22, and the timing pulleys 14a and 14b are rotated at a constant speed.

  In the bed 2, mounting pillars 23a and 23b are erected in the vicinity of the bar springs 3b and 3d, respectively. Pickups 24a and 24b serving as detection means are attached to these mounting columns 23a and 23b, respectively. The pickups 24a and 24b detect the vibration of the vibration frame 4 with respect to the bed 2, and as shown in FIGS. 2 and 3, the vibration detection units 34a and 34b vibrate corresponding to the pickups 24a and 24b. The detection projections 25a and 25b projecting downward from the frame 4 are in contact with each other. The detection outputs of the pickups 24a and 24b are given to a vibration detection circuit (not shown).

  As shown in FIG. 1, the vibration frame 4 is further provided with a feed screw shaft 26 as a longitudinal member. Both sides of the feed screw shaft 26 are rotatably supported by bearing projections 27 and 28 projecting upward from the vibration frame 4. A moving motor 29 for rotating the feed screw shaft 26 is connected to the left end portion of the feed screw shaft 26. The movement motor 29 and the feed screw shaft 26 function as movement guide means. In this embodiment, the feed screw shaft 26 is provided on the upper side of the vibration frame 4, but may be provided on the lower side of the vibration frame 4. The moving motor 29 may be a normal electric motor, or may be a pneumatic motor or a hydraulic motor instead.

  The feed screw shaft 26 is provided with a left-hand thread forming portion 30 with a left-hand thread on the right side and a right-thread forming portion 31 with a right-hand thread on the left side. The left screw forming portion 30 is inserted through a screw bearing 32 provided on the bearing mount 5, and the right screw forming portion 31 is inserted through a screw bearing 33 provided on the bearing mount 6. Therefore, by rotating the feed screw shaft 26 in a certain direction by the moving motor 29, the bearing mount 5 is guided to the left screw forming portion 30, and the bearing mount 6 is guided to the right screw forming portion 31 to vibrate. The frame 4 is moved in a direction approaching each other. Further, by rotating the feed screw shaft 26 in the opposite direction by the moving motor 29, the two bearing mounts 5 and 6 are moved away from each other on the vibration frame 4.

  In this embodiment, the feed screw shaft 26 is rotated by a moving motor 29. However, instead of the moving motor 29, a handle is attached to one end of the feed screw shaft 26, and the feed screw shaft 26 is manually rotated. You may make it make it. Further, the feed screw shaft 26 may be rotated by a rotating machine using pneumatic pressure and hydraulic pressure. Furthermore, instead of the feed screw shaft, a configuration in which the bearing mount is moved using a longitudinal member that is slid by an air cylinder may be used.

  Further, in this embodiment, since both the bearing mounts 5 and 6 are movable with respect to the bed 2, the feed screw shaft 26 has the left screw forming portion 30 and the right screw forming portion 31, When only one of the bearing mounts 5 and 6 is movable with respect to the bed 2 and the other is fixed with respect to the bed 2, the feed screw shaft 26 is moved relative to the movable bearing mount. The shaft may be a right-handed screw or a left-handed screw.

  Since this dynamic balance testing machine 1 is configured as described above, the bearing mounts 5 and 6 can be easily adjusted to a desired interval by driving the moving motor 29. After the bearing mounts 5 and 6 are set at a desired interval, the DUT 11 is placed on the rollers 7a and 7b and the rollers 8a and 8b of the bearing mount 5 and rotated, and the vibration frame 4 with respect to the bed 2 at this time is rotated. When the pickups 24a and 24b detect the vibration, a dynamic balance test of the DUT 11 is performed.

In this dynamic balance testing machine 1, since the bearing mounts 5 and 6 are erected on the same vibration frame 4, in the vibration of the vibration frame 4 relative to the bed 2 detected by the pickups 24a and 24b, the vibration frame The influence caused by individual differences can be eliminated.
The bearing mounts 5 and 6 are connected by a feed screw shaft 26. When the feed screw shaft 26 is rotated in a certain direction by a moving motor 29, the bearing mounts 5 and 6 and the feed screw shaft 26 are connected. , And the movable frame 4 is movable in a direction toward or away from the vibration frame 4. Therefore, according to the length of the DUT 11, the distance in the left-right direction between the bearing mounts 5 and 6, that is, the distance between the rollers 7a and 8a and the distance between the rollers 7b and 8b can be adjusted.

  The bearing mount 5 is provided with a driving motor 18, and the driving force of the driving motor 18 is supplied to the rollers 7 a and 7 b via the first transmission mechanism, that is, the timing pulleys 13 a, 13 b, 16, 19 and the timing belt 20. And to the rollers 8a and 8b of the bearing mount 6 via the spline shaft 12 and the second transmission mechanism, that is, the timing pulleys 14a, 14b, 17, 21 and the timing belt 22. A spline 14 is formed on the spline shaft 12, and the first transmission mechanism and the second transmission mechanism are movable along with the bearing mounts 5 and 6 along the spline 14. Therefore, even if the distance between the first transmission mechanism and the second transmission mechanism is changed as the distance between the bearing mounts 5 and 6 is changed, the coupling relation between the first transmission mechanism and the second transmission mechanism and the spline shaft 12 is changed. Also move without hindrance. Therefore, the movement of the first transmission mechanism and the second transmission mechanism does not affect the accuracy of unbalance measurement. In the dynamic balance testing machine 1, no components are arranged between the rollers 7 a and 7 b of the bearing mount 5 and the rollers 8 a and 8 b of the bearing mount 6. Therefore, when it is necessary to measure the unbalance of the DUT 11 having the rollers 7a and 7b and the protruding portions 35 (see FIG. 1) protruding in the radial direction of the rollers 8a and 8b, the protruding portions The device under test 11 can be supported without interfering 35 with the components of the dynamic balance testing machine 1, and such unbalance of the device under test 11 can be measured.

As a result, the dynamic balance testing machine 1 can change the roller interval with a simple configuration, and can accurately measure the unbalance of various types of test objects.
In addition, since the drive motor 18 is fixed to the bearing mount 5, the distance between the drive motor 18 and the rollers 7a and 7b can be relatively shortened, whereby the first transmission mechanism can be simply configured. Can do. Further, since the drive motor 18 can move together with the bearing mount 5 in the axis (left and right) direction of the spline shaft 12, the disposition position of the drive motor 18 can be determined with respect to the unbalance measurement accuracy when the bearing mount 5 is moved. The resulting error can be reduced.

As a result, unbalance can be accurately measured with a simple configuration.
In the first transmission mechanism, a total of four timing pulleys including timing pulleys 13a and 13b corresponding to the rollers 7a and 7b, a timing pulley 16 corresponding to the spline shaft 12, and a timing pulley 19 corresponding to the driving motor 18 are provided. Are connected by a single timing belt 20. Therefore, the spline shaft 12 and the rollers 7a and 7b can be simultaneously rotated by transmitting the driving force of the driving motor 18 with the minimum necessary timing pulley and timing belt, that is, with a simple configuration.

As a result, unbalance can be accurately measured with a simple configuration.
In the above embodiment, the two bearing mounts 5 and 6 are provided on the vibration frame 4, but the number of the bearing mounts may be three or more. In particular, when the DUT 11 is long or heavy in the axial direction, three or more bearing mounts may be provided. Even in that case, the roller of each bearing mount can be rotated based on the configuration of the present invention. Further, the bearing mounts movable with respect to the vibration frame 4 do not have to be all bearing mounts, and may be any arbitrary one of the three or more bearing mounts as necessary. When making an arbitrary bearing mount movable, the feed screw shaft 26 and the moving motor 29 for moving the bearing mount may be one set, or two or more sets of the feed screw shaft 26 and the moving motor may be used. 29 may be required. In any case, it may be configured based on the idea of the present invention.

  Further, the present invention is not limited to the above-described embodiment, and various modifications can be made within the scope of the claims, and even a so-called soft type dynamic balance testing machine can be used as a so-called hard type dynamic balance. I would like to mention that the test machine can be applied together.

It is a front view of the dynamic balance testing machine concerning one embodiment of this invention. It is an AA arrow line view of FIG. It is a BB arrow line view of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Dynamic balance testing machine 2 Bed 3a-3d Bar spring 4 Vibration frame 5, 6 Bearing mount 7a, 7b Roller 8a, 8b Roller 12 Spline shaft 13a, 13b Timing pulley 14a, 14b Timing pulley 15 Spline 16, 17 Timing pulley 18 Drive Motor 19 Timing pulley 20 Timing belt 21 Timing pulley 22 Timing belt 24a, 24b Pickup 26 Feed screw shaft 29 Motor for movement

Claims (4)

A vibration frame held on the bed by an elastic body so as to vibrate;
Detection means for detecting vibration of the vibration frame;
Two or more bearing stands each provided with a pair of rollers that are erected on the vibration frame and support and rotate the device under test;
A common rotating shaft pivotally supported by the plurality of bearing mounts,
The vibration frame is provided with movement guide means, and at least one of the plurality of bearing mounts is guided by the movement guide means to be movable on the vibration frame,
One of the plurality of bearing stands includes a drive source, a first transmission mechanism for transmitting the driving force of the drive source to the roller and the rotating shaft provided in the bearing stand. And is provided,
Among the plurality of bearing stands, the bearing stands other than the bearing stand provided with the drive source and the first transmission mechanism are configured to transmit the rotation of the rotary shaft to the rollers provided in the bearing stands. A second transmission mechanism is provided;
A spline or a keyway is formed on the rotary shaft, and at least one of the first transmission mechanism and the second transmission mechanism is in the axial direction of the rotary shaft along the spline or keyway. A dynamic balance testing machine characterized in that it is movable. In the dynamic balance testing machine according to claim 1,
The drive source is fixed to the bearing stand, and is guided by the movement guide means so as to be movable in the axial direction of the rotary shaft along with the bearing stand on the vibration frame. Balance testing machine. The dynamic balance testing machine according to claim 1 or 2,
The first transmission mechanism includes at least four timing pulleys and one timing belt, and the rotary shaft and the roller are driven to rotate simultaneously by the driving force of the driving source. . In the dynamic balance testing machine according to any one of claims 1 to 3,
The movement guide means includes a longitudinal member that is provided on the vibration frame and is connected to the plurality of bearing mounts for adjusting the distance between the bearing mounts.
The longitudinal member is screw-coupled to at least one of the plurality of bearing mounts, and by rotating the longitudinal member, the coupling position of the longitudinal member and at least one bearing mount screw-coupled changes, Thereby, a dynamic balance testing machine characterized in that at least one bearing stand can be moved.

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