Dynamic balancing test machine

Abstract

A dynamic balancing tester according to an embodiment of the present invention includes: a vibration unit, which holds a rotating body as a test body in a manner that the rotating body is rotatable; a first spring, which elastically supports the vibration unit and limits the displacement of the vibration unit in a direction parallel to the rotation axis of the rotating body; and at least three second springs, which elastically support the vibration unit and limit the displacement of the vibration unit in a specified direction orthogonal to the rotation axis, at least three second springs are mounted on the vibration unit on the same specified plane, and the vibration unit holds the rotating body in a manner that the projection of the center of gravity of the rotating body on the specified plane is at a position approximately the same as the position where the first spring is mounted on the vibration unit.

Description

[0001] This application is a divisional application of the application with patent application number CN201680088288.X and original application date August 10, 2016 and invention name “Dynamic Balancing Testing Machine”. Technical Field

[0002] The invention relates to a dynamic balancing testing machine. Background Art

[0003] There is known a dynamic balancing tester that holds a rotating body as a test body in a rotatable manner on a vibration table, which is supported on a frame in a vibratory manner, so that the rotating body is rotated and the vibration generated on the vibration table due to the dynamic imbalance of the rotating body is measured, thereby measuring the dynamic balance state of the test body.

[0004] The dynamic balancing tester described in Japanese Patent Gazette No. 5426991 (hereinafter referred to as "Patent Document 1") adopts the following structure: a roughly rectangular flat plate-shaped base of a vibration table is mounted on a longitudinal spring at approximately the center of the width direction of its upper end so as to be suspended, and horizontal springs are mounted and supported near the four corners of the roughly rectangular shape, thereby connecting the table in a vibratory manner.

[0005] The dynamic balancing tester described in Japanese Patent No. 5622171 (hereinafter referred to as "Patent Document 2") adopts a structure in which a test object is held by an air bearing.

[0006] The dynamic balancing tester described in Japanese Utility Model Publication No. 5-17636 (hereinafter referred to as "Patent Document 3") has a nozzle for blowing compressed air for rotationally driving a rotating body, and a structure capable of adjusting the height and direction of the air blown by the nozzle to the rotating body. Summary of the invention

[0007] In a dynamic balancing tester, the greater the difference between the displacement of the upper surface side (lower surface side) of the base caused by the prescribed unbalance amount of the upper surface side (lower surface side) of the rotating body and the displacement of the upper surface side (lower surface side) of the base caused by the prescribed unbalance amount of the lower surface side (upper surface side) of the rotating body, the higher the measurement sensitivity. However, in the structure described in Patent Document 1, the position where the longitudinal spring is mounted on the base has a large offset compared to the point where the center of gravity of the rotating body is projected onto the base, so the displacement of the upper surface side (lower surface side) of the base increases not only the unbalance degree of the upper surface side (lower surface side) of the rotating body, but also the unbalance degree of the lower surface side (upper surface side) of the rotating body. As a result, the difference between the displacement of the upper surface side (lower surface side) of the base caused by the specified imbalance amount on the upper surface side (lower surface side) of the rotating body and the displacement of the upper surface side (lower surface side) of the base caused by the specified imbalance amount on the lower surface side (upper surface side) of the rotating body becomes smaller, which is one of the reasons for the decrease in the measurement sensitivity of the dynamic balancing tester.

[0008] As described below, according to one embodiment of the present invention, a dynamic balancing tester having high measurement sensitivity is provided.

[0009] A dynamic balancing tester according to one embodiment of the present invention comprises: a vibration unit, which holds a rotating body as a test body in a manner that the rotating body is rotatable; a first spring, which elastically supports the vibration unit and limits the displacement of the vibration unit in a direction parallel to the rotation axis of the rotating body; and at least three second springs, which elastically support the vibration unit and limit the displacement of the vibration unit in a specified direction orthogonal to the rotation axis, at least three second springs are mounted on the vibration unit on the same specified plane, and the vibration unit holds the rotating body in a manner that the projection of the center of gravity of the rotating body on the specified plane is at a position substantially the same as the position where the first spring is mounted on the vibration unit.

[0010] According to this structure, the rotating body is held in such a manner that the projection of the center of gravity of the rotating body onto the specified plane on which at least three second springs are installed on the vibration unit is approximately at the same position as the position at which the first spring is installed on the vibration unit. As a result, the displacement of the lower side (upper side) of the vibration unit caused by the imbalance of the upper surface side (lower surface side) of the rotating body can be reduced, and further, the difference between the displacement of the upper surface side (lower surface side) of the vibration unit caused by the specified imbalance amount on the upper surface side (lower surface side) of the rotating body and the displacement of the upper surface side (lower surface side) of the vibration unit caused by the specified imbalance on the lower surface side of the rotating body can be increased. Therefore, the measurement sensitivity is improved, and the measurement accuracy can be improved.

[0011] Furthermore, the dynamic balancing tester according to one embodiment of the present invention may have a structure in which the first springs are attached to the vibration unit at positions substantially equidistant from respective positions at which at least three second springs are attached to the vibration unit.

[0012] Furthermore, in one embodiment of the present invention, a structure may be adopted in which positions where at least three second springs are mounted on the vibration unit are arranged symmetrically with respect to a plane passing through the rotation axis and positions where the first springs are mounted on the vibration unit.

[0013] Furthermore, the dynamic balancing tester according to one embodiment of the present invention may have four second springs arranged in a substantially rectangular shape on a predetermined plane with the positions where the second springs are attached to the vibration unit as vertices.

[0014] Furthermore, in one embodiment of the present invention, a structure in which a relief structure for allowing the first spring to pass is formed in the vibration unit may be adopted.

[0015] In addition, in one embodiment of the present invention, the avoidance structure may be a hole, a groove or a notch.

[0016] In one embodiment of the present invention, the vibration unit may have a base having a mounting portion for mounting a first spring and at least three second springs, and a bearing unit fixed to the base to hold the rotating body in a rotatable manner.

[0017] Furthermore, in one embodiment of the present invention, a structure may be adopted in which the vibration unit has a shape that is substantially symmetrical with respect to a plane containing a position for mounting the first spring and the rotation axis.

[0018] In one embodiment of the present invention, the base may be a substantially rectangular plate having sides parallel to the rotation axis, and the second spring may be mounted near each of the four vertices of the base.

[0019] Furthermore, in one embodiment of the present invention, a structure may be adopted in which the bearing unit is fixed to the vicinity of one end portion of the base in the rotation axis direction.

[0020] Furthermore, in one embodiment of the present invention, a structure may be adopted in which the vibration unit has an opening penetrating in a direction perpendicular to the predetermined plane.

[0021] In the dynamic balancing test machine of the structure described in Patent Document 2 that utilizes an air bearing to hold the object to be tested, the bearing portion that generates friction with the object to be tested is not structured to be easily replaceable. Therefore, not only does it require a lot of man-hours and costs when the bearing portion needs to be replaced, but the measurement operation itself is stopped when the replacement takes time, which is one of the reasons for the increase in operating costs and the decrease in productivity.

[0022] As described below, according to one embodiment of the present invention, a dynamic balancing tester capable of reducing running costs and improving productivity is provided.

[0023] A dynamic balancing tester according to one embodiment of the present invention has a bearing unit, which forms an air bearing that holds a rotating body serving as a test body in a rotatable manner. The bearing unit has: a bearing housing; and a thrust bearing component that is detachably fixed to the bearing housing. The thrust bearing component is a plate-like component having an opening for a shaft to pass through, and a thrust air bearing is formed between the thrust bearing component and the rotating body.

[0024] According to this structure, the thrust bearing component that is easy to wear is made into a replaceable component, and both sides of the component can be used as a thrust bearing, thereby reducing the man-hours for replacing the component, the component cost and the time of stopping the measurement work due to the component replacement, reducing the operating cost and improving productivity.

[0025] Furthermore, in one embodiment of the present invention, a structure in which the thrust bearing member is formed in a flat plate shape may be adopted.

[0026] Furthermore, in one embodiment of the present invention, a bearing unit may have a structure in which the bearing unit includes a positioning and fixing member that positions the thrust bearing member and is detachably fixed to the bearing housing.

[0027] Furthermore, in one embodiment of the present invention, the following structure may be adopted, wherein the positioning and fixing component includes: a positioning component that positions the thrust bearing component; and a fixing component that detachably fixes the positioning component to the bearing housing.

[0028] In one embodiment of the present invention, the bearing unit may include a radial bearing member that is detachably held in a bearing housing, and a radial air bearing is formed between the radial bearing member and the rotating body.

[0029] Furthermore, in one embodiment of the present invention, a structure in which a positioning and fixing component is used to fix the radial bearing component and the thrust bearing component to the bearing housing together.

[0030] Furthermore, in one embodiment of the present invention, a structure in which the opening of the thrust bearing component is circular may be adopted.

[0031] Furthermore, in one embodiment of the present invention, a structure in which the thrust bearing member is a substantially disk-shaped member may be employed.

[0032] Furthermore, in one embodiment of the present invention, a structure may be adopted in which the positioning and fixing member is positioned so that the center of the circular opening of the thrust bearing member is located on the axis of the radial bearing member.

[0033] In addition, in one embodiment of the present invention, the following structure can be adopted, wherein the radial bearing component has a cylindrical protrusion on the end face used to configure the thrust bearing component, which has a diameter substantially the same as the outer diameter of the thrust bearing component and is coaxial with the axis of the radial bearing component, and the positioning and fixing component has a cylindrical hollow portion, which has a diameter substantially the same as the outer diameter of the thrust bearing component and the protrusion, and is formed to have a depth substantially the same as a dimension obtained by adding the thickness of the thrust bearing component to the height of the protrusion.

[0034] In a dynamic balancing test machine having a structure described in Patent Document 3 and having a nozzle for blowing compressed air for driving a rotating body to rotate, it is possible to rotationally drive test bodies of various sizes and shapes, and when the nozzle interferes with the assembly or disassembly of the test body, the nozzle can be moved to a position where it does not interfere. However, it is time-consuming and laborious to move the nozzle each time the test body is assembled or disassembled, and it is very difficult to return the nozzle to the same position each time, which is one of the reasons for the reduction in working efficiency and measurement accuracy.

[0035] As described below, according to one embodiment of the present invention, a dynamic balancing tester capable of improving workability and measurement accuracy is provided.

[0036] A dynamic balancing testing machine of one embodiment of the present invention includes: a driving unit that blows air to a rotating body that is rotatably supported to drive the rotating body; a moving unit that moves the driving unit in the direction of the rotation axis of the rotating body between a driving position capable of driving the rotating body and a standby position for easy disassembly and assembly of the rotating body; and a changing unit that changes the driving position in the direction of the rotation axis.

[0037] According to this structure, a mechanism for moving the drive unit to a position that does not hinder the assembly and disassembly of the test object and a mechanism for changing the position of the drive unit according to the shape and size of the test object are provided as separate mechanisms. As a result, the assembly and disassembly of the test object can be easily performed, and the trouble of adjusting the position of the drive unit each time the test object is assembled and disassembled is eliminated. The position shift of the drive unit can be prevented, and the operability and measurement accuracy can be improved.

[0038] In one embodiment of the present invention, a structure may be adopted in which the moving unit supports the driving unit, and the changing unit changes the position of the driving unit in the rotation axis direction by moving the moving unit in the rotation axis direction.

[0039] In one embodiment of the present invention, a configuration may be adopted in which the changing unit supports the driving unit, and the moving unit changes the position of the driving unit in the rotation axis direction by moving the changing unit in the rotation axis direction.

[0040] Furthermore, the dynamic balancing tester according to one embodiment of the present invention may have a structure including a guide that restricts movement of the driving unit in the direction of the rotation axis.

[0041] Furthermore, the dynamic balancing tester according to one embodiment of the present invention may have a structure including a support member that supports the driving unit, and a guide that guides movement of the support member in the direction of the rotation axis.

[0042] In one embodiment of the present invention, a configuration may be adopted in which the changing unit supports the supporting member, and the moving unit changes the position of the driving unit via the supporting member by moving the changing unit in the rotation axis direction.

[0043] In one embodiment of the present invention, a structure may be adopted in which the moving unit supports the supporting member, and the changing unit changes the position of the driving unit via the supporting member by moving the moving unit in the rotation axis direction.

[0044] Furthermore, in one embodiment of the present invention, a structure in which the moving unit is driven by fluid pressure may be adopted.

[0045] Furthermore, in one embodiment of the present invention, a structure may be adopted in which the driving unit has a nozzle for blowing air toward the rotating body.

[0046] Furthermore, in one embodiment of the present invention, the following structure may be adopted, wherein the nozzle includes: at least one forward jet nozzle for rotating the rotating body in a forward direction; and at least one reverse jet nozzle for rotating the rotating body in a direction opposite to the forward direction.

[0047] In one embodiment of the present invention, the driving unit may include a hollow portion surrounding the outer periphery of the rotating body and penetrating in the direction of the rotating axis, and a nozzle may be formed on the inner periphery of the hollow portion. BRIEF DESCRIPTION OF THE DRAWINGS

[0048] Figure 1 It is a front view of the main part of the dynamic balancing tester according to the embodiment of the present invention.

[0049] Figure 2 It is a right side view of the main part of the dynamic balancing tester according to the embodiment of the present invention.

[0050] Figure 3 It is a plan view of the main part of the dynamic balancing tester according to the embodiment of the present invention.

[0051] Figure 4 It is an exploded view of a vibration unit of a dynamic balancing machine according to an embodiment of the present invention.

[0052] Figure 5 It is a diagram for explaining the vibration displacement generated when the vibration unit of the comparative example is subjected to a dynamic balance test.

[0053] Figure 6 It is a diagram for explaining vibration displacement generated when the vibration unit according to the embodiment of the present invention is subjected to a dynamic balance test.

[0054] Figure 7 It is a plan view of a bearing housing of a dynamic balancing tester according to an embodiment of the present invention.

[0055] Figure 8 It is a cross-sectional view of a bearing unit of a dynamic balancing machine according to an embodiment of the present invention.

[0056] Fig. 9 It is a front view of the driving unit, the guiding unit, the changing unit, and the moving unit of the dynamic balancing tester according to the embodiment of the present invention.

[0057] Fig.10 It is a right side view of the driving unit, the guiding unit, the changing unit, and the moving unit of the dynamic balancing tester according to the embodiment of the present invention.

[0058] Fig.11 It is a plan view of a driving unit, a guiding unit, a changing unit, and a moving unit of a dynamic balancing tester according to an embodiment of the present invention. DETAILED DESCRIPTION

[0059] Hereinafter, embodiments of the present invention will be described with reference to the drawings.

[0060] Figure 1 , Figure 2 and Figure 3 The following are the front view, right side view and plan view of the main parts of the dynamic balancing tester 1. Figure 1 The left and right direction is set as the X-axis direction, the direction perpendicular to the paper is set as the Y-axis direction, and the up and down direction is set as the Z-axis direction. In addition, the Z-axis direction is the vertical direction, and the X and Y-axis directions are the horizontal directions. Figure 1 The front side (the side on the surface of the paper) is referred to as the front, and the depth side (the side on the back of the paper) is referred to as the back.

[0061] The dynamic balancing tester 1 of this embodiment is suitable for dynamic balancing test of a rotating body (test body W) having blades such as a turbine rotor of a supercharger. The dynamic balancing tester 1 is configured as follows: the test body W can be driven to rotate by blowing air to the blades of the test body W, the vibration generated at this time can be measured, and the dynamic balance of the test body W can be measured based on the measurement result of the vibration.

[0062] The dynamic balancing tester 1 includes: a vibration unit 200 that holds the test object W in a rotatable manner with its rotation axis facing the Z-axis direction; a drive unit 300 that drives the test object W to rotate by blowing air to the blades of the test object W held by the vibration unit 200; and a stand 100 that supports the vibration unit 200 and the drive unit 300. In addition, the dynamic balancing tester 1 also includes a guide unit 400, a change unit 500, and a moving unit 600 described later. In addition, in Figure 1-3 In the figure, the driving unit 300, the guiding unit 400, the changing unit 500 and the moving unit 600 are omitted.

[0063] like Figure 1-3 As shown, the vibration unit 200 is supported on the stand 100 by a longitudinal spring (first spring) 110 extending in the Z-axis direction and four transverse springs (second springs) 120 extending in the Y-axis direction. The longitudinal spring 110 and the transverse spring 120 are substantially rigid bodies in the longitudinal direction, and are round rod-shaped components that only allow substantial bending deformation. The longitudinal spring 110 supports the vibration unit 200 by suspending it from above, and the transverse spring 120 supports the vibration unit 200 from the rear side. With respect to the vibration unit 200, the displacement in the Z-axis direction is limited by the longitudinal spring 110, and the displacement in the Y-axis direction is limited by the transverse spring 120, so that it is substantially allowed to perform only translational motion (vibration) in the X-direction and rotational motion (vibration) around the Y-axis.

[0064] The stand 100 has: two vibration sensor units 130, which measure the vibration of the vibration unit 200 in the X-axis direction; and a phase sensor unit 140, which detects the rotation phase of the test object W. The front end of the measuring element 132 of one vibration sensor unit 130 is connected to the vicinity of the upper end of the back side of the vibration unit 200, and measures the vibration displacement on the upper surface side of the vibration unit 200. In addition, the front end of the measuring element 132 of the other vibration sensor unit 130 is connected to the vicinity of the lower end of the back side of the vibration unit 200, and measures the vibration displacement on the lower surface side of the vibration unit 200. In addition, the phase sensor unit 140 is a device that detects the rotation phase of the test object W in an optical non-contact manner. The phase sensor unit 140 is installed on the upper part of the stand 100, and detects the rotation phase of the test object W from directly above.

[0065] Figure 4 2 is an exploded view of the vibration unit 200. The vibration unit 200 includes a base 210 and a bearing unit 220 detachably fixed to the front surface of the base 210 by bolts. The bearing unit 220 forms an air bearing and holds the test object W in a rotatable manner.

[0066] The base 210 is a substantially rectangular metal plate having sides parallel to the X-axis and the Z-axis. A circular opening 214 is formed on the upper portion of the base 210 and passes through in the Y direction. By providing the opening 214, the vibration unit 200 is lightened, and thus the measurement sensitivity is improved.

[0067] A substantially rectangular longitudinal spring mounting opening 211 penetrating in the Y direction is formed substantially in the center of the base 210. In addition, the base 210 has a longitudinal spring mounting member 219 for mounting the longitudinal spring 110 on the base 210. The longitudinal spring mounting member 219 is inserted into the longitudinal spring mounting opening 211 and is detachably fixed to the main body of the base 210 by bolts.

[0068] In addition, in the base 210, two escape holes 212a and 212b extending in the Z-axis direction are formed on a straight line passing through the center of the opening 214. The upper escape hole 212a penetrates from the upper surface of the base 210 to the opening 214, and the lower escape hole 212b penetrates from the lower end of the opening 214 to the longitudinal spring mounting opening 211. The longitudinal spring 110 passes through the escape hole 212a, the opening 214, and the escape hole 212b. The front end of the longitudinal spring 110 is inserted into the longitudinal spring mounting portion 219a of the longitudinal spring mounting component 219, and the longitudinal spring mounting component 219 is inserted into the longitudinal spring mounting opening 211. The escape holes 212a and 212b are formed with an inner diameter that is sufficiently larger than the outer diameter of the longitudinal spring 110 so as not to contact the longitudinal spring 110.

[0069] In addition, transverse spring mounting portions 213 for mounting the front end of the transverse spring 120 are provided at the four corners of the substantially rectangular base 210. The longitudinal spring mounting opening 211 is formed so that the center position C of the arrangement of the four transverse spring mounting portions 213 (i.e., the position at the same distance from each transverse spring mounting portion 213) is located substantially at the center of the longitudinal spring mounting opening 211. Therefore, in the present embodiment, the position (longitudinal spring mounting position P) at which the longitudinal spring 110 is mounted on the base 210 by the longitudinal spring mounting member 219 coincides with the center position C.

[0070] A key 217 extending in the Z-axis direction for positioning the bearing unit 220 is provided on the front surface of the lower portion of the base 210 on which the bearing unit 220 is mounted. In addition, air supply holes 215 and 216 through which compressed air supplied to the bearing unit 220 flows are passed through the lower portion of the base 210 in the Y-axis direction.

[0071] The vibration unit 200 of the present embodiment is configured so that the projection of the center of gravity of the test object W held by the bearing unit 220 on the base 210 overlaps with the longitudinal spring mounting position P. In other words, the vibration unit 200 is configured so that the center of gravity of the test object W is arranged on or near a straight line extending from the longitudinal spring mounting position P in the Y-axis direction.

[0072] In a dynamic balancing tester, the greater the difference between the displacement of the upper surface side (lower surface side) of the vibration unit caused by the specified unbalance amount on the upper surface side (lower surface side) of the test body and the displacement of the upper surface side (lower surface side) of the vibration unit caused by the specified unbalance amount on the lower surface side (upper surface side) of the test body, the higher the measurement sensitivity. Figure 5 and Figure 6 As described above, the vibration unit 200 of the present embodiment has a larger difference than the conventional structure described in Patent Document 1, and thus has a higher measurement sensitivity than the conventional structure.

[0073] Figure 5 2 is a diagram illustrating the vibration displacement occurring during a dynamic balance test in a vibration unit 200' as a comparative example. Figure 6 2 is a diagram for explaining the vibration displacement generated during the dynamic balance test in the vibration unit 200 of the present embodiment. Figure 5 In FIG. 1 , the same reference numerals as those in the present embodiment are used to denote the components corresponding to the vibration unit 200 of the present embodiment. The vibration unit 200 ′ of the comparative example is different from the vibration unit 200 of the present embodiment in that the vertical spring mounting position P′ is located at the center of the upper end of the base.

[0074] exist Figure 5 and Figure 6 In the figure, O represents the longitudinal spring fixing position where the longitudinal spring 110 is fixed to the stand 100, G represents the center of gravity of the test object W, Mo represents the weight installed on the test object W to apply the imbalance, F represents the centrifugal force generated by the rotation of the weight Mo installed on the test object W, Uu (U'u) represents the displacement in the X direction of the upper surface side of the vibration unit 200 (200') measured when the weight Mo is installed on the upper surface side of the test object W, and Ul (U'l) represents the displacement in the X direction of the upper surface side of the vibration unit 200 (200') measured when the weight Mo is installed on the upper surface side of the test object W. The displacement in the X direction of the upper surface side of the vibration unit 200 (200') is measured in the state of the lower surface side of the test object W, Lu (L'u) represents the displacement in the X direction of the lower surface side of the vibration unit 200 (200') measured in the state of the weight Mo installed on the upper surface side (lower surface side) of the test object W, and Ll (L'l) represents the displacement in the X direction of the lower surface side of the vibration unit 200 (200') measured in the state of the weight Mo installed on the lower surface side of the test object W. The displacements Uu (U'u) and Ul (U'l) are measured by the upper vibration sensor unit 130, and the displacements Lu (L'u) and Ll (L'l) are measured by the lower vibration sensor unit 130.

[0075] In addition, the displacement of the vibration unit 200 (200') is the sum of the displacement caused by the bending vibration of the longitudinal spring 110 around the Y axis with the longitudinal spring fixing position O as the fulcrum and the displacement caused by the bending vibration of the longitudinal spring 110 around the Y axis with the longitudinal spring installation position P (P') as the fulcrum. However, in order to explain the difference in the displacement of the vibration unit 200 (200') in the X direction caused by the difference in the longitudinal spring installation position P (P'), the displacements Uu, Ul, Lu, Ll (U'u, U'l, L'u, L'l) are explained as the displacements caused by the bending vibration of the longitudinal spring 110 around the Y axis with the longitudinal spring installation position P (P') as the fulcrum. In addition, the centrifugal force F changes direction according to the rotation phase of the test body W, but in the following description, the state where the centrifugal force acts in the positive direction of the X axis (right direction in the figure) is explained.

[0076] Figure 5 (a) and Figure 6 (a) is a diagram for explaining a case where a weight Mo is attached to the upper surface side of the test object W. Figure 5 (b) and Figure 6 (b) is a diagram for explaining a case where a weight Mo is attached to the lower surface side of the test object W. Figure 5 As shown in (a), in the case where a weight Mo is attached to the upper surface side of the vibration unit 200' of the comparative example, a moment is generated due to the centrifugal force F, which causes the vibration unit 200' to rotate counterclockwise in the figure with the longitudinal spring installation position P' as the axis. Therefore, both the displacement U'u and the displacement L'u are displacements in the positive direction of the X axis (right direction in the figure) (however, the magnitude of the displacement U'u is very small). In addition, Figure 5 As shown in (b), in the vibration unit 200' of the comparative example, when a weight Mo is attached to the lower surface side of the test body W, a moment that causes the vibration unit 200' to rotate counterclockwise in the figure with the longitudinal spring installation position P' as the axis is generated due to the centrifugal force F. Therefore, both the displacement U'l and the displacement L'l are displacements in the positive direction of the X-axis. That is, regardless of whether the weight Mo is attached to the upper surface side or the lower surface side of the test body W, the upper surface side and the lower surface side of the vibration unit 200' generate displacements in the same direction.

[0077] Therefore, in the vibration unit 200' of the comparative example, regardless of whether the weight Mo is attached to the upper surface side or the lower surface side of the test body W, the displacement in the positive direction of the X-axis (the right direction in the figure) generated by the centrifugal force F with the longitudinal spring fixed position O as the fulcrum is added to the displacements U'u, U'l, L'u, L'l in the positive direction of the X-axis, and the displacement of the vibration unit 200' in the positive direction of the X-axis (the right direction in the figure) becomes larger.

[0078] In contrast, Figure 6As shown in (a), in the vibration unit 200 of the present embodiment, when a weight Mo is attached to the upper surface side of the test body W, a torque is generated due to the centrifugal force F, which causes the vibration unit 200 to rotate clockwise in the figure with the longitudinal spring installation position P as the axis. Therefore, the displacement Uu is the same as the comparative example, which is the displacement in the positive direction of the X axis (the right direction in the figure), but the displacement Lu is different from the comparative example, which is the displacement in the negative direction of the X axis (the left direction in the figure). In addition, as Figure 6 As shown in (b), when a weight Mo is attached to the lower surface side of the test body W, a moment is generated to rotate the vibration unit 200 in the counterclockwise direction in the figure with the longitudinal spring installation position P as the axis. Therefore, the displacement L1 is the displacement in the positive direction of the X axis (the right direction in the figure) as in the comparative example, but the displacement U1 is the displacement in the negative direction of the X axis (the left direction in the figure) as in the comparative example.

[0079] Therefore, in the vibration unit 200 of the present embodiment, when the weight Mo is attached to the upper surface side of the test body W, the displacement of the upper surface side of the vibration unit 200 is the displacement in the positive direction of the X-axis (right direction in the figure) generated by the centrifugal force F with the longitudinal spring fixed position O as the fulcrum plus the displacement Uu in the positive direction of the X-axis, and the displacement becomes larger. The displacement of the lower surface side of the vibration unit 200 is the displacement in the positive direction of the X-axis (right direction in the figure) generated by the centrifugal force F with the longitudinal spring fixed position O as the fulcrum minus the displacement Lu in the negative direction of the X-axis (left direction in the figure), and the displacement becomes smaller. Similarly, when the weight Mo is added to the lower surface side of the test body W, the displacement of the lower surface side of the vibration unit 200 is the displacement in the positive direction of the X-axis (the right direction in the figure) generated by the centrifugal force F with the longitudinal spring fixed position O as the fulcrum plus the displacement Ll in the positive direction of the X-axis, and the displacement becomes larger. The displacement of the upper surface side of the vibration unit 200 is the displacement in the positive direction of the X-axis (the right direction in the figure) generated by the centrifugal force F with the longitudinal spring fixed position O as the fulcrum minus the displacement Ul in the negative direction of the X-axis (the left direction in the figure), and the displacement becomes smaller.

[0080] As can be seen from the above, the vibration unit 200 of the present embodiment has a larger difference between the displacement of the upper surface side (lower surface side) of the vibration unit 200 corresponding to the prescribed unbalance amount of the upper surface side (lower surface side) of the test object W and the displacement of the upper surface side (lower surface side) of the vibration unit 200 corresponding to the prescribed unbalance amount of the lower surface side (upper surface side) of the test object W. As described above, the larger the difference, the higher the sensitivity of the dynamic balancing tester, and therefore, the sensitivity of the vibration unit 200 of the present embodiment can be made higher than that of the vibration unit 200' of the comparative example.

[0081] In addition, in the vibration unit 200 of the present embodiment, the center position C of the four lateral spring mounting portions 213 coincides with the longitudinal spring mounting position P. Therefore, when the weight Mo is attached to the upper surface side of the test object W, the vibration unit 200 is Figure 5-6 The clockwise rotation angle in the figure is substantially equal to the counterclockwise rotation angle in the figure of the vibration unit 200 when the weight Mo is attached to the lower surface side of the test object W. Therefore, the measurement sensitivity of the imbalance on the upper surface side of the test object W and the measurement sensitivity of the imbalance on the lower surface side of the test object W can be made equal, and the imbalance can be measured with high precision regardless of whether the imbalance is on the upper surface side or on the lower surface side.

[0082] In addition, the shape of the base 210 and the arrangement of the longitudinal spring 110 and the transverse spring 120 are not limited to the contents of this embodiment. The plane on which the four transverse spring mounting parts 213 are arranged is parallel to the rotation axis of the test object W. In addition, the positional relationship between the center position C of the arrangement of the four transverse spring mounting parts 213, the longitudinal spring mounting position P, and the center of gravity of the test object W is the relationship described above (that is, the center position C, the longitudinal spring mounting position P, and the center of gravity of the test object W are arranged in the Y-axis direction, and the center position C is consistent with the longitudinal spring mounting position P). In addition, the base 210 and the bearing unit 220 can also be formed integrally as one component. In addition, the number of transverse springs 120 can be three or more that can stably support the base 210.

[0083] Figure 7 and Figure 8 They are respectively a top view of the bearing housing 221 and a cross-sectional view of the bearing unit 220. Figure 4 and Figure 8 As shown, the bearing unit 220 includes a bearing housing 221, a radial bearing component 222, a thrust bearing component 223, a positioning component 224, a fixing component 225, and a sealing component 226. The radial bearing component 222, the thrust bearing component 223, and the sealing component 226 are replaceable components that are suitable for the outer diameter of the journal of the test object W.

[0084] The radial bearing member 222 is accommodated in the bearing housing 221, and the thrust bearing member 223 is placed on the upper surface of the radial bearing member 222. The positioning member 224 is a member for positioning the thrust bearing member 223 with respect to the radial bearing member 222. The fixing member 225 is a member for positioning and fixing the radial bearing member 222, the thrust bearing member 223, and the positioning member 224 with respect to the bearing housing 221. The sealing member 226 is a member for pressing and fixing an O-ring 227A at the lower end of the space Sr described later from the lower side.

[0085] The bearing housing 221 has a substantially cylindrical hollow portion 221A extending in the Z-axis direction. The hollow portion 221A is formed in a stepped shape having a large diameter portion 221Aa as a main portion and a small diameter portion 221Ab formed at the lower end and having a smaller diameter than the large diameter portion 221Aa. Figure 7 As shown, a groove 221F is formed in the bearing housing 221 , and the groove 221F is engaged with a key 217 provided on the base 210 , so that the bearing housing 221 is positioned with respect to the base 210 .

[0086] The bearing housing 221 has flow paths 221B and 221C through which compressed air for forming an air bearing flows. The compressed air flowing through the flow path 221B is supplied to the radial bearing member 222, and the compressed air flowing through the flow path 221C is supplied to the thrust bearing member 223. One ends (inlets) of the flow paths 221B and 221C are connected to the air supply holes 215 and 216 of the base 210 via O-rings 218A and 218B, respectively.

[0087] The other end (outlet 221Be) of the flow path 221B opens at the large diameter portion 221Aa of the hollow portion 221A. Figure 7 As shown, two annular grooves 221D and 221E are formed concentrically with the hollow portion 221A on the upper surface of the bearing housing 221. The outlet 221Ce of the flow path 221C opens at the bottom surface of the outer groove 221D. In addition, an O-ring 227B is accommodated in the inner groove 221E.

[0088] The radial bearing component 222 is a substantially cylindrical component, and is formed with a substantially cylindrical hollow portion 222E penetrating in the Z-axis direction. The journal of the test object W is inserted into the hollow portion 222E. The radial bearing component 222 is divided into a cylindrical portion 222A, a flange portion 222B, and a protruding portion 222C in order from the bottom according to its outer diameter.

[0089] The cylindrical portion 222A is a substantially cylindrical portion with the smallest outer diameter that is housed in the hollow portion 221A of the bearing housing 221 , and has an outer diameter that is substantially the same as the inner diameter of the small diameter portion 221Ab of the hollow portion 221A.

[0090] The flange portion 222B is a disc-shaped portion having an outer diameter larger than the outer groove 221D of the bearing housing 221. The flange portion 222B is placed on the upper surface of the bearing housing 221 in a state where the radial bearing member 222 is assembled to the bearing housing 221.

[0091] The protruding portion 222C is a substantially cylindrical portion that protrudes upward from the center portion of the upper surface of the flange portion 222B and has a smaller outer diameter than the flange portion 222B.

[0092] An annular groove 222D for accommodating an O-ring 227C is concentrically formed on the lower surface of the flange portion 222B of the radial bearing member 222. The inner circumference of the groove 222D is substantially the same diameter as the inner circumference of the groove 221D of the bearing housing 221, and the width of the groove 222D is formed larger than that of the groove 221D.

[0093] The hollow portion 222E of the radial bearing component 222 has a large diameter portion 222Ea located in the center of the Z-axis direction, a small diameter portion 222Eb located in the upper portion, and a small diameter portion 222Ec located in the lower portion. The small diameter portion 222Eb is formed in the protruding portion 222C, the large diameter portion 222Ea is formed in the upper portion of the cylindrical portion 222A, and the small diameter portion 222Ec is formed in the lower portion of the cylindrical portion 222A. In addition, a radial air bearing is formed between the peripheral surfaces of the small diameter portions 222Eb and 222Ec and the journal of the test object W.

[0094] A plurality of radial bearing air supply holes 222F are formed at equal intervals in the circumferential direction at the lower portion of the cylindrical portion 222A, and the radial bearing air supply holes 222F penetrate the cylindrical portion 222A in the radial direction and open at the small diameter portion 222Ec. In addition, a plurality of radial bearing air supply holes 222G are formed at equal intervals in the circumferential direction at the upper portion of the radial bearing member 222 (including the flange portion 222B and the protrusion 222C disposed outside the bearing housing 221) to connect the outer periphery and the inner periphery of the radial bearing member 222. One end (inlet) of the radial bearing air supply hole 222G opens at the lower surface of the root of the flange portion 222B (the position facing the peripheral portion of the hollow portion 221A), and the other end (outlet) opens at the inner peripheral surface of the small diameter portion 222Eb. Furthermore, in the upper portion of the radial bearing member 222 , a plurality of thrust bearing air supply holes 222H are formed at equal intervals in the circumferential direction, connecting the lower end of the inner periphery of the groove 222D and the upper end of the inner periphery of the small diameter portion 222Eb.

[0095] When the radial bearing member 222 is mounted in the bearing housing 221, a cylindrical space Sr is formed between the cylindrical portion 222A of the radial bearing member 222 and the peripheral surface of the hollow portion 221A (large diameter portion 221Aa) of the bearing housing 221. The compressed air supplied from the outlet 221Be of the flow path 221B fills the space Sr.

[0096] In addition, a space Ss is formed by the groove 221D of the bearing housing 221, the lower end of the inner circumference of the groove 222D of the radial bearing component 222, and the O-ring 227C. The compressed air supplied from the outlet 221Ce of the flow path 221C fills the space Ss. The space Sr is sealed by the O-rings 227A and 227B, and the space Ss is sealed by the O-rings 227B and 227C. The radial bearing air supply holes 222F and 222G are connected to the space Sr at one end (inlet) thereof, and the compressed air in the space Sr is supplied to the small diameter parts 222Eb and 222Ec. In addition, the thrust bearing air supply hole 222H is connected to the space Ss, and the compressed air in the space Ss is supplied to the inner circumference of the thrust bearing component 223.

[0097] The thrust bearing component 223 is a precision component in the shape of an open circular plate (flat washer) having substantially the same inner and outer diameters as the protruding portion 222C of the radial bearing component 222. The journal of the test object W passes through the opening 223A of the thrust bearing component 223. The flange portion Wa of the test object W is placed on the inner circumference of the upper surface of the thrust bearing component 223 in a state where compressed air is not supplied from the thrust bearing air supply hole 222H.

[0098] When compressed air is supplied from the thrust bearing air supply hole 222H, a thrust air bearing is formed between the inner peripheral portion of the upper surface of the thrust bearing component 223 and the flange Wa of the test object W, and the test object W floats from the thrust bearing component 223. In addition, when the supply of compressed air is stopped, the test object W descends and the flange Wa is placed on the thrust bearing component 223. When the supply of compressed air is stopped before the rotation of the test object W is completely stopped, the flange Wa rubs against the thrust bearing component 223, so the upper surface of the thrust bearing component 223 gradually wears. If the wear amount of the thrust bearing component 223 increases, a good thrust air bearing cannot be obtained, and the floating of the test object W becomes unstable. Therefore, the thrust bearing component 223 needs to be replaced regularly. The thrust bearing component 223 of this embodiment is formed in a flat plate shape, so the front and back sides of the thrust bearing component 223 can be interchanged and both sides can be used for the formation of the thrust air bearing. Thus, the life of the thrust bearing member 223 is substantially extended by two times, and therefore, the cost required for replacement of the thrust bearing member 223 can be reduced.

[0099] The positioning member 224 is an annular member having a substantially cylindrical hollow portion 224C extending in the Z-axis direction, and includes a flange portion 224A and a cylindrical portion 224B. The cylindrical portion 224B is a substantially cylindrical portion extending vertically. The inner diameter of the cylindrical portion 224B is substantially the same as the outer diameter of the protruding portion 222C of the radial bearing member 222 and the thrust bearing member 223, and the protruding portion 222C of the radial bearing member 222 and the thrust bearing member 223 are accommodated in the hollow portion 224C of the cylindrical portion 224B without a gap.

[0100] The flange portion 224A is a substantially disk-shaped portion that protrudes toward the outer periphery from the lower end portion of the cylindrical portion 224B, and has substantially the same outer diameter as the flange portion 222B of the radial bearing member 222 .

[0101] The inner diameter of the claw 224h is smaller than the outer diameters of the protrusion 222C and the thrust bearing member 223 , and larger than the opening 223A of the thrust bearing member 223 .

[0102] Furthermore, the depth of the hollow portion 224C of the positioning member 224 (the distance from the lower surface of the flange portion 224A to the lower surface of the claw 224h) is equal to the sum of the height of the protruding portion 222C of the radial bearing member 222 and the height of the thrust bearing member 223. Therefore, the protruding portion 222C of the radial bearing member 222 and the thrust bearing member 223 are accommodated in the hollow portion 224C of the positioning member 224 without any gap in the vertical direction. That is, the positioning member 224 is used to position the thrust bearing member 223 relative to the radial bearing member 222.

[0103] The fixing member 225 is an annular member. The fixing member 225 has: a cylindrical hollow portion 225A, which is formed from the bottom surface to the front of the upper surface; and a circular opening 225B, which penetrates from the upper end of the hollow portion 225A to the upper surface of the fixing member 225. The hollow portion 225A has a substantially same diameter as the flange portion 222B of the radial bearing member 222 and the cylindrical portion 224B of the positioning member 224. The opening 225B is formed concentrically with the hollow portion 225A, and has a diameter smaller than the hollow portion 225A and larger than the cylindrical portion 224B of the positioning member 224. In addition, in the fixing member 225, holes for passing the fixing screws are formed at four locations at a position closer to the outside than the hollow portion 225A.

[0104] The hollow portion 225A is formed to have a depth equal to the sum of the height of the flange portion 222B of the radial bearing member 222 and the height of the flange portion 224A of the positioning member 224. Therefore, in a state where the lower surface of the fixing member 225 contacts the upper surface of the bearing housing 221, the upper surface of the flange portion 224A contacts the upper end surface of the hollow portion 225A, the lower surface of the flange portion 224A contacts the upper surface of the flange portion 222B, and the lower surface of the flange portion 222B contacts the upper surface of the bearing housing 221. That is, by fixing the bearing housing 221 with the fixing member 225, the positioning member 224, the thrust bearing member 223, and the radial bearing member 222 are fixed to the bearing housing 221.

[0105] By adopting a structure in which the positioning member 224, the thrust bearing member 223, and the radial bearing member 222 are fixed to the bearing housing 221 by fixing the bearing housing 221 with the fixing member 225, the radial bearing member 222, the thrust bearing member 223, and the positioning member 224 can be replaced by only removing and attaching the screw for fixing the fixing member 225. Therefore, it is easy not only to replace the bearing member corresponding to the size of the test body W, but also to repair and replace the parts such as the thrust bearing member 223 that are easy to wear. In addition, the thrust bearing member 223 is formed in such a way that both surfaces thereof can be used as the surface for forming the thrust air bearing. Therefore, even if one surface is worn, the other surface can be reused as the bearing surface, and the replacement frequency of the parts can be reduced. Furthermore, by making the thrust bearing member 223 into a shape that is easy to form as in the present embodiment, the unit price of the parts can be suppressed.

[0106] In addition, the thrust bearing component 223 can be easily replaced and its two surfaces can be used as thrust bearing surfaces, so the replacement frequency of the components can be reduced. Therefore, the positioning component 224 and the fixing component 225 can also be formed into one component. In addition, the shape of the thrust bearing component 223 can also be different from a disc shape, and can be used even after the front and back surfaces are interchanged. Furthermore, the bearing housing 221 and the radial bearing component 222 can also be formed into one component.

[0107] Fig. 9 , Fig.10 and Fig.11 They are respectively a front view, a right side view, and a plan view of the additional mechanism portion (the driving unit 300 , the guide unit 400 , the changing unit 500 , and the moving unit 600 ) of the dynamic balancing tester 1 .

[0108] like Figure 9-11As shown, the drive unit 300 includes a nozzle component 310 and a relay component 320. The nozzle component 310 is a substantially rectangular metal component, and is formed with a cylindrical hollow portion 311 that penetrates in the Z-axis direction. The hollow portion 311 is a portion surrounding the blades of the test object W during testing. Therefore, the inner peripheral surface of the hollow portion 311 is formed with a diameter that is sufficiently larger than the outer diameter of the test object W in a manner that does not contact the test object W.

[0109] Three nozzles 312 are formed on the inner peripheral surface of the hollow portion 311 to spray air toward the test object W. Two of the three nozzles 312 are forward spray nozzles 312A oriented in a manner to rotationally drive the test object W in a forward direction (counterclockwise when viewed from above), and one is a reverse spray nozzle 312B oriented in a manner to rotationally drive the test object W in a direction opposite to the forward direction (clockwise when viewed from above).

[0110] Flow paths 313A and 313B are formed in the injection nozzle member 310. One end of the flow path 313A opens on the right side of the lower surface of the injection nozzle member 310, and the other end branches and connects to the two forward injection nozzles 312A. One end of the flow path 313B opens on the left side of the lower surface of the injection nozzle member 310, and the other end connects to the reverse injection nozzle 312B.

[0111] During the dynamic balancing test, the nozzle assembly 310 rotates the object W to be tested in the counterclockwise direction by the forward nozzle 312A, and generates a clockwise driving force by the reverse nozzle 312B after the measurement is completed, thereby applying a brake to the rotation of the object W to be tested. By adopting a structure in which the reverse nozzle 312B brakes the rotation, the test time from the end of the measurement to the removal of the object W to be tested can be shortened.

[0112] The relay component 320 is divided into a relay component 320A fixed to the right end of the lower surface of the injection nozzle component 310 and a relay component 320B fixed to the left end of the lower surface of the injection nozzle component 310. Flow paths 322A and 322B are formed in the relay components 320A and 320B, respectively. One end of the flow paths 322A and 322B is connected to the flow paths 313A and 313B of the injection nozzle component 310, respectively. In addition, the other ends of the flow paths 322A and 322B are connected to corresponding compressed air supply sources (not shown) via connecting parts 321A and 321B, respectively.

[0113] In addition, the driving unit 300 is not limited to the structure of the present embodiment as long as it has a nozzle for blowing air to the test object W to rotate and drive it. For example, as long as there are more than one forward jet nozzle 312A, the test object W can be rotationally driven, and therefore, more than one forward jet nozzle 312A can be provided in the jet nozzle member 310. In addition, other braking mechanisms such as a mechanism for braking by friction by contacting with the journal of the test object W can be provided instead of the reverse jet nozzle 312B.

[0114] The driving unit 300 is supported by the stage 100 via the guide unit 400, the change unit 500, and the moving unit 600. The guide unit 400 includes four support rods 410, four guides 420, and two guide support bases 430A and 430B.

[0115] The support rods 410 are cylindrical members, and upper ends of two support rods 410 are fixed to the relay member 320A, while upper ends of the other two support rods 410 are fixed to the relay member 320B.

[0116] The guide 420 is a cylindrical member having a hollow portion 421 formed therein, and the hollow portion 421 supports the support rod 410 so that the support rod 410 can slide in its axial direction. A large diameter portion 422 having a larger diameter than the lower portion of the guide 420 is formed at the upper end portion of the guide 420.

[0117] The guide support platforms 430A and 430B are metal parts that are formed into a crank shape when viewed from the Y-axis direction and extend in the Y-axis direction, and are arranged opposite to each other in the X-axis direction. The guide support platforms 430A and 430B respectively have fixing parts 431A and 431B, vertical parts 432A and 432B, and guide support parts 433A and 433B. The vertical parts 432A and 432B are rectangular flat plate-shaped parts arranged perpendicular to the X-axis. The fixing parts 431A and 431B for fixing the guide support platforms 430A and 430B to the gantry 100 by bolts protrude outward from the lower ends of the vertical parts 432A and 432B in the X-axis direction. In addition, the guide support parts 433A and 433B that support the guide 420 protrude inward from the upper ends of the vertical parts 432A and 432B in the X-axis direction.

[0118] The fixing portions 431A and 431B are formed with a plurality of holes through which fixing bolts for fixing the guide support platforms 430A and 430B to the stage 100 pass.

[0119] A substantially rectangular opening 432Aa penetrating in the X-axis direction is formed in the center of the upper portion of the vertical portion 432A of the guide support base 430A.

[0120] The guide support parts 433A and 433B have two cylindrical through holes 430Aa and 430Ba extending in the Z-axis direction. The through holes 430Aa and 430Ba have substantially the same diameter as the outer diameter of the lower portion of the guide 420 and receive the lower portion of the guide 420. The guide 420 is supported by the guide support parts 433A and 433B in a state where the large diameter portion 422 is placed on the upper surface of the guide support parts 433A and 433B.

[0121] The support rod 410 fixed to the relay member 320A of the drive unit 300 is slidably inserted into the hollow portion 421 of the guide member 420 accommodated in the through hole 430Aa of the guide member support base 430A. In addition, the support rod 410 fixed to the relay member 320B is inserted into the guide member 420 accommodated in the through hole 430Ba of the guide member support base 430B. The guide member support bases 430A and 430B are fixed to the stage 100 at intervals in the X-axis direction with the guide member support portion 433A facing the left side and the guide member support portion 433B facing the right side. The drive unit 300 is guided by the guide unit 400 so as to be movable only in the Z-axis direction relative to the stage 100.

[0122] The driving unit 300 is supported on the stage 100 via the indicator rod 410 of the guide unit 400 , the changing unit 500 , and the moving unit 600 so as not to freely move in the up-down direction.

[0123] The changing unit 500 includes a supporting member 510 , a screw 520 , a coupling portion 530 , and a locking member 540 .

[0124] The support member 510 is a stepped cylindrical member extending in the Z-axis direction and having a small diameter portion 511 and a large diameter portion 512. The support member 510 is supported by the moving unit 600 with the small diameter portion 511 at the bottom. In addition, a cylindrical hole 513 extending in the Z-axis direction and rotatably supporting the screw 520 is formed on the upper surface of the support member 510.

[0125] The screw 520 includes a threaded portion 521 as an external thread and an operating portion 522. The threaded portion 521 has substantially the same diameter as the hole 513 formed in the support member 510, and is rotatably supported on the support member 510 by inserting its front end into the hole 513. The operating portion 522 is a handle for operating when the threaded portion 521 is rotated about the axis.

[0126] The connection part 530 includes a lifting member 531 and a support rod connection member 532. The lifting member 531 is a metal member formed in a crank shape when viewed from the Y-axis direction. The lifting member 531 includes a threaded fitting portion 531A extending in the X-axis direction, a vertical portion 531B extending downward from the X-axis negative direction end of the threaded fitting portion 531A, and a fixing portion 531C extending from the lower end of the vertical portion 531B in the X-axis negative direction. The fixing portion 531C is formed so that its cross section is smaller than the opening 432Aa of the vertical portion 432A formed in the guide support base 430A, and passes through the opening 432Aa.

[0127] The threaded fitting portion 531A is formed with an internal thread 531Aa that penetrates in the Z-axis direction near the center thereof in the X-axis direction and the Y-axis direction. The threaded portion 521 is fitted with the internal thread 531Aa. In addition, the threaded fitting portion 531A is formed with an internal thread 531Ab that penetrates in the Z-axis direction near the end thereof in the positive direction of the X-axis. The end of the fixing portion 531C in the negative direction of the X-axis is fixed to the end of the support rod connecting member 532 in the positive direction of the X-axis by a fixing member (not shown).

[0128] The support rod connection member 532 is a substantially rectangular metal plate arranged horizontally. The X-axis and Y-axis dimensions of the support rod connection member 532 are formed to be substantially the same as the X-axis and Y-axis dimensions of the injection nozzle member 310, respectively.

[0129] Openings 532A are formed near the four corners of the substantially rectangular support rod connection member 532, through which the lower end of the support rod 410 of the guide unit 400 passes. The support rod 410 passing through the opening 532A is fixed to the support rod connection member 532 by a fixing member 532B. In addition, a journal avoidance opening (not shown) is formed substantially coaxially with the rotation axis of the test object W in a manner that does not contact the journal of the test object W supported by the vibration unit 200.

[0130] The connecting portion 530 is limited to the Z-axis direction by the guide unit 400. Therefore, when the operating portion 522 is operated to rotate the screw member 520, the connecting portion 530 formed with the internal thread 531Aa engaged with the threaded portion 521 moves up and down along the Z-axis direction. With the up and down movement of the connecting portion 530, the four support rods 410 move up and down synchronously, and the driving unit 300 fixed to the upper end of the support rod 410 also moves up and down. That is, by operating the operating portion 522 of the change unit 500, the height direction position of the driving unit 300 can be adjusted.

[0131] In addition, the threaded fitting portion 531A is formed with an internal thread 531Ac extending from the internal thread 531Aa to the outside in the Y-axis direction. The threaded portion 541 (external thread) of the locking member 540 is fitted with the internal thread 531Ac. The threaded portion 541 has a length that enables its front end to reach the internal thread 531Aa. The operating portion 542 of the locking member 540 can be rotated and screwed into the threaded portion 541 until the front end of the threaded portion 541 reaches the internal thread 531Aa, thereby preventing the screw 520 from rotating.

[0132] That is, by providing the change unit 500 , the position of the driving unit 300 in the Z-axis direction can be changed and fixed to match the test object W having different shapes and sizes by a simple operation of rotating the operation portion 522 of the screw 520 and the operation portion 542 of the lock member 540 .

[0133] The moving unit 600 includes an actuator 610 and a stopper 620. The actuator 610 is a linear actuator that supports the change unit 500 in a manner that allows it to be raised and lowered. In the present embodiment, a cylinder is used as the actuator 610. A cylindrical hollow portion 611 that is substantially the same diameter as the small diameter portion 511 of the support member 510 of the change unit 500 and extends in the Z direction is formed on the upper surface of the actuator 610. The hollow portion 611 is connected to a fluid pressure device that supplies fluid pressure to the actuator 610. By moving the small diameter portion 511 inserted into the hollow portion 611 up and down using fluid pressure, the drive unit 300 can be raised and lowered via the change unit 500.

[0134] The stopper 620 includes a stopper 621 and a threaded portion 622 (external thread). The threaded portion 622 is engaged with the internal thread 531Ab formed in the threaded engagement portion 531A of the change unit 500. The stopper 620 is configured such that when the drive unit 300 is in a lowered position due to the operation of the actuator 610, the lower end of the threaded portion 622 abuts against the stopper 621.

[0135] The moving unit 600 is configured to raise and lower the Z-axis direction position of the driving unit 300 between a driving position that rotates and drives the test object W by blowing air to the test object W and a standby position that is lower than the driving position. By being configured to be able to lower the driving unit 300 to the standby position that is lower than the driving position, the test object W can be easily replaced. In addition, a structure is adopted in which the changing unit 500 is also raised and lowered together with the driving unit 300, so that the trouble of adjusting the Z-axis direction position of the driving unit 300 each time the test object W is replaced can be saved, and the operability and the position accuracy of the driving unit 300 can be improved.

[0136] The height of the standby position can be changed by using the length of the threaded portion 622 protruding from the lower surface of the threaded fitting portion 531A of the change unit 500. Therefore, by adjusting the screwing depth of the threaded portion 622 into the internal thread 531Ab, for example, even if the driving position is changed to a higher position, the height of the standby position can be maintained at a lower position. By adopting such a structure, it is possible to prevent the workability from being deteriorated due to the change of the driving position. In addition, if Figure 1 and Figure 2 As shown, in order to facilitate the assembly and disassembly of the test object W, the dynamic balancing tester 1 includes a lifting unit 150 that lifts up the journal of the test object W from the bottom to raise the position of the test object W in the Z-axis direction.

[0137] In addition, even if the positional relationship between the guide unit 400, the change unit 500 and the moving unit 600 is not the positional relationship as in the above-mentioned embodiment, as long as the structure is adopted that the lifting action of the drive unit 300 based on the moving unit 600 is performed between the driving position and the standby position, it is not limited to the content of the present embodiment. For example, a structure in which the positions of the change unit 500 and the moving unit 600 are interchanged can also be adopted. In addition, a structure in which the change unit 500 (moving unit 600) directly supports the drive unit 300 in a manner that the Z-axis direction position of the drive unit 300 can be changed (moved) can also be adopted, and the moving unit 600 (change unit 500) moves (changes) the Z-axis direction positions of the change unit 500 (moving unit 600) and the drive unit 300 via the guide unit 400. Furthermore, a structure in which the guide unit 400 is not provided, the drive unit 300 is provided at the top layer, and the drive unit 300, the change unit 500 and the moving unit 600 overlap can also be adopted.

[0138] The above is an explanation of an example of an embodiment of the present invention. The embodiment of the present invention is not limited to the contents of the above description, and various modifications can be made within the scope of the technical concept expressed by the scope of the claims. For example, the contents obtained by appropriately combining the embodiments described illustratively in the specification or self-evident embodiments are also included in the embodiments of the present application.

[0139] In the above embodiment, the bearing unit 220 is fixed to the lower end of the base 210, and the test body W is supported on the upper surface side of the bearing unit 220. However, as long as a structure is adopted in which the projection of the center of gravity of the test body W on the plane defined by the position where the transverse spring 120 is installed on the vibration unit 200 is located near the position where the longitudinal spring 110 is installed on the vibration unit 200, a structure in which the bearing unit 220 is fixed to the upper side of the base 210 and the test body W is suspended on the lower surface side of the bearing unit 220 may also be adopted.

[0140] In the above embodiment, the test object W as the test object is supported by the vibration unit 200 with the rotation axis vertically. However, a configuration may be adopted in which the rotation axis of the test object W is tilted by rotating the coordinate axis in the above embodiment around the X axis.

[0141] In the above-mentioned embodiment, a rotating body having a journal is envisioned as the test body, but the radial bearing component 222 may be configured to have a shape of a roughly cylindrical protrusion that does not have the hollow portion 222E but protrudes upward through the opening 223A of the thrust bearing component 223. By using the outer peripheral surface of the protrusion as the surface for forming a radial air bearing, a dynamic balancing test machine corresponding to a rotating body having a roughly cylindrical hollow rotating axis can be provided.

Claims

1. A dynamic balancing test machine, characterized in that: include: a driving unit that blows air to a rotating body that is rotatably supported to rotationally drive the rotating body; a moving unit that moves the driving unit in the direction of the rotation axis of the rotating body between a predetermined driving position in which the rotating body can be driven and a predetermined standby position in which the rotating body can be easily attached or detached; and a changing unit that changes the driving position in the direction of the rotation axis, The moving unit is configured to be restricted from moving in the driving position when moving from the standby position to the driving position. The changing unit comprises: a connecting member connected to the driving unit and capable of moving integrally with the driving unit; a supporting member supported by the moving unit so as to be movable in the direction of the rotation axis; and a mechanism interposed between the support member and the connection member and capable of adjusting the position of the connection member relative to the support member in the direction of the rotation axis, The moving unit is capable of moving the driving unit via the changing unit by moving the supporting member in the direction of the rotation axis. The changing unit can change the drive position in the rotation axis direction by adjusting the position of the connection member relative to the support member in the rotation axis direction.

2. The dynamic balancing tester according to claim 1, characterized in that: The connection member is configured such that a support rod connection member as a part thereof is connected to a support rod fixed to the driving unit via a fixing member.

3. The dynamic balancing tester according to claim 1, characterized in that: The changing unit includes a first screw mechanism that can move forward and backward in the direction of the rotation axis. The driving position can be changed in the rotation axis direction by adjusting the position of the connection member relative to the support member in the rotation axis direction using the first screw mechanism.

4. The dynamic balancing tester according to claim 3, characterized in that: The first thread mechanism has: A first internal thread member is formed at a position of the connecting member that faces the supporting member and extends in the direction of the rotation axis; and a first external threaded member engaged with the first internal threaded member and supported at one end by the supporting member, By rotating the first male screw to move it in the rotation axis direction, the position of the connecting member relative to the supporting member in the rotation axis direction can be adjusted.

5. The dynamic balancing tester according to any one of claims 1 to 4, characterized in that: The change unit has: A stopper fixed in a specified position; A second internal thread member formed at a position of the connecting member opposite to the stopper and extending in the direction of the rotation axis; and a second external thread member that engages with the second internal thread member and has one end that protrudes from the connecting member toward the stopper, At the standby position, one end of the second external screw abuts against the stopper, thereby stopping the movement of the drive unit to which the connecting member is fixed in the direction of the rotation axis. The standby position can be adjusted in the rotation axis direction by rotating the second external screw to move it in the rotation axis direction.

6. The dynamic balancing tester according to claim 5, characterized in that: A guide unit is provided for limiting the movement of the drive unit in the direction of the rotation axis. The guiding unit comprises: a support rod fixed to the drive unit; and A guide supports the support rod so as to be movable in the direction of the rotation axis.

7. The dynamic balancing tester according to claim 6, characterized in that: The guide unit has a plurality of support rods. The plurality of support rods are connected by the connection member.

8. The dynamic balancing tester according to any one of claims 1 to 4, characterized in that: A guide unit is provided for limiting the movement of the drive unit in the direction of the rotation axis. The guiding unit comprises: a support rod fixed to the drive unit; and A guide supports the support rod so as to be movable in the direction of the rotation axis.

9. The dynamic balancing tester according to claim 8, characterized in that: The guide unit has a plurality of support rods. The plurality of support rods are connected by the connection member.

10. The dynamic balancing tester according to claim 1, characterized in that: The moving unit is driven by a pneumatic cylinder.

11. The dynamic balancing tester according to claim 1, characterized in that: The driving unit has a nozzle that blows air toward the rotating body.

12. The dynamic balancing tester according to claim 11, characterized in that: The nozzle comprises: At least one forward injection nozzle for driving the rotating body to rotate in a forward direction; and At least one reverse jet nozzle is configured to rotationally drive the rotating body in a direction opposite to the forward direction.

13. The dynamic balancing tester according to claim 11, characterized in that: The driving unit has a hollow portion surrounding the outer periphery of the rotating body and penetrating in the direction of the rotating axis. The nozzle is formed on the inner periphery of the hollow portion.

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