JPS59107233A - Dynamic balance adjusting device of rotating body - Google Patents

Abstract

PURPOSE:To simplify the balance adjustment, by changing automatically the relative rotation phase of two concentrically fixed rotating members. CONSTITUTION:A burbine wheel of a turbocharger is rotated by compressed air from an air supply tube 20, and a concentrically fixed rotating body (blower impeller) 4 is rotated also. The oscillation at this time is detected by an oscillating detecting head 30; and if the detected value exceeds a prescribed value, compressed air is stopped to stop the rotation, and fixings of the turbine wheel and the rotating body 4 are loosened by a nut runner 32, and phases of both rotating bodies are changed by a rotating device 60. After both rotating bodies are fixed, compressed air is supplied again to test the oscillation; and this test is repeated until the detected value becomes the prescribed value or smaller. Thus, the balance adjustment of rotating bodies is simplified.

Description

Detailed Description of the Invention The present invention (i) relates to a dynamic balance adjustment device for a rotating body, and in particular, it is designed to reduce vibrations as much as possible during rotation of a rotating body in which two rotating members are fixed concentrically to each other and rotate integrally. The present invention relates to a device for aligning the relative phases of both rotating members in order to reduce the size of the rotary member.

A typical example of the above-mentioned rotating bodies is the rotating body of a turbocharger for an internal combustion engine. This rotating body includes a turbine wheel and a blower propeller that are concentrically connected to each other by a rotating shaft.When the turbine wheel is rotationally driven by the exhaust gas of the internal combustion engine, the blower propeller transfers air to the engine. This supercharges the combustion chamber. Since all rotating bodies rotate at extremely high speeds, they cannot be used if their dynamic balance is poor. Therefore,
Traditionally, all rotating bodies have been subjected to vibration tests.
For machines with excessive vibration, the dynamic balance has been improved by changing the relative rotational phase between the turbine wheel and the wind propeller, so that the vibration is below a standard value.

However, in the past, vibration tests were carried out by attaching the rotating body to a vibration tester, and for rejected products, the vibration test was carried out again after changing the relative rotational phase between the turbine wheel and the wind propeller. It is necessary to repeat this work, which requires a great deal of ingenuity, and if a rotating body with large vibrations occurs continuously, the vibration reduction work described above cannot be done in time, so it is not possible to produce the planned number of units. There were even situations that occurred that should not have happened.

The present invention aims to solve the above-mentioned conventional problems by providing a device that can perform vibration testing of rotating bodies and vibration reduction work for excessive vibrations all at once and automatically. It was done for a direct purpose. However, adjusting the dynamic balance of a rotating body to reduce vibration is necessary in a wide range of other technical fields, and the present invention is limited to a dynamic balance adjustment device for a rotating body of a turbocharger. isn't it. That is, it includes two or more rotating members that are fixed concentrically to each other and rotate integrally, and at least one of the rotating members is fixed to another rotating member by a screw member so that the screw member can be loosened. If the relative rotational phase of the rotating members can be changed in this state, the vibrations of any rotating body can be reduced by the dynamic balance adjustment device according to the present invention.

In order to achieve the above object, the dynamic balance adjustment device according to the present invention includes: (a support jig that rotatably supports a rotating body including first and second rotating members fixed by an aluminum member; (bl) A rotational drive device that rotates and stops the rotating body supported by the support jig; a screw member operating device that engages a portion other than the rotating member with the screw member to loosen and tighten the screw member; It is connected to a relative rotation device to rotate, a rotation drive device, a vibration detection head, a screw member operating device, and a relative rotation device, and is operated at a predetermined time to drive the rotation of the rotating body and detect vibration. let them do it;
The detection result is compared with a preset standard value, and if it is less than the standard value, it is judged as passing, while J1! ;If the value exceeds half the value, stop the rotation of the rotating body, loosen the screw member, rotate both rotating members relative to each other, tighten the screw member, drive the rotating body, detect vibration, and detect the detection result and reference value. The control device is configured to automatically repeat the comparison with 4% until the detection result becomes less than the reference value.

According to the device configured in this way, not only the vibration measurement of the rotating body and the pass/fail judgment of the vibration quality are automatically performed, but also the dynamic balance is automatically adjusted for rejected products. It is considered a passed product.

Therefore, the operator only needs to attach and detach the rotating body to and from the device and operate the control device. number is significantly reduced. Furthermore, if necessary, these tasks can also be automated and unmanned.

Moreover, once the rotating body is installed, there is no need to remove it from vibration measurement to completion of dynamic balance adjustment, which significantly shortens the time required for dynamic balance adjustment.
Even if rotating bodies with large vibrations appear one after another, this will no longer cause a decline in production volume, as was the case in the past.

be.

DESCRIPTION OF THE PREFERRED EMBODIMENTS A dynamic balance adjusting device for a rotating body of a turbocharger, which is an embodiment of the present invention, will be described in detail below with reference to the drawing J.

FIG. 1 shows a center assembly of a turbocharger, in which a rotating body 4 is rotatably held in a center housing 2. As shown in FIG. The rotating body 4 includes a rotating shaft 6 whose intermediate portion is rotatably supported by the housing 2 via a bearing, and a turbine wheel 8 and a wind impeller (hereinafter simply referred to as an impeller) 10 fixed concentrically to both ends of the rotating shaft 6. It consists of. The turbine wheel 8 is irremovably fixed to the rotating shaft 6 and constitutes one rotating member, and an impeller 10 as another rotating member is rotatable at a small diameter portion 11 formed at one end of the rotating shaft 6. In addition, it is pressed against and fixed to the stepped surface 13 of the rotating shaft 6 by a nut 12 as a screw member screwed onto the rotating shaft.

Therefore, when the nut 12 is tightened, the impeller 10 is integrated with the rotating shaft 6 and the turbine wheel 8. When the impeller 10 is loosened, the impeller 10 is connected to the rotating shaft 6 and the turbine wheel 8.
It becomes possible to rotate relative to.

FIG. 2 shows a device for vibration testing and dynamic lance adjustment of this center assembly. 14 in the figure
is a support jig main body, which is fixed to the base 18 via the bracket throat 16. The support jig main body 14 is similar to the turbine housing of a turbocharger, and by fixing the above-mentioned centano\Using 2 to this support jig main body 14, the rotating body 4 is connected to the Centano\Using 2 and the support jig. "The turbine wheel 8 is rotatably supported by the support jig consisting of the main body 14, and is rotationally driven by the compressed air supplied through the air supply pipe 20. That is, in this embodiment. In this case, the center housing 2' functions as a part of the support jig by being fixed to the support jig main body 14, but the turbine housing of the turbocharger itself is attached to the bracket 16 together with the center housing 2'. Attaching and detaching 1
．． It is also possible to function as a support jig. The air after rotationally driving the turbine wheel 8 is transferred to the support jig main body 1
4 is discharged through an exhaust pipe 22 connected to the exhaust pipe 22. Air supply pipe 2
0 is provided with a flow rate regulating valve 24, and this flow rate regulating valve 24 is connected to a control device 26. Control device 2
6 rotates the rotating body 4 according to a predetermined rotational speed pattern by controlling this flow rate regulating valve 24, and the rotation of this rotating body 4 is controlled by the impeller IO.
The speed is detected by a tachometer 28 using a laser beam provided on the outside in the radial direction, and feedback is sent back to the control device 26.

A vibration detection head 30 is attached to the support jig main body 14, and this head 30 is connected to a control device 26 and sends a signal of a magnitude corresponding to the vibration level of the support jig main body 14 to the control device 26. It is now possible to

A nut runner 32 is provided at the front of the support jig main body 14, while a rotational reaction force receiving device 34 is provided at the rear, and in this embodiment, both constitute a screw member operating device.

The nut runner 32 includes an impact wrench 36 that is driven by compressed air.
It is fixed concentrically and perfectly. A wrench socket 44 is attached to the tip of the rotating shaft of the impact wrench 36, and the impact wrench 36 is connected to the support jig main body 14.
This wrench socket 4
4 engages with the nut 12 of the rotating body 4 shown in FIG. 1 to loosen or tighten it. The supply of compressed air to the impact wrench 36 and the air cylinder 40 is controlled by solenoid valves 46 and 48, respectively.On the other hand, the rotary reaction force receiver 34 is connected to the air cylinder 50 fixed to the base 18 and its piston rond. The fixed reaction force receiver includes a member 52, and the member 52 is inserted into the exhaust pipe 22 through an axial slot formed in the exhaust pipe 22, and then bent at a right angle. It extends toward the support jig main body 14 along the center line of the exhaust pipe 22.A retaining member 54 with serration holes is fixed to the tip of the member 52, and the reaction force receiver is fixed to the tip of the member 52. The member 52 is connected to the support jig 14 by the reaction force receiver 50.
When the engaging member 54 is moved forward toward the serration portion 56 formed at one end of the rotating shaft 6 shown in FIG.
The rotation shaft 6 is configured to be engaged with the rotation shaft 6 to prevent the rotation shaft 6 from rotating. The reaction force receiver also includes the guy 1-rod 5 in the member 52.
7 is fixed, and this guide rod 57 passes through a bracket 58 for fixing the air cylinder 50 in parallel with the piston rod of the air cylinder 50, so that the reaction force receiver allows the member 52 to rotate around the axis of the piston rod. is prevented from doing. 59 is a solenoid valve.

A rotation device 60 for rotating the impeller 10 by a predetermined angle is further provided on the base 18. Rotating device 6
As shown in FIG. 3, the support jig 0 includes a movable stage 66 that is guided on a guide rail 62 fixed to the heath 18 and moved in a direction parallel to the center line of the support jig main body 14 by an air cylinder 64. The moving table 66 is connected to the support jig main body 1.
4 and a ring frame 68 concentric with the ring frame 68, and an annular bevel gear 70 is rotatably disposed within the ring frame 68. This bevel gear 70 is meshed with another bevel gear 74 fixed to the output shaft of a pulse motor 72 fixed to a moving table 66, and is rotated by a predetermined angle within the ring frame 68 as the pulse motor 72 rotates. It will be done.

An elastic ring 76 made of rubber or the like is fixed to the opening edge of the center hole of the bevel gear 70, and the movable stage 66 is connected to the air cylinder 6.
4 toward the support jig main body 14, this elastic ring 76 engages with the blades of the impeller 10 as shown by the two-dot chain line in FIG.
is configured to connect with. Note that 78 is a stopper bolt, which is provided to prevent the moving platform 66 from moving forward when the elastic ring 76 engages with the blades of the impeller IO as described above. Further, the supply of compressed air to the air cylinder 64 is controlled by a solenoid valve 80. Reference numeral 81 in FIG. 2 indicates a cover that covers the entire mechanical section of the dynamic balance adjustment device.

Including the solenoid valve 80, the solenoid valves 46, 48 and 5
9 and the pulse motor 72 are both connected to the control device 2.
6 and is controlled by this control device 26. This control device 26 also serves as an operation panel, and includes a setting device 82 for setting the vibration reference value of the rotating body 4, a display device 84 for displaying the set value, and a vibration detection device 7. and a display device 86 for displaying the measured vibration value detected by 30. Further, 88 is a start button for starting the device, 90 is an emergency stop button, 92 is a power lamp for indicating the power-on state, and 94 is an operation display for indicating that the device is in operation. The lamp 96 is a pass indicator lamp that indicates that the vibration test result is a pass, and the numeral 98 is a fail indicator lamp.

Next, a vibration test and dynamic balance adjustment work using the above device will be explained.

First, the assembled center assembly is attached to the support jig main body 14. Attachment is performed by connecting the center housing 2 to the support jig main body 14 using a predetermined connector (not shown), and as a result of this connection, the nut 12 of the center assembly is concentrically opposed to the wrench socket 44 of the nut runner 32, And serration part 5
6 is in a state where the rotation reaction force receiver is concentrically opposed to the engaging member 54 of the device 34.

Next, when the start button 88 of the control device 26 is operated, the flow rate adjustment valve 24 is opened and compressed air is supplied from the air supply pipe 20 to the support jig main body 14 which also serves as a turbine housing.
The turbine wheel 8 is driven to rotate. As a result, the impeller 10 also rotates integrally, and this rotational speed is measured by the tachometer 28 and fed back to the control device 26.

The control device 26 adjusts the flow rate regulating valve 24 so that the difference between the rotational speed fed back and the predetermined rotational speed pattern becomes zero, and as a result, the rotating body 4 of the center assembly reaches the predetermined rotational speed. The rotation speed can be increased according to the pattern. During this rotation, the vibration detection rod 30 detects the vibration of the support jig main body 14, that is, the radial vibration of the rotating body 4. The detection results are supplied to the control device 26 and stored.

Although both the turbine wheel 8 and the impeller 10 are manufactured to minimize dynamic unbalance, it is inevitable that slight unbalance will occur.
Each of these vibrates in the radial direction as the rotating body 4 rotates. Incidentally, the rotation 16 is bent, the nut 12 is unbalanced, etc., which cause vibrations in the rotating body 4, and these vibrations can also be eliminated by adjusting the phase of the impeller 10. However, for ease of understanding, the turbine wheel will be used here. 8 and the impeller 10, and if the vibration of the turbine wheel 8 is represented by a solid line and the vibration of the impeller 10 is represented by a broken line, these are shown in FIG. As illustrated in FIGS. 1 to 10, various relative phase differences can be obtained.

Now, if these vibrations appear with a phase difference of 180 degrees as shown in FIG. 4, they will cancel each other out. However, the amplitudes of the two are usually different, and since the turbine wheel 8 and the impeller lO are separated by a certain distance in the width direction, the vibrations are not completely canceled out, and the vibration of the rotating body 4 as a whole becomes the smallest. In such a state, the level of vibration detected by the vibration detection head 30 is set by the setting device 82.
Since the value is normally smaller than the reference value set in the control device 26, the control device 26 determines the pass, turns on the pass indicator lamp, and stops the operation of the dynamic balance adjustment device. That is, the flow rate adjustment valve 24 is closed to stop the rotation of the rotating body 4.

When the center assembly is removed after stopping, the vibration test work for one center assembly is completed.

The above is the operation when the center assembly passes the vibration test in the assembled state, but if the result of the first vibration test is a failure, the following operation is performed. For example, when the phases of the vibrations of the turbine wheel 8 and the impeller 10 match exactly as shown in FIG. 5, the vibration of the rotating body 4 becomes the largest. Therefore,
There is a possibility that the control device 26 will make a rejection judgment, but if this judgment is made, the rejection indicator lamp will light up, the flow rate adjustment valve 24 will be closed, and the rotation of the rotating body 4 will stop. I am made to do so. At the end of the deceleration process of the rotating body 4, a command is issued from the control device 26 to operate the rotational reaction force receiver device 34 and the air cylinder 50, and the reaction force receiver is activated by the engagement member 54 provided at the tip of the part JtA52. is engaged with the serration portion 56 of the rotating body 4 to prevent the rotating body 4 from rotating.

Subsequently, the air cylinder 64 of the rotating device 60 is operated based on the command from the control bag W26, causing the elastic ring 76 of the bevel gear 70 to engage with the blades of the impeller 10. At the same time, the air cylinder 40 of the nut runner 32 is also operated, causing the wrench socket 44 attached to the tip of the impact wrench 36 to engage with the nut 12 of the rotating body 4. This engagement may not be achieved simply by moving the wrench socket 44 in the axial direction, but if the in-vacuum wrench 36 subsequently starts rotating, the engagement will definitely occur at the beginning of the rotation. It will be done. impact wrench 36
The rotation takes place only for a short time, thereby loosening the NAND 12 by a predetermined amount. In this state, the impeller 10 and the rotating shaft 6 are able to rotate relative to each other.

In this state, the pulse motor 72 is rotated based on a command from the control device 26, and the bevel gear 70 is rotated by 90 degrees via the bevel gear 74.

The bevel gear 70 is engaged with the impeller 10 by an elastic ring 76, and since the rotation of the rotating shaft 6 is prevented by the rotational reaction force receiving device 34, the impeller 10 is rotated at 90 degrees with respect to the rotating shaft 6. The plane of the impeller 10 is rotated, and the relative rotational phase of the impeller 10 with respect to the turbine wheel 8 is changed by 90 degrees. That is, in this embodiment, the rotational reaction force receiving device 34 also serves as a part of a relative rotation device that rotates the turbine wheel 8 and the impeller 10 by a predetermined angle. After this phase adjustment is performed, the impact wrench 36 of the slot runner 32 is again rotated in the opposite direction to the aforementioned direction, and the slot 2 is tightened.

After that, it is connected to the command from the control device 26.

In the I-runner 322 rotational reaction force receiver, the device 34 and the rotating device 60 are simultaneously separated from the rotating body 4.

Subsequently, the clearing HIM regulating valve 24 is opened, the rotating body 4 is rotated, and the vibration test is performed again. If the results of the first vibration test were as shown in Figure 5, the vibration phase of the turbine wheel 8 and impeller 10 should change as shown in Figure 6 by changing their positions. In this case, the vibration of the entire rotating body 4 has not yet fallen below the reference value. Therefore, the control device 26 makes a judgment of failure, and -
The same operation as described above is repeated, and the relative phase between the turbine wheel E (and the impeller 10) is further changed by 110 degrees. As a result, the vibration phase of both is shifted by 180 degrees as shown in Figure 4. As a result, the vibration level of the rotating body 4 falls below the reference value, the control device 26 determines whether the vibration test has passed, the pass indicator lamp 96 lights up, and the rotation of the rotating body 4 reaches ('\+l-Saichi). Therefore, if the sensor and assembly are removed from the support jig main body 14, one cycle of the vibration test and dynamic balance adjustment work is completed.

Above, two extreme cases have been described: a case where the relative phase between the turbine wheel 8 and the impeller 10 is in a state where vibration is favorable and a case where it is in an unfavorable state. It is normal to be in an intermediate state. For example, as shown in Figure 6 in the initially assembled state,
The state will be in the state shown in FIG. 7, FIG. 8, FIG. 9, or FIG. 1O. For example, if you are in the state shown in Figure 6, if you change the phase by 90 degrees once, you will be in the state shown in Figure 4 and you will pass the test, and if you are in the state shown in Figure 7, you will pass the test. Figures 5 and 6 can be obtained by changing the phase by 90 degrees three times.
After passing through the state shown in the figure, the test should reach the state shown in Fig. 4 and be passed. In addition, if the phase is shifted by about 45 degrees as shown in FIG. 8, the state shown in FIG. 9 will be obtained by performing the phase adjustment by 90 degrees once.

If the measured vibration level is below the standard (+I'j) in this state, the rotating body 4 passes the test. However, if it fails in the state shown in Figure 9, the 90-degree phase change is performed again. However, even if this phase change is performed, only the vibration phase of both will change as shown in Fig. 10, and the vibration level of the entire rotating body should hardly change.In this case, the vibration level of the rotating body will be reduced. is determined to be between the state shown in FIG. 9 and the state shown in FIG. 10, and the pulse motor 72 is rotated 45 degrees in the opposite direction to the normal direction. The vibration phase becomes the state shown in Fig. 4, and the rotating body 4 becomes a passed product.Furthermore, the vibration phase of the assembled rotating body 4 is in a state other than that shown in Figs. 4 to 10. In this case, the product will be close to one of these, and the final product will be adjusted to a state between the state shown in Figure 4 and the state shown in Figure 9, and the product will pass. .

As is clear from the above explanation, in this embodiment, while the vibration level fluctuates greatly as a result of the phase change, the impeller 10 is rotated in the positive direction by 90 degrees, and the vibration level changes by changing the phase twice before and after. is not so large, the impeller IO is rotated 45 degrees in the opposite direction, and as a result, all rotating bodies 4 are normally accepted. However, in the event that the measured vibration level does not fall below the reference value even after the above operations, the control device 26 determines that the dynamic balance of the rotating body 4 cannot be adjusted, and the failure indicator lamp is turned on. Stop the operation of the dynamic balance adjustment device while keeping 98 lit.

Although certain embodiments of the present invention have been described in detail above, the present invention should not be limited thereto. For example, instead of rotating the impeller 10 as an adjustable rotating member,
By preventing the rotation of the impeller 10 and rotating the rotating shaft 6 and the turbine wheel 8 as a rotating member fixed thereto, the relative phase of the two rotating members, that is, the impeller 10 and the turbine wheel 8, can be adjusted. It is also possible to configure the relative rotation device to change the .

Further, the rotating body is not limited to the turbocharged rotating body, but as long as it is a rotating body in which a plurality of rotating members are fixed to each other concentrically and with relative rotational phase change capability by screw members, Vibration can be reduced by the dynamic balance adjustment device according to the present invention. Of course, the rotating member fixed to the rotating shaft 6 may be formed integrally with the rotating shaft 6.

In addition, the center assembly of a turbocharger has a structure in which a turbine wheel and an impeller, which are rotating members, are fixed to both ends of a rotating shaft whose intermediate portion is rotatably held by the center housing. Although it is preferable to use it as part of a support jig for a body, depending on the structure of the rotor, it is also possible to rotatably support the rotation axis of the rotor itself by the support jig.

Furthermore, if a non-contact type vibration detection head is used, it is possible to measure the vibration of the rotating body itself, and if the vibration of the rotating body is measured in such a way that the vibration mode can be determined,
It is possible to determine by calculation how to change the mutual phases of the rotating members of the rotating body to obtain the optimum state in terms of vibration prevention.

Therefore, if the control device is capable of this calculation and can also control the relative rotation device based on the calculation results, it will be possible to make all products pass with a single phase change, and The efficiency of balance adjustment work is further improved.

In addition, it goes without saying that the present invention can be implemented with various modifications and improvements based on the knowledge of those skilled in the art without departing from the spirit thereof.

[Brief explanation of the drawing]

FIG. 1 is a front view (partially cut away) of a center assembly of a turbocharger in which dynamic balance adjustment is performed by an apparatus according to an embodiment of the present invention. 21st! I is a system diagram of a dynamic balance adjustment device that is an embodiment of the present invention, and also serves as a plan view of the main mechanical parts. FIG. 3 is a plan view illustrating a main part of the rotating device in the apparatus shown in FIG. 2 in cross section. 4 to 10 are graphs showing various vibration phase differences between the turbine wheel and the impeller in the center assembly shown in FIG. 1. FIG. 2: Center housing 4: Rotating body 6: Rotating shaft
8: Terhiso wheel 10 Nibro wine propeller I2: Nasoto I4: Support jig body 2o: Air supply pipe 22: Exhaust pipe 24
:Flow p adjustment valve 26:Control unit W 28:Rotary needle 3
0: Vibration detection head 32: Nano tranner 34: Rotation reaction force receiver device 44: Wrench socket 54: Engagement member
56: Serration section 60: Rotating device
70: Bevel gear 72: Pulse motor 76: Elastic ring 82: Setting device 84.86: Display device 96:
Pass indicator lamp 9th: Reject indicator lamp Applicant: Tokota Automobile Co., Ltd. Figure 4 Figure 6 Figure 8 rv! 10 [] Figure 5 Figure 7 Figure 9 (゛]

Claims (1)

[Scope of Claims] includes first and second rotating DB members fixed concentrically to each other by a rod member, and when the rod member is loosened, the relative rotational phase of the two rotary members can be changed. A dynamic balance adjustment device that changes the relative rotational phase of both rotating members in order to reduce vibrations during rotation of a rotating body, comprising: a support jig that rotatably supports the rotating body; and a support jig that rotatably supports the rotating body; A rotational drive device that rotates, stops, and rotates a rotating body supported by a jig; A vibration detection node that detects vibrations of the rotating body during rotation; and a portion of the rotating body other than the first rotating member when the rotating body is stopped. and a screw member operating device that engages with the screw member to loosen and tighten the screw member, and a relative rotation that relatively rotates both rotating members by a predetermined angle while the screw member is loosened. The device is connected to the rotary drive device, the vibration detection head, the screw member operating device, and the relative rotation device, and is operated at a predetermined time to perform rotational drive of the rotating body and vibration detection, and to record the detection results in advance. Compare it with the set standard value, and if it is below the standard value, it will be judged as passing, but if it exceeds the standard value, the rotation of the rotating body will be stopped, the screw member will be loosened, and the relative rotation of both rotating members will be rotated. , a control device that automatically repeats the tightening operation of the screw member, the rotational drive of the rotating body, the detection of vibration, and the comparison of the detection result with a reference value until the detection result becomes equal to or less than the reference value. A dynamic balance adjustment device for rotating bodies.