JP2010025862A - Rotary machine support device and design method thereof - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary machine support device capable of vibration inspection of a rotary machine in a sweep operation region with sufficient accuracy, and to provide its design method. <P>SOLUTION: The rotary machine support device 10 supports the rotary machine 1 having a turbine blade 3 driven and rotated by fluid and a rotational axis 7 to which the turbine blade 3 is fixed. Further, the rotary machine support device has a base part 50 and a support part 51 for supporting the rotary machine 1, and the support part 51 includes a mount member 15 for supporting a rotary machine 1, and a spring member 52 for attaching the mount member 15 to the base part 50. A first vibration measurement system including the support part 51 and the rotary machine 1 is constituted such that the resonance frequency at least in a vibration measurement direction may be lower than initial number of rotations of the sweep operation region of the rotary machine 1, and a second vibration measurement system excluding the spring member 52 from the first vibration measurement system is constituted such that the resonance frequency may be higher than final number of rotations of the sweep operation region of the rotary machine 1. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a rotating machine support device that can be supported when a rotation balance inspection is performed on a rotating machine that is rotationally driven by a fluid, and a design method thereof.

  In a rotating machine that is rotationally driven by a fluid, the rotational balance is corrected. Such a rotary machine includes a supercharger, a turbo compressor, a gas turbine, and the like. The conventional rotation balance correction will be described by taking a supercharger as an example.

  A supercharger is a device that supplies compressed air to an engine by using exhaust gas energy of an engine mounted on a vehicle or a ship. The turbocharger includes a turbine blade that is rotationally driven by the exhaust gas of the engine, a compressor blade that supplies compressed air to the engine by rotating integrally with the turbine blade, and a turbine blade that is coupled to one end and the other end. And a rotating shaft to which the compressor blades are coupled. The supercharger includes a turbine housing that houses the turbine blades therein, a compressor housing that houses the compressor housing, and a bearing housing in which a bearing that supports the rotating shaft is incorporated.

The supercharger rotational balance inspection is performed before the supercharger is shipped as a product.
For example, the rotation balance inspection is performed by the apparatus shown in FIG. As shown in FIG. 11, a compressor housing (not shown) is removed from the supercharger 21 in which all the components have been assembled. Next, the turbine housing (support portion) 23 of the supercharger 21 is attached to the support body (base portion) 27 with bolts 25 or the like. Thereafter, the rotating body including the turbine blade 29, the compressor blade 31, and the rotating shaft 33 is rotationally driven by supplying the turbine blade 29 with compressed gas having the same pressure as the exhaust gas of the engine. When the rotating body reaches a predetermined rotation speed, the rotation angle detector 37 detects the rotation angle of the rotating body while detecting the acceleration (that is, vibration) of the rotating body with the acceleration pickup 35. Thereby, for example, the calculator 38 detects how much acceleration (vibration) is generated at which rotation angle at a predetermined rotation speed. An unbalance amount is obtained based on the detected data. Balance correction is performed by removing a part of the rotating body (for example, a part of the nut 39) so as to eliminate the unbalanced amount (for example, see Patent Document 1).
JP 2002-39904 A

By the way, after performing the balance correction, a sweep operation is performed in which the rotational speed is gradually increased to tens of thousands to 100,000 rpm that is the range of use of the turbocharger, which is harmful at all the rotational speeds in this sweep operation range. It is desirable to confirm that there is no vibration.
However, when measuring the vibration characteristics of the rotating body of the supercharger in the sweep operation range, there is a possibility that the measurement varies and the inspection cannot be performed with high accuracy.

  The present invention has been made in view of such circumstances, and it is an object of the present invention to provide a rotating machine support device and a design method thereof that can accurately perform vibration inspection of the rotating machine in the sweep operation region. Yes.

  When the resonance frequency of the vibration measurement system between the rotating machine and the support portion that supports the rotating machine exists in the sweep operation region, the inventor vibrates by amplifying the vibration of the vibration measuring system (rotating machine) by resonance. We gained the knowledge that the variation in measurement becomes large and accurate measurement becomes difficult. And based on such knowledge, this invention was completed.

  A rotating machine support device according to the present invention includes a turbine blade that is rotationally driven by a fluid, and a rotating machine support device that supports a rotating machine having a rotating shaft to which the turbine blade is fixed. A support member for supporting the rotating machine, and a spring member for attaching the mount member to the base part. The first vibration measurement system including the rotary machine is configured such that at least the resonance frequency in the vibration measurement direction is lower than the initial rotational speed in the sweep operation range of the rotary machine, and the spring member is excluded from the first vibration measurement system. The second vibration measurement system is characterized in that the resonance frequency is higher than the final rotation speed in the sweep operation region of the rotating machine.

According to the rotating machine support device of the present invention, the resonance frequency in at least the vibration measurement direction of the first vibration measurement system is set lower than the initial rotational speed in the sweep operation region, so that disturbance vibration during vibration measurement in the sweep operation region Can be insulated. In addition, since the resonance frequency of the second vibration measurement system is set higher than the final rotation speed in the sweep operation region, there is no harmful resonance point in the sweep rotation speed, and generation of vibration due to resonance can be suppressed.
Therefore, vibration inspection in the sweep rotation range can be performed with high accuracy.

  In the rotary machine support device, it is preferable that the first vibration measurement system is set such that the resonance frequency of each of the six degrees of freedom is lower than the initial rotational speed in the sweep operation range of the rotary machine.

  According to this configuration, all the resonance frequencies of six degrees of freedom are set lower than the initial rotational speed in the sweep operation region, so that disturbance vibration can be more reliably insulated.

  In the rotary machine support device, the second vibration measurement system is configured such that each of the resonance frequencies of the constituent members constituting the second vibration measurement system is higher than the final rotation speed. It is preferable.

  According to this configuration, it is possible to prevent harmful resonance from being included in the sweep rotation range and perform highly accurate measurement.

  The rotating machine support device design method of the present invention is a turbine blade driven to rotate by a fluid, and a rotating machine support device design method for supporting a rotating machine having a rotating shaft to which the turbine blade is fixed. The rotation support device includes a base, and a support including a mount member that supports the rotating machine and a spring member for attaching the mount member to the base. The support and the rotation The first vibration measurement system including the machine is designed so that at least the resonance frequency in the vibration measurement direction is lower than the initial rotational speed in the sweep operation region of the rotary machine, and the first vibration measurement system and the spring And a step of designing the second vibration measurement system excluding the member so that the resonance frequency is higher than the final rotation speed in the sweep operation region of the rotary machine. To.

According to the design method of the rotating machine support device of the present invention, since the resonance frequency of at least the vibration measurement direction of the first vibration measurement system is set lower than the initial rotational speed of the sweep operation region, vibration measurement is being performed in the sweep operation region. Can be isolated. In addition, since the resonance frequency of the second vibration measurement system is set higher than the final rotational speed of the sweep operation region, there is no harmful resonance point in the sweep operation region, and the occurrence of vibration due to resonance can be suppressed.
Therefore, it is possible to obtain a rotating machine support device that can accurately perform vibration inspection in the sweep operation region.

  Moreover, in the design method of the rotating machine support device, it is preferable that the resonance frequency of each of the six degrees of freedom is set lower than the initial rotational speed for the first vibration measurement system.

  According to this configuration, all the resonance frequencies of six degrees of freedom are set lower than the initial rotational speed in the sweep operation region, so that disturbance vibration can be more reliably insulated.

  Further, in the design method of the rotating machine support device, with respect to the second vibration measurement system, the resonance frequency of each component constituting the second vibration measurement system is set higher than the final rotation speed. It is preferable.

  According to this configuration, it is possible to prevent harmful resonance from existing in the sweep operation range, and it is possible to perform highly accurate measurement.

  Moreover, in the design method of the rotating machine support device, it is preferable to set the resonance frequency of the first vibration measurement system by changing the shape and / or material of the spring member.

  According to this configuration, the spring constant in the first vibration measurement system can be lowered by changing the shape and / or material of the spring member, and as a result, the resonance frequency in the first vibration measurement system is swept. It can be made lower than the initial rotational speed of the region.

  Moreover, in the design method of the rotating machine support device, it is preferable that the resonance frequency in the second vibration system is set by providing a reinforcing portion on the mount member.

  According to this configuration, the spring constant in the second vibration measurement system is improved by providing the reinforcing portion on the mount member, and as a result, the resonance frequency in the second vibration measurement system is made higher than the final rotational speed in the sweep operation region. Can be high.

  ADVANTAGE OF THE INVENTION According to this invention, the vibration test | inspection in a sweep rotation area can be accurately performed with respect to a rotary machine.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
Fig.1 (a) is a figure which shows the structure of the supercharger supported by the rotation support apparatus which concerns on this embodiment. As shown in FIG. 1A, the supercharger 1 includes a turbine blade 3 that is rotationally driven by the exhaust gas of the engine, and a compressor blade that supplies compressed air to the engine by rotating integrally with the turbine blade 3. 5 and a rotating shaft 7 having a turbine blade 3 connected to one end and a compressor blade 5 connected to the other end. The turbocharger 1 includes a turbine housing 9 that houses the turbine blades 3 therein, a compressor housing that houses the compressor blades 5 (not shown in the present embodiment because it is removed), rotation, And a bearing housing 8 in which bearings 8a and 8b for supporting the shaft 7 are incorporated.

  The turbine housing 9 is formed with a scroll flow path 9a through which a fluid (exhaust gas from the engine) for rotationally driving the turbine blades 3 flows. The bearing housing 8 and the turbine housing 9 are coupled by the coupling member 2.

  FIG. 1B is a diagram showing the coupling member 2 viewed from the axial direction of the rotating shaft 7. As shown in FIG. 1B, the coupling member 2 includes a pair of semicircular arc members 2a that are divided from each other, and a bolt 2b and a nut 2c that couple the pair of semicircular arc members 2a. Composed. In addition, you may make it connect the bearing housing 8 and the turbine housing 9 directly with a volt | bolt etc., without using the coupling member 2. FIG.

  FIG. 2 is a diagram illustrating a cross-sectional configuration of the rotating machine support device 10 according to the present embodiment. The rotating machine support device 10 is a support device that can be supported when the rotation balance inspection of the supercharger 1 is performed. 2 shows a state in which the supercharger 1 shown in FIG. 1A is attached to the rotating machine support device 10. 3 is a view taken along the line AA in FIG. 2, and FIG. 2 is a view taken along the line BB in FIG. FIG. 4 is a detailed perspective view of the rotary machine support device 10.

The rotating machine support device 10 is mainly configured by a base portion 50 and a support portion 51 that is mounted on the base portion 50 and supports the supercharger 1.
The support portion 51 includes a mount member 15 that supports the rotary machine, and a spring member 52 for attaching the mount member 15 to the base portion 50. Furthermore, the support part 51 is provided with the housing member 6 for supercharger attachment, and the pressing member 11 as the component.

  The support portion 51 is attached to the base portion 50 by fixing one end side of the spring member 52 attached to the mount member 15 to an attachment portion (not shown) provided in the base portion 50.

  That is, when the supercharger 1 is supported on the rotating machine support device 10, the turbine housing 9 and the compressor housing (not shown) of the supercharger 1 are removed, and the housing member 6 that replaces the turbine housing 9 is provided. The housing member 6 (flow channel portion 14) and the turbine housing 9 attached to the finished product may be different in at least one of shape and size.

  The housing member 6 includes a flow path portion 14 and an attachment portion 13. The flow path portion 14 is formed with a flow path 14 a for flowing a fluid for rotationally driving the turbine blade 3. On the other hand, the flow path 14 a is not formed in the attachment portion 13. In the present embodiment, the flow path portion 14 and the attachment portion 13 are separate members that are divided from each other.

  The pressing member 11 applies a pressing force to the pressed portion 1a of the supercharger 1 at a position closer to the compressor blade 5 than the flow path 14a. As shown in FIGS. 2 to 4, the pressed portion 1 a is a part of the bearing housing 8, and is a protruding portion that protrudes from the outer peripheral surface of the bearing housing 8 in the radial direction of the rotating shaft 7. As shown in FIG. 3, the pressed portion 1 a has an annular shape when viewed from the axial direction of the rotating shaft 7.

  The mount member 15 is provided with a pressing force generator 12 that presses the pressing member 11 against the pressed portion 1a. As this pressing force generator 12, for example, a hydraulic type was used. That is, in the example of FIGS. 2 to 4, the pressing member 11 is a clamp rod of a hydraulic clamp. In this case, the pressing member 11 may be a known swing-type clamp rod that is moved in the axial direction of the rotary shaft 7 while turning by hydraulic pressure. The hydraulic chamber to which the hydraulic pressure is supplied is formed inside the hydraulic clamp body (pressing force generator 12), and the hydraulic clamp body is fixed to the mount member 15. In the example of FIG. 2, four hydraulic clamps including such a clamp rod (pressing member 11) and a hydraulic clamp body (pressing force generator 12) are provided in the circumferential direction of the rotating shaft 7 at intervals.

The attachment portion 13 sandwiches the pressed portion 1a with the pressing member 11 at a position closer to the compressor blade 5 than the flow path 14a. Thereby, the to-be-pressed part 1a is pressed against the attachment part 13 with the said pressing force.
As shown in FIG. 4, the attachment portion 13 is fixed to the mount member 15 by a bolt (not shown) provided in the bolt hole 16. As shown in FIG. 2, the flow path portion 14 is attached and fixed to the mount member 15 by a coupling means such as a bolt 17 inserted into the bolt hole 19. In other figures (FIGS. 2 and 3), the bolt holes 16 are not shown.

  Specifically, as shown in FIG. 2, the attachment portion 13 has an inner portion 13a and an extension portion 13b. The inner portion 13a has the same position in the radial direction of the rotating shaft 7 as the pressed portion 1a, and receives the pressing force.

  The extension portion 13b extends radially outward from the inner portion 13a to the outside of the flow path portion 14, and is coupled to the mount member 15 by the bolt at the end on the turbine blade 3 side to exert a pressing force on the mount member 15. Let As a result, the pressing force can be applied to the mount member 15 with little or no pressing force acting on the turbine housing 9.

  FIG. 5 is a diagram in which members other than the attachment portion 13 in FIG. 3 are omitted, and a plan configuration diagram of the attachment portion 13 is shown. As shown in FIG. 5, the attachment portion 13 is formed with an opening 13 c (see FIG. 5) into which the bearing housing 8 is inserted. That is, the mounting portion 13 is circular as viewed from the axial direction so as to match the shape of the opening 13c, and the outer peripheral surface of the bearing housing 8 is inserted and fitted into the opening 13c of the mounting portion 13. .

  That is, the mount member 15 supports the supercharger 1 through the pressing member 11 and the housing member 6 including the attachment portion 13 and the pressing member 11 as described above. Therefore, a pressing force by the pressing member 11 is applied to the mount member 15 via the mounting portion 13.

  In order to attach the supercharger 1 to the rotating machine support device 10 described above, the turbine housing 9 and the compressor housing are first removed from the finished supercharger 1 (see FIG. 11). On the other hand, the flow path portion 14 and the attachment portion 13 are attached (fixed) to the mount member 15 in this order. Next, the turbine blade 3 is passed through the opening 13 c and a part of the bearing housing 8 is inserted into the opening 13 c of the mounting portion 13. In this state, the pressed member 1 presses the pressed portion 1 a of the bearing housing 8 against the mount member 15 via the mounting portion 13. Thereby, the supercharger 1 is attached and fixed to the mount member 15. Note that attachment (fixation) of the flow path portion 14 and the attachment portion 13 to the mount member 15 is performed by a coupling means such as a bolt as described above.

By the way, in general, a rotating machine such as a supercharger performs rotation balance inspection and balance correction processing as necessary before product shipment.
In the rotational balance inspection, a rotating body composed of a turbine blade, a compressor blade, and a rotating shaft is attached to a rotating machine support device, and is rotationally driven at a predetermined number of rotations to obtain an unbalance amount of the rotating body. Then, the balance of the rotating body is corrected by removing a part of the rotating body (for example, a part of the nut connecting the compressor blade and the rotating shaft) so as to eliminate the unbalance amount.

  Further, after performing the balance correction, a sweep operation is performed in which the turbocharger is gradually increased in speed to tens of thousands (for example, 40,000) to 100,000 rpm or more which is a normal use range. At this time, it is confirmed that no harmful vibration occurs at all the rotational speeds in the sweep operation region.

  FIG. 6 is a diagram showing vibration characteristics when a rotation inspection is performed in the sweep operation range for the supercharger 1 after balance correction supported by the rotating machine support device 10. FIG. 7 is a comparative view showing the vibration characteristics generated when the rotation inspection is performed in the sweep rotation range in the conventional rotating machine support device, and FIG. 7A corresponds to FIG. FIG. 7B corresponds to FIG. 6 and 7, a line graph is drawn for each excitation force of the supercharger 1. That is, in FIGS. 6 and 7, a plurality of line graphs show a case where the position of the test weight (not shown) provided at the tip of the rotating shaft 7 is changed and the excitation force of the supercharger 1 is varied. ing.

In FIG. 6A and FIG. 7A, the horizontal axis indicates the rotational speed [Krpm] of the turbine. The vertical axis indicates the relative value of the influence coefficient α. The influence coefficient α is a value obtained by α = G / U. Here, G is the acceleration amplitude [m / s ² ] that the bearings 8a, 8b of the supercharger 1 receive from the rotating shaft 7 when the turbine is driven to rotate, U is the turbine blade 3, the rotating shaft 7, and This is the unbalance amount [g] of the rotating body composed of the compressor blades 5. That is, the influence coefficient α indicates the degree of influence on the vibration in the rotating body during rotation.
In FIGS. 6B and 7B, the horizontal axis indicates the rotational speed [Krpm] of the turbine blade, and the vertical axis indicates the phase of the influence coefficient α (that is, the rotational angle of the rotating body) [deg]. Show.

Based on FIG. 6 and FIG. 7, the characteristics of the rotating machine support device according to the present embodiment and the conventional rotating machine support device are compared.
In the conventional rotating machine support device, the correlation between the sweep operation range of the supercharger and the resonance frequency of the vibration measurement system composed of the supercharger and the support portion that supports the supercharger is considered. Therefore, there is a possibility that the resonance frequency of the vibration measurement system exists in the sweep operation range of the turbocharger. If the resonance frequency of the vibration measurement system exists in the sweep operation range in this way, resonance will amplify the vibration of the vibration measurement system (rotary machine), resulting in large variations in vibration measurement and making accurate measurement difficult. End up.

  Thus, when the resonance frequency exists in the sweep operation range, it can be seen that the influence coefficient α and its phase vary depending on the difference in the excitation force, as shown in FIGS. 7 (a) and 7 (b). That is, when the resonance frequency exists in the sweep operation region, it means that the linearity in the influence coefficient α is broken (indicating non-linearity). If the influence coefficient α varies in this manner, errors in vibration measurement increase, and it is difficult to accurately grasp the vibration phenomenon in the sweep region.

  As described above, the inventor finds that when the resonance frequency of the vibration measurement system between the rotating machine and the support portion that supports the rotating machine exists in the sweep rotation region, variation in vibration measurement increases and accurate measurement is difficult. I got the knowledge that And based on this knowledge, the rotary machine support apparatus 10 which concerns on this embodiment was comprised as follows.

  That is, in the rotating machine support device 10 according to the present embodiment, the first vibration measurement system including the support portion 51 and the supercharger 1 is configured such that the resonance frequency in at least the vibration measurement direction has a sweep operation range of the supercharger 1. It was made to be configured to be lower than the initial rotational speed. Furthermore, in the rotary machine support device 10 according to the present embodiment, the second vibration measurement system obtained by removing the spring member 52 from the first vibration measurement system is used in the sweep operation region of the turbocharger 1. It was configured to be higher than the final rotation speed.

  In the present embodiment, as described in the design method described later, each shape is designed so as to eliminate resonance points in the first vibration measurement system and the second vibration measurement system from within the sweep operation range.

  As a result, the influence coefficient α does not vary due to the difference in the excitation force (the influence coefficient α maintains the linearity), and variations in vibration measurement within the sweep operation range are suppressed. 6 (a) and 6 (b), a plurality of broken lines are overlapped.

  FIG. 8 shows the results of the rotational balance inspection of the supercharger 1 in the sweep region in the case where the rotary machine support device 10 according to the present embodiment and the conventional rotary machine support device are used as the comparison target. FIG. 8A shows the result according to the present embodiment, and FIG. 8B shows the result according to the prior art. In addition, the several broken line in Fig.8 (a), (b) has each shown the vibration characteristic of the multiple types of supercharger.

  As shown in FIG. 8B, conventionally, since the influence function varies in the sweep operation range, the vibration measurement cannot be performed satisfactorily, and it is difficult to understand the difference in the vibration phenomenon due to the individual difference of the turbocharger. On the other hand, according to the present embodiment, as shown in FIG. 8A, since there is no resonance point in the sweep operation range, it is possible to clearly grasp the difference in the vibration phenomenon due to the individual difference in the supercharger.

  Therefore, according to the present embodiment, after performing the unbalance correction as described above, even when the inspection for confirming the rotational balance of the supercharger 1 is performed in the sweep rotational range, highly accurate measurement can be performed. it can.

(Design method of rotating machine support device)
Then, the design method of the said rotary machine support apparatus 10 is demonstrated.
First, in the first vibration measurement system including the support unit 51 and the supercharger 1 supported by the support unit 51, at least the resonance frequency in the vibration measurement direction is higher than the initial rotational speed in the sweep operation region of the supercharger 1. Design to be low (step S1).

  FIG. 9 is a diagram showing a three-dimensional shape model for vibration analysis in the first vibration measurement system. In this figure, the axis direction of the rotation axis is the X axis direction, and the directions orthogonal to the X axis are YZ directions. Axial direction.

  Specifically, in the present embodiment, a vibration analysis simulation is performed using the three-dimensional shape model M, and the first vibration measurement system is set so that all the resonance frequencies of six degrees of freedom are lower than the initial rotational speed of the sweep operation range. decide. Note that the six degrees of freedom include three degrees of freedom of translational vibration in each of the XYZ axes in FIG. 9 and three degrees of freedom in the rotational direction around each of the XYZ axes.

  The resonance frequency can be adjusted to be low by, for example, reducing the spring constant of the spring member 52. Specifically, the spring constant can be lowered by narrowing one side of the two-dimensional block spring of the spring member 52 shown in FIG. 9 or deepening the slit S.

  In the present embodiment, a two-dimensional block spring is used as the spring member 52. However, the present invention is not limited to this, and a coil spring or a leaf spring can also be used. When using a coil spring, the spring constant can be lowered as described above by reducing the coil wire diameter or increasing the winding density of the spring. When using a leaf spring, the spring constant can be lowered by reducing the thickness of the leaf spring. The spring constant may be lowered by changing the material of the spring member 52 as well as the shape and lowering the Young's modulus.

  As described above, in the vibration analysis simulation, the above-described spring constant may be set under the condition that all the resonance frequencies of the six degrees of freedom in the first vibration measurement system are lower than the initial rotational speed in the sweep operation range. Most desirable.

However, it may be difficult to set the spring constant so that the resonance frequency satisfies the above condition in all six degrees of freedom. In such a case, a sweep mode is not necessarily required for a vibration mode (for example, a vibration mode orthogonal to the measurement direction, a rotation vibration mode centered on the measurement direction) that hardly affects the measurement direction of the vibration measurement sensor in the rotating machine support device 10. It is not necessary to make it lower than the initial rotational speed of the region.
That is, with respect to the first vibration measurement system, it is possible to set the spring constant so that at least the resonance frequency in the vibration measurement direction is lower than the initial rotational speed in the sweep operation region.

  For example, when the vibration measurement direction of the vibration measurement sensor in the rotating machine support device 10 coincides with the Z-axis direction in FIG. 9, the rotation mode (resonance frequency) in the X-axis direction, the Y-axis direction, and the Z-axis center is the sweep operation range. May be included. When the vibration measurement direction coincides with the Y-axis direction, the rotation mode (resonance frequency) about the X-axis direction, the Z-axis direction, and the Y-axis center may be included in the sweep operation range. When the vibration measurement direction matches the X-axis direction, the Y-axis direction, the Z-axis direction, and the rotation mode (resonance frequency) about the X-axis center may be included in the sweep operation region.

Subsequently, in addition to the above-described step S1, the second vibration measurement system obtained by removing the spring member 52 from the first vibration measurement system has a resonance frequency higher than the final rotational speed of the sweep operation region of the turbocharger 1. (Step S2).
In this case, the resonance frequency of each member constituting the second vibration measurement system is set higher than the final rotation speed. That is, among the members, the lowest resonance frequency is set higher than the final rotation speed.

Hereinafter, a case where the resonance frequency of the mount member 15 is adjusted to be high will be described as an example.
First, a three-dimensional shape model relating to the mount member 15 is formed, and vibration analysis simulation is performed on this model.
As a result, for example, when the mount member 15 is twisted, a reinforcing member that increases the thickness of the member is provided so as to improve the strength only in the twisting direction. If such reinforcement is performed, the mass of the mount member 15 increases, but in this case, there is no problem because the resonance frequency (spring constant) of the first vibration measurement system described above decreases.

  FIG. 10 shows changes in the shape of the 3D model when the resonance frequency of the mount member 15 is increased, and FIG. 10A is a diagram showing the configuration of the mount member before improvement (initial design). 10 (b) is a view showing the structure of the mount member 15 after improvement. Each figure shows a 3D model at the time of the simulation result, and is in a state where twisting occurs.

When the resonance frequency is made higher than the final rotation speed, it is necessary to set the value to 2 KHz or higher. As shown in FIG. 10A, the mount member 100 at the initial design has a structure in which the mounting position of the spring member is the mount lower portion 100a and the digging portion 101 is large, and the resonance frequency is 1904 Hz. there were.
On the other hand, in the mount member 15 according to the present embodiment, as shown in FIG. 10B, a part of the housing 6 is used as a reinforcing member that improves the strength against the twisting direction caused by the digging portion 101. The above-mentioned mounting portion 13 is provided. Furthermore, in this embodiment, the attachment position of the spring member 52 was changed to the mount center part 15a. As a result, the resonance frequency of the mount member 15 could be improved to 2288 KHz.

  By the way, if the mass of the mount member 15 itself increases with reinforcement, the resonance frequency may not change as a result. Therefore, in the shape change accompanied with the improvement in strength, it is important how to perform the reinforcement to improve the Young's modulus in the vibration direction with the same mass. Since the resonance frequency is proportional to the value of √ (elastic modulus / specific gravity), in order to increase the resonance frequency of the mount member 15, it is preferable to employ a material having a high elastic modulus and / or a material having a low specific gravity. Examples thereof include fine ceramics and MMC (Metal Matrix Composites).

  Even when the resonance frequency is set to be higher than the final rotation speed, the vibration mode that hardly affects the measurement direction of the vibration measurement sensor in the rotating machine support device 10 is not necessarily higher than the final rotation speed in the sweep operation region. There is no need to do.

  For example, when the vibration measurement direction of the vibration measurement sensor in the rotary machine support device 10 coincides with the Z-axis direction in FIG. 10 and the mount member 15 is twisted (rotated) about the Z-axis, the torsion mode is the sweep operation. You may be allowed to enter the area. When the vibration measurement direction in the rotary machine support device 10 coincides with the Y-axis direction, the resonance frequency of the vibration mode of the Y-axis center vibration generated in the mount member 15 may be included in the sweep operation region. Similarly, when the vibration measurement direction in the rotary machine support device 10 coincides with the X-axis direction, the resonance frequency of the vibration mode of the vibration about the X-axis center generated in the mount member 15 may be included in the sweep operation region.

According to the design method of the rotating machine support device according to the present embodiment, the resonance frequency in at least the vibration measurement direction of the first vibration measurement system is set lower than the initial rotational speed of the sweep operation region. The disturbance vibration during measurement can be isolated. In addition, since the resonance frequency of the second vibration measurement system is set higher than the final rotational speed of the sweep operation region, there is no harmful resonance point in the sweep operation region, and the occurrence of vibration due to resonance can be suppressed.
Therefore, it is possible to design the rotating machine support device 10 that enables the vibration inspection in the sweep operation range to be accurately performed.

The present invention is not limited to the embodiments described above, and various modifications can be made without departing from the spirit of the present invention.
The rotating machine support device of the present invention can be applied to other rotating machines such as a turbo compressor and a gas turbine in addition to the supercharger. That is, the rotary machine support device of the present invention can be applied to any rotary machine that is rotationally driven by supplying fluid to the turbine blades.

It is a figure which shows the structure of the supercharger supported by the rotation support apparatus which concerns on this embodiment. It is a figure which shows the cross-sectional structure of a rotary machine support apparatus. It is an AA arrow directional view of FIG. It is a perspective view which shows the detailed structure of a rotary machine support apparatus. The plane block diagram of an attachment part is shown. It is a figure which shows the vibration characteristic of the rotary machine supported by the rotary machine support apparatus. It is a figure which shows the vibration characteristic of the rotary machine supported by the conventional rotary machine support apparatus. It is a figure for demonstrating the effect of the rotating machine support apparatus which concerns on this embodiment. It is a figure for demonstrating the design method of a rotary machine support apparatus. It is a figure for demonstrating the design method of a rotating machine support apparatus following FIG. It is a block diagram for performing the rotation balance test | inspection of the conventional supercharger.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Supercharger (rotary machine), 3 ... Turbine blade, 7 ... Rotary shaft, 10 ... Rotary machine support apparatus, 15 ... Mount member, 50 ... Base part, 51 ... Support part, 52 ... Spring member

Claims (8)

In a rotating machine support device for supporting a rotating machine having a turbine blade rotationally driven by a fluid and a rotating machine to which the turbine blade is fixed,
A base part and a support part for supporting the rotating machine,
The support part includes a mount member that supports the rotating machine, and a spring member for attaching the mount member to the base part,
The first vibration measurement system including the support unit and the rotary machine is configured such that at least the resonance frequency in the vibration measurement direction is lower than the initial rotational speed of the sweep operation range of the rotary machine
The second vibration measurement system obtained by removing the spring member from the first vibration measurement system has a resonance frequency higher than the final rotation speed in the sweep operation range of the rotary machine. apparatus.   2. The rotary machine support according to claim 1, wherein the resonance frequency of each of the six degrees of freedom is set to be lower than an initial rotational speed of a sweep operation range of the rotary machine. apparatus.   3. The second vibration measurement system according to claim 1, wherein each of the resonance frequencies of the constituent members constituting the second vibration measurement system is set higher than the final rotation speed. A rotating machine support device according to claim 1. In a method of designing a rotating machine support device that supports a rotating machine having a turbine blade that is rotationally driven by a fluid and a rotating machine to which the turbine blade is fixed.
The rotation support device includes a base part, and a support part including a mount member that supports the rotating machine and a spring member for attaching the mount member to the base part,
The first vibration measurement system including the support portion and the rotary machine is designed so that at least a resonance frequency in the vibration measurement direction is lower than an initial rotational speed in a sweep operation range of the rotary machine, and the first A rotary machine comprising a step of designing a second vibration measurement system obtained by removing the spring member from a vibration measurement system so that a resonance frequency is higher than a final rotation speed in a sweep operation range of the rotary machine. Support device design method.   5. The method for designing a rotating machine support device according to claim 4, wherein the resonance frequency of each of the six degrees of freedom is set lower than the initial rotational speed for the first vibration measurement system.   6. The second vibration measurement system according to claim 4 or 5, wherein a resonance frequency of each component member constituting the second vibration measurement system is set higher than the final rotational speed. Design method for rotating machine support device.   The rotary machine support device according to any one of claims 4 to 6, wherein the resonance frequency of the first vibration measurement system is set by changing a shape and / or a material of the spring member. Design method.   The method for designing a rotary machine support device according to any one of claims 4 to 7, wherein the resonance frequency of the second vibration system is set by providing a reinforcing portion on the mount member.

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