JP5526513B2 - Fluid pressure seal and rotating machine subject to vibration measurement using it - Google Patents

Description

  The present invention relates to a fluid pressure utilization seal provided between an outlet forming surface in which an outlet from which a fluid flows out is formed and an inlet forming surface in which an inlet through which fluid flows from the outlet is formed. The present invention also relates to a vibration measurement target rotating machine that uses a fluid pressure seal and is a vibration measurement target.

  When fluid is introduced from the outlet to the inlet, a seal is used between the outlet forming surface and the inlet forming surface in order to seal the fluid flow path from the outside.

  For example, the fluid is lubricating oil and is supplied to a bearing of a rotating body in a rotating machine such as a supercharger. In this case, the outlet is an opening formed in the outlet forming surface at the tip of the fluid pipe through which the lubricating oil flows, and the inlet is the outer surface (inlet) of the stationary side portion of the rotating machine to which the bearing is attached. It is an opening formed on the (formation surface). A flow path through which lubricating oil flows from the inlet to the bearing is formed inside the stationary side portion.

As shown in FIG. 8, there is an O-ring at the connection point between the outlet forming surface 54 in which the outlet 53 in the fluid pipe 51 is formed and the inlet forming surface 57 in which the inlet 59 in the stationary side portion 55 is formed. 61 (FIG. 8A) or a flat seal 63 (FIG. 8B) can be used. Reference numeral 51 a indicates a flange of the fluid pipe 51.
FIG. 8A shows a case where an O-ring 61 is used. By pressing the O-ring 61 against the inflow port forming surface 57 with the pressing force indicated by the arrow in this figure, the flow path 65 is sealed from the outside.
FIG. 8B shows a case where the flat seal 63 is used. By pressing the flat seal 63 against the inlet forming surface 57 with the pressing force indicated by the arrow in this figure, the flow path 65 is sealed from the outside. The flat seal 63 has a flat surface in contact with the inlet forming surface 57.

As prior art documents of the present application, there are the following patent documents 1 and 2.
JP 2002-39904 A JP-A-2005-207805

  A pressing force acts on the inflow port forming surface 57 by sealing the flow path 65 described above. That is, when the O-ring 61 and the flat seal 63 are used, in order to seal the flow path 65, it is necessary to strongly press the O-ring 61 and the flat seal 63 against the inlet forming surface as shown in FIG. Accordingly, a large pressing force (for example, 10 kgf) acts on the inflow port forming surface 57.

  Such a large pressing force is not preferable when measuring vibrations of a rotating machine (refer to Patent Documents 1 and 2 for details) as follows. This vibration measurement is performed when the rotating body of the rotary machine described above is rotating at a high speed. In this case, if the above-described pressing force is applied to the stationary side portion (casing) of the rotating machine, vibration inherent to the rotating machine is attenuated. Therefore, there is a possibility that the vibration characteristics unique to the rotating machine cannot be measured and extracted with high accuracy.

  For this reason, a seal is desired that allows the connection portion between the outlet and the inlet to be sealed without causing almost any pressing force (external force) to act on the inlet forming surface 57.

Therefore, an object of the present invention is to provide a seal that can seal a connection portion between an outflow port and an inflow port without almost applying an external force to the inflow port formation surface.
Another object of the present invention is to provide a vibration measurement target rotating machine that is a vibration measurement target that enables highly accurate vibration measurement using such a seal.

In order to achieve the above object, the seal of the present invention utilizes fluid pressure.
That is, the present invention provides a fluid pressure utilization seal provided between an outlet forming surface in which an outlet from which a fluid flows out is formed and an inlet forming surface in which an inlet through which fluid flows from the outlet is formed. Because
The fluid pressure utilization seal is attached to the outlet forming surface so as to surround a fluid passage region from the outlet to the inlet.
Further, the fluid pressure utilization seal is located at an inner tip that is in contact with the inlet forming surface and surrounds the inlet, and away from the inner tip in a direction from the inlet center toward the inlet outer peripheral edge and surrounds the fluid passage region. An outer portion and an enlarged portion extending from the inner tip to the outer portion and surrounding a fluid passage region,
The enlarged portion is pressed against the inflow port formation surface by the fluid pressure in the fluid passage region, so that the fluid passage region is kept sealed from the outside.

  According to the fluid pressure utilization seal of the present invention described above, since the enlarged portion is pressed against the inlet forming surface by the fluid pressure in the fluid passage region, the fluid passage region is sealed (sealed) with respect to the outside. The seal is made by the fluid pressure only by applying a small force for bringing the inner tip into contact with the inlet forming surface from the fluid pressure utilizing seal to the inlet forming surface. Therefore, it is possible to seal the connection portion between the outlet and the inlet with almost no external force acting on the inlet forming surface.

  According to a preferred embodiment of the present invention, the fluid pressure utilizing seal is elastically deformed by the fluid pressure in the fluid passage region, and thereby the enlarged portion is pressed against the inlet forming surface.

  Thus, by elastically deforming the fluid pressure utilization seal by the fluid pressure in the fluid passage region, the enlarged portion can be pressed against the inlet forming surface so as to be in close contact with the inlet forming surface. Thereby, the connection location of an outflow port and an inflow port can be sealed more reliably.

Further, according to a preferred embodiment of the present invention, the cross-sectional shape of the enlarged portion by a plane including the central axis of the fluid pressure utilization seal is a direction inclined from the central axis from the inlet forming surface to the outer portion. It extends in the direction toward the outlet .

Thus, the cross-sectional shape of the enlarged portion by a plane including the central axis of the fluid pressure utilization seal, from the inflow port providing surface to the outer part, a direction inclined from the central axis in a direction toward the outlet port side Since it extends, the seal is elastically deformed by the fluid pressure in the flow path, thereby increasing the contact area between the inner tip and the enlarged portion and the inflow port forming surface. This provides a more secure seal.

In order to achieve the other object, the present invention is a vibration measurement target rotating machine that uses the above-described fluid pressure utilization seal and is a vibration measurement target,
A rotating body that is driven to rotate;
A stationary side portion that supports the rotating body via a bearing,
The inflow port is an opening through which lubricating oil flows from the outflow port, and the lubricating oil that has flowed into the inflow port is supplied to the bearing,
The inflow port forming surface is provided on a stationary side portion.

  According to the above-described rotating machine subject to vibration measurement of the present invention, when the inlet forming surface on which the inlet for introducing the lubricant is formed is provided on the stationary side, the stationary side (that is, the inlet forming) The connection portion between the outlet and the inlet can be sealed with almost no external force acting on the surface). As a result, vibration is not attenuated by an external force for sealing the connection portion, so that vibration characteristics of the rotating machine can be extracted and measured with high accuracy.

  According to the present invention described above, the connection portion between the outlet and the inlet can be sealed with almost no external force acting on the inlet forming surface.

  The best mode for carrying out the present invention will be described with reference to the drawings. In addition, in each figure, the same code | symbol is attached | subjected to a common or corresponding part, and the overlapping description is abbreviate | omitted.

[Fluid pressure seal]
FIG. 1A is a longitudinal sectional view showing a configuration of a fluid pressure utilization seal 10 according to an embodiment of the present invention. FIG. 1B is a view taken along line 1B-1B in FIG.

  The fluid pressure utilization seal 10 according to the present embodiment seals a connection portion between the outflow port 3 through which the fluid flows out and the inflow port 5 through which the fluid from the outflow port 3 flows in using the fluid pressure. In the example of FIG. 1A, the outlet 3 is formed on the outlet forming surface 4 at the tip of the pipe 7, and the inlet 5 is the outer surface (inlet forming surface 9) of the member that receives the fluid from the outlet 3. ).

The fluid pressure utilization seal 10 is provided between the outlet forming surface 4 and the inlet forming surface 9. Moreover, the fluid pressure utilization seal 10 is attached to the outlet forming surface 4 so as to surround the fluid passage region 11 from the outlet 3 to the inlet 5.
As shown in FIG. 1A, the fluid pressure utilization seal 10 includes an inner tip 13 that extends in contact with the inlet forming surface 9 that forms the inlet 5 and surrounds the inlet 5, and a flow from the center of the inlet 5. An outer portion 15 that is located away from the inner tip 13 in the direction toward the outer peripheral edge of the inlet 5 and surrounds the fluid passage region 11, and extends from the inner tip 13 to the outer portion 15. And an enlarged portion 17 surrounding the. In this example, the inner tip 13 has an annular shape when viewed from the direction of the central axis C of the fluid pressure utilization seal 10, and each of the outer portion 15 and the enlarged portion 17 has a cross-sectional shape by a plane orthogonal to the central axis C. (Hereinafter referred to as a cross-sectional shape) is annular (see FIG. 1B). In this example, the inner tip 13 is a flat contact surface, and the outer portion 15 has a cylindrical shape. In this example, as shown in FIG. 1A, the enlarged portion 17 has a cross-sectional shape (hereinafter, referred to as a vertical cross-sectional shape) by a plane including the central axis C in a direction inclined outward from the central axis C. And extends linearly from the inner tip 13 to the outer portion 15 in the direction toward the outlet 3.

  In this embodiment, the whole fluid pressure utilization seal 10 is formed of an elastic body such as rubber. That is, the inner front end 13, the outer portion 15, and the enlarged portion 17 are formed of an elastic body such as rubber. In this case, preferably, the inner tip 13, the outer portion 15, and the enlarged portion 17 are integrally formed.

  In the example of FIG. 1 (A), the outer portion 15 is fixed and adhered to the outflow port forming surface 4 of the flange 7a at the tip of the pipe 7 in a watertight manner by an adhesive or other coupling means. A use seal 10 is attached to the pipe 7.

FIG. 1A shows a state in which no fluid flows through the fluid passage region 11 inside the fluid pressure utilization seal 10. On the other hand, FIG. 2 shows a state in which a fluid flows in the fluid passage region 11 in the configuration of FIG.
As shown in FIG. 2, when the fluid passes through the fluid passage region 11, the fluid pressure (for example, 300 to 500 kPa) acts on the fluid pressure utilization seal 10. As a result, the enlarged portion 17 is pressed against the inflow port forming surface 9 by the fluid pressure in the fluid passage region 11, so that the fluid passage region 11 is kept sealed from the outside. In the present embodiment, as shown in FIG. 2, the fluid pressure utilization seal 10 is elastically deformed by the fluid pressure in the fluid passage region 11 (for example, 300 to 500 kPa), whereby the enlarged portion 17 is formed on the inlet forming surface 9. Pressed. The contact area between the fluid pressure utilization seal 10 and the inflow port formation surface 9 in FIG. 2 is larger than that in the state of FIG.

According to the fluid pressure utilization seal 10 of the above-described embodiment, the enlarged portion 17 is pressed against the inflow port forming surface 9 by the fluid pressure in the fluid passage region 11, thereby maintaining the sealing (seal) of the fluid passage region 11 with respect to the outside. Therefore, the seal is made by the fluid pressure only by applying a micro force for bringing the inner tip 13 into contact with the inlet forming surface 9 from the fluid pressure utilizing seal 10 to the inlet forming surface 9. Therefore, it is possible to seal the connection portion between the outflow port 3 and the inflow port 5 with almost no external force acting on the inflow port formation surface 9. Further, since the inflow port forming surface 11 and the fluid pressure utilization seal 10 are merely brought into contact with each other, the fluid pressure utilization seal 10 and the structure on the pipe 7 side can be easily attached to and detached from the inflow port formation surface 9.
Further, the fluid pressure utilization seal 10 is elastically deformed by the fluid pressure in the fluid passage region 11, so that the enlarged portion 17 can be pressed against the inlet forming surface 9 so as to be in close contact with the inlet forming surface 9. Thereby, the connection location of the outflow port 3 and the inflow port 5 can be more reliably made the fluid pressure utilization seal 10.
Furthermore, since the longitudinal cross-sectional shape of the enlarged portion 17 extends from the inlet forming surface 9 to the outer portion 15 in a direction inclined from the central axis C toward the outlet 3 , the fluid pressure utilizing fluid pressure When fluid pressure acts on the utilization seal 1010, the fluid pressure utilization seal 10 is elastically deformed, and the contact area between the fluid pressure utilization seal 10 (that is, the inner tip 13 and the enlarged portion 17) and the inflow port formation surface 9 increases. Therefore, the sealing is performed more reliably.

[Rotating machine subject to vibration measurement using a fluid pressure seal]
Next, a rotary machine 20 (referred to as a vibration measurement target rotary machine) that is a vibration measurement target using the fluid pressure utilization seal 10 will be described. FIG. 3 is a configuration diagram of the vibration measurement target rotating machine 20.

  In the example of FIG. 3, the vibration measurement target rotating machine 20 is a supercharger. The supercharger 20 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 20 includes a turbine blade 21 that is rotationally driven by the exhaust gas of the engine, a compressor blade 23 that supplies compressed air to the engine by rotating integrally with the turbine blade 21, and the turbine blade 21 coupled to one end. And a rotating shaft 24 to which the compressor blade 23 is coupled at the other end. The turbocharger 20 includes a turbine housing 25 that houses the turbine blades 21, a compressor housing (not shown) that houses the compressor blades 23, and a bearing 27 that supports the rotating shaft 24. Bearing housing 29. The turbine blades 21, the compressor blades 23, and the rotating shaft 24 constitute a rotating body of the vibration measurement target rotating machine 20. The turbine housing 25, compressor housing and bearing housing 29 are stationary sides.

Vibration measurement of the vibration measurement target rotating machine 20 (in this example, a supercharger) is performed as follows.
The vibration measurement turbine housing 25 of the supercharger 20 from which the compressor housing (not shown) is removed is attached to the vibration measurement support 31 with bolts 28 or the like. Thereafter, compressed gas having the same pressure as the exhaust gas of the engine is supplied to the turbine blades 21 through a flow path (not shown) formed in the turbine housing 25, whereby the turbine blades 21, the compressor blades 23, and the rotation are supplied. The rotating body composed of the shaft 24 is driven to rotate. When the rotating body reaches a predetermined rotational speed, the rotation angle detector 35 measures the rotation angle of the rotating body while measuring the vibration (that is, acceleration) of the rotating body with the acceleration pickup 33 attached to the bearing housing 29. . Thereby, for example, the calculator 37 measures how much vibration (acceleration) is generated at which rotation angle at a predetermined rotation speed. The unbalance amount is obtained based on this measurement data. The balance is corrected by removing a part of the rotating body (for example, a part of the nut 39) so as to eliminate the unbalance amount.

  At the time of the above-described vibration measurement, the above-described fluid pressure utilization seal 10 is used in order to accurately measure the vibration inherent in the supercharger 20. The fluid pressure utilization seal 10 is provided between the lubricating oil supply pipe 7 and the bearing housing 29. An outflow port 3 is formed at the tip of the lubricating oil supply pipe 7, and an inflow port 5 is formed in the inflow port forming surface 9 which is the outer surface of the bearing housing 29. Lubricating oil flows into the inflow port 5 from the outflow port 3 at a pressure of, for example, about 300 to 500 kPa. The lubricating oil flowing into the inflow port 5 is supplied to the bearing 27 through a lubricating oil passage 41 formed inside the bearing housing 29. It is preferable to reduce the force acting on the inlet forming surface 9 as much as possible when connecting the outlet 3 of the lubricating oil supply pipe 7 to the inlet 5 of the inlet forming surface 9 while sealing the lubricant from the outside. . This is because the external force acting on the inflow port forming surface 9 adversely affects vibration measurement and becomes an obstacle to highly accurate vibration measurement. Therefore, the outlet 3 and the inlet 5 are connected using the fluid pressure utilization seal 10 described above.

4 is a partially enlarged view of the vicinity of the fluid pressure utilization seal 10 in FIG. The structure and function of the fluid pressure utilization seal 10 in FIG. 4 are the same as those of the fluid pressure utilization seal 10 described above with reference to FIGS. 1 and 2. In FIG. 4, the outer portion 15 of the fluid pressure utilization seal 10 is water-tightly bonded and bonded to the outlet forming surface 4 of the flange 7 a attached to the tip of the lubricating oil supply pipe 7. In this state, the fluid pressure seal 10 attached to the tip of the lubricating oil supply pipe 7 is brought into contact with the inflow port forming surface 9 of the bearing housing 29 in the supercharger 20 fixed to the support 31 with a small force. Let This contact may be made by arranging and fixing the lubricating oil supply pipe 7 to the supercharger 20 using an appropriate instrument / device.
The lubricating oil supplied to the bearing 27 passes through an oil drain passage (not shown) formed inside the bearing housing 29 and passes through an oil drain port 43 provided on the outer surface of the bearing housing 29 to drain the oil pipe 45. To flow. For example, a seal 47 shown in FIG. 3 is provided at a connection portion between the oil discharge port 43 and the oil discharge pipe 45. The seal 47 is made of rubber and is attached to the flange 45 a of the oil drain pipe 45. Since the pressure of the lubricating oil at the oil outlet 43 is small, the oil does not leak to the outside simply by bringing the seal 47 into contact with the outer surface of the bearing housing 29 with a small force. Therefore, the fluid pressure utilization seal 10 does not have to be used for the connection between the oil discharge port 43 and the oil discharge pipe 45.

According to the vibration measurement target rotating machine 20 of the present embodiment described above, the inlet forming surface 9 in which the inlet 5 through which the lubricating oil flows is formed is provided on the stationary side portion (the bearing housing 29 in the example of FIG. 3). In this case, the connection portion between the outlet 3 and the inlet 5 can be sealed with almost no external force acting on the stationary side (that is, the inlet forming surface 9). As a result, the vibration is not attenuated by the external force for sealing the connection portion, so that the vibration characteristics of the rotating machine 20 can be extracted and measured with high accuracy.
Further, since the inlet forming surface 11 and the fluid pressure using seal 10 are merely brought into contact with each other, the structure on the fluid pressure using seal 10 and the lubricating oil supply pipe 7 side can be easily attached to and detached from the inlet forming surface 9.

  The present invention is not limited to the above-described embodiment, and various changes can be made without departing from the scope of the present invention.

[Other Embodiments]
For example, the shape of the fluid pressure utilization seal 10 may be the shape shown in FIG. 5 in addition to the shape shown in FIG. The fluid pressure utilization seal 10 in FIG. 5 is the same as the fluid pressure utilization seal 10 in FIG. 1 except for the points described below.
In FIG. 1, when the fluid pressure utilization seal 10 is also used and the outlet 3 and the inlet 5 are connected, when no fluid pressure is applied to the fluid pressure utilization seal 10, the inner tip of the fluid pressure utilization seal 10. 13 is in surface contact with the inlet forming surface 9.
In the case of FIG. 5, when no fluid pressure is applied to the fluid pressure utilization seal 10 in the connected state, the inner tip 13 of the fluid pressure utilization seal 10 forms an inflow port as shown in FIG. The surface 9 is in contact with a line (drawing a circle). In FIG. 5, as in the case of FIG. 1B, the inner tip 13 has an annular shape when viewed from the central axis C direction of the fluid pressure utilization seal 10, and each of the outer portion 15 and the enlarged portion 17 is The cross-sectional shape is annular. In the case of FIG. 5, when the fluid pressure acts, the fluid pressure utilization seal 10 is elastically deformed as shown in FIG. 5B, and the enlarged portion 17 is pressed against the flow path forming surface by the fluid pressure.

Further, the shape of the fluid pressure utilization seal 10 may be the shape shown in FIG. The fluid pressure utilization seal 10 in FIG. 6 is the same as the fluid pressure utilization seal 10 in FIG. 1 except for the points described below.
In FIG. 1, the vertical cross-sectional shape of the enlarged portion 17 extends linearly from the inner tip 13 to the outer portion 15 in a state where an external force including fluid pressure is not applied to the fluid pressure utilization seal 10.
In the case of FIG. 6, in the state where the external force including the fluid pressure is not applied to the fluid pressure utilization seal 10, the longitudinal section shape of the enlarged portion 17 is changed from the inner tip 13 to the outer portion as shown in FIG. It extends in a curved line up to 15. FIG. 6B shows a state in which fluid pressure is acting on the fluid pressure utilization seal 10 in the configuration of FIG. In FIG. 6, as in the case of FIG. 1B, the inner tip 13 has an annular shape when viewed from the central axis C direction of the fluid pressure utilization seal 10, and each of the outer portion 15 and the enlarged portion 17 is The cross-sectional shape is annular.

Further, the shape of the fluid pressure utilization seal 10 may be the shape shown in FIG. The fluid pressure utilization seal 10 in FIG. 7 is the same as the fluid pressure utilization seal 10 in FIG. 1 except for the points described below.
In the case of FIG. 7, the vertical cross-sectional shape of the enlarged portion 17 is orthogonal to the central axis C, as shown in FIG. 7A, with no external force including fluid pressure acting on the fluid pressure utilization seal 10. Extending from the inner tip 13 to the outer portion 15. In FIG. 7A, the entire enlarged portion 17 is in contact with the inflow port forming surface 9. In the case of FIG. 7, preferably, the outer portion 15 is not elastically deformed, or is formed of a material that is difficult to elastically deform and has high rigidity (for example, metal), and the inner tip 13 and the enlarged portion 17 are easily elastically deformed. It is made of a material (for example, rubber). With this configuration, the entire enlarged portion 17 is pressed against the inflow port formation surface 9 by the fluid pressure and contacts the inflow port formation surface 9 (state shown in FIG. 7B). Also in the case of FIG. 7, the enlarged portion 17 is elastically deformed by the fluid pressure, but this elastic deformation amount is smaller than that in the case of FIG. 1. In the case of FIG. 7, even if fluid pressure acts on the fluid pressure utilization seal 10, the contact area between the fluid pressure utilization seal 10 and the inflow port formation surface 9 is that the fluid pressure acts on the fluid pressure utilization seal 10. It may be the same as the state of FIG. The inner tip 13 and the enlarged portion 17 are integrally formed, and the enlarged portion 17 is water-tightly coupled to the outer portion 15 with an adhesive or the like. In FIG. 7, as in the case of FIG. 1B, the inner tip 13 has an annular shape when viewed from the central axis C direction of the fluid pressure utilization seal 10, and each of the outer portion 15 and the enlarged portion 17 is The cross-sectional shape is annular.

  Further, according to the present invention, the vibration measurement target rotating machine 20 described above may be a rotating machine other than a supercharger (for example, a turbo compressor or a gas turbine).

When the fluid pressure utilization seal 10 of the present invention is used, the outlet forming surface 4 is provided on the pipe 7 in the above-described embodiment. However, according to the present invention, the outlet forming surface 4 is provided on another structure. It may be done.
Similarly, when the fluid pressure utilization seal 10 of the present invention is used, the inflow port 5 may be provided on a device other than the vibration measurement target rotating machine 20. That is, the fluid pressure utilization seal 10 of the present invention is useful when it is not desired to apply an external force to the inflow port forming surface 9 other than the vibration measurement target rotating machine 20.

  According to the present invention, the fluid may be a liquid or a gas.

It is a longitudinal cross-sectional view which shows the structure of the fluid pressure utilization seal | sticker by embodiment of this invention. 1A shows a state in which fluid pressure is acting on the fluid pressure utilization seal. The case where the fluid pressure use seal | sticker of FIG. 1 is used for the vibration measurement object rotary machine is shown. FIG. 4 is a partially enlarged view of the vicinity of a fluid pressure utilization seal in FIG. 3. It is a longitudinal cross-sectional view which shows the structure of the fluid pressure utilization seal | sticker by other embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the fluid pressure utilization seal | sticker by other embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the fluid pressure utilization seal | sticker by other embodiment of this invention. The conventional seal | sticker used for the connection location of an outflow port and inflow is shown.

Explanation of symbols

3 Outlet, 4 Outlet forming surface, 5 Inlet, 7 Pipe (lubricating oil supply pipe), 7a Flange, 9 Inlet forming surface, 10 Fluid pressure seal, 11 Fluid passage area, 13 Inner tip, 15 Outer part , 17 Enlarged part, 20 Vibration measurement target rotating machine (supercharger), 21 Turbine blade (rotating body), 23 Compressor blade (rotating body), 24 Rotating shaft (rotating body), 25 Turbine housing (stationary side part), 27 Bearing, 28 Bolt, 29 Bearing housing (stationary side), 31 Support, 33 Accelerometer, 35 Rotation angle detector, 37 Calculator, 39 Nut, 41 Lubricating oil passage, 43 Oil outlet, 45 Oil exhaust pipe, 45a flange, 47 seal,

Claims (5)

A fluid pressure-use seal for a vibration measuring target rotating machine, which is used when the rotating body of a rotating machine is driven to rotate and the vibration of the rotating machine is measured with a pickup attached to the stationary side of the rotating machine. ,
The rotating machine includes the rotating body that is rotationally driven, and the stationary side portion that supports the rotating body via a bearing,
The fluid pressure utilization seal is provided between an outlet forming surface in which an outlet from which lubricating oil flows out is formed and an inlet forming surface in which an inlet through which lubricating oil flows from the outlet is formed, The lubricating oil flowing into the inflow port is supplied to the bearing,
The outlet forming surface is located at a tip of a lubricating oil supply pipe, and the inlet forming surface is an outer surface of the stationary side portion;
The fluid pressure utilization seal so as to surround the fluid passage region from the outlet to the inlet, mounted on said outlet opening forming surface,
The fluid pressure utilization seal includes an inner tip that is in contact with the inlet forming surface and surrounds the inlet, and an outer tip that is located away from the inner tip in a direction from the inlet center toward the inlet outer peripheral edge and surrounds the fluid passage region. And an enlarged portion extending from the inner tip to the outer portion and surrounding a fluid passage region,
For the rotary machine subject to vibration measurement, wherein the enlarged portion is pressed against the inlet forming surface by the pressure of the lubricating oil in the fluid passage region, so that the fluid passage region is sealed against the outside . Fluid pressure seal. 2. The vibration measurement target rotation according to claim 1, wherein the inner front end has an annular shape as viewed from the direction of the central axis of the fluid pressure utilization seal extending from the outflow port toward the inflow port. Fluid pressure seal for machinery. 3. The vibration according to claim 1, wherein the fluid pressure utilization seal is elastically deformed by the pressure of the lubricating oil in a fluid passage region, whereby the enlarged portion is pressed against the inflow port forming surface. 4. Fluid pressure seal for the rotating machine to be measured . The cross-sectional shape of the enlarged portion by a plane including the central axis of the fluid pressure utilization seal extends from the inflow port forming surface to the outer side portion in a direction inclined from the central axis toward the outlet side. The fluid pressure utilization seal for a vibration measuring object rotary machine according to claim 2, wherein The fluid pressure-use seal according to any one of claims 1 to 4, wherein the vibration measurement target rotating machine is a vibration measurement target,
And the rotating body which is driven to rotate,
Vibration measurement target rotary machine this and the stationary side of the rotating body is supported via a bearing, Ru provided with, it is characterized.

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