JPH0315137B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a small and lightweight thrust load measuring device for accurately measuring the thrust load acting on a bearing.

[Prior Art] For example, when an excessive thrust load is applied to a bearing portion of a rotating machine such as an aircraft engine, a gas turbine, or an axial flow compressor, not only the bearing is damaged but also the entire machine is affected. For this reason,
Accidents can be prevented and safety can be improved by measuring this thrust load and taking measures according to the value to bring the bearing to its original normal load state.

Therefore, various devices for measuring thrust loads have been studied.

[Problems to be solved by the invention] However, since the area around the bearing is generally located in a narrow area and the atmosphere is immersed in high temperature oil, it is considered difficult to install a thrust load measuring device in this area. Moreover, a mechanism for detecting thrust load and a device equipped with the mechanism may be large in size, making it difficult to put them into practical use. Conventionally, operations were performed without a thrust load measuring device, disassembled after operation, and inspections of the degree of damage to bearings, etc. were determined based on guesswork and experience. It was a sloppy operation, which was the biggest safety defect.

In view of the above-mentioned circumstances, the present invention has been made with the object of making it possible to quickly and accurately measure the thrust load acting on a bearing by installing a small and lightweight thrust load measuring device around the bearing. be.

[Means for Solving the Problems] The present invention provides a bearing support member disposed with a slight gap on the side of a flange fixed to the outer periphery of a bearing outer race fitted to a rotatable shaft; A cantilever-like or both-end supported beam-like load conversion member arranged at approximately equal intervals in the circumferential direction of the bearing support member and having strain gauges attached thereto, and a load conversion member that converts the thrust load acting on the bearing through the flange. A member for transmitting the load to the member, and a member attached to the bearing support member to support the tangential force due to the drag torque acting in the circumferential direction of the flange, and the thickness of the shaft in the axial direction is at least partially thinned. The structure includes a drag prevention fitting and a transmission member that transmits a tangential force due to a drag torque acting on the flange to the drag prevention fitting.

[Operation] The thrust load is transmitted from the shaft to the bearing, the flange of the bearing outer race, the thrust load transmission member to the load conversion member, and by displacing the load conversion member, it is detected by a strain gauge and taken out to the outside. The tangential force due to the twisting torque that occurs as the shaft rotates is supported by the drag-preventing fitting.

[Examples] Examples of the present invention will be described below with reference to the accompanying drawings.

1 to 4 show a first embodiment of the present invention, in which an inner race 3 of a bearing 2 is attached to a rotatable shaft 1.
An outer race 5 is fitted to the outer periphery of the inner race 3 via balls 4, and a flange 6 is fixed to the outer periphery of the outer race 5. Also inner lace 3
is fastened to the shaft 1 by a tightening nut 7.

A hollow cylindrical bearing support member 8 fixed to a casing (not shown) is disposed on the side of the flange 6 so that a required gap G ₁ is maintained between the bearing support member 8 and the flange 6. A plurality of load conversion members 9 arranged at substantially equal intervals in the circumferential direction are fixed in a cantilever shape by a plurality of fixing bolts 10 on the side opposite to the flange 6 of the load conversion member 9. Strain gauges 11 or 11' are attached to the upper and lower concave portions of the strain-generating portion 9a of the beam portion or to the inner surface of the circular hole portion as required.

A plurality of bolts 12 for thrust load transmission are installed at approximately equal intervals in the circumferential direction of the flange 6 so as to pass through the flange 6 in the longitudinal direction of the shaft 1. It penetrates through and its tip is fixed to the tip of the cantilever-shaped portion of the load converting member 9. The outer diameter of the bearing support member 8 penetrating portion of the bolt 12 is slightly smaller than the inner diameter of the through hole 13, and a gap G ₂ is maintained between the bolt 12 and the inner circumference of the through hole 13, and the outer diameter of the flange 6 penetrating portion and load conversion. The diameter of the member 9 is larger than the outer diameter of the penetration portion, and the step portions at both ends of the large diameter portion abut against the side of the flange 6 and the side of the load conversion member 9, respectively, and the bearing 2 receives a thrust load, causing the flange 6 to deform. In this case, the thrust load is not transmitted to the bearing support member 8 and the bolt 12
The load is transmitted to the load converting member 9 via.

In the circumferential direction of the flange 6, a load conversion member 9,
A bolt 14 is installed between the bolts 9 and 9 and is attached so as to pass through the flange 6. The bolt 14 passes through a through hole 18 in the bearing support member 8, and its tip protrudes into a recess 15 provided in the bearing support member 8. There is. Further, both ends of the anti-tangling fitting 17 are fixed to the recess 15 by fixing bolts 16, and the tip of the bolt 14 is fixed to the center of the anti-tangling fitting 17. The center of support is a concentrated load beam. The outer diameter of the bolt 14 through the bearing support member 8 is smaller than the inner diameter of the through hole 18, and a gap G ₃ is maintained between the bolt 14 and the inner circumference of the through hole 18. The diameter is larger than the outer diameter of the penetration part, and the step portions at both ends of the large diameter part abut the sides of the flange 6 and the sides of the anti-slip fitting 17, respectively, and the bearing 2 receives a thrust load, causing the flange 6 to deform. In this case, the thrust load is not transmitted to the bearing support member 8 and is transferred to the anti-tangling fitting 1 via the bolt 14.
7. The anti-entanglement fitting 17 has a thin plate structure in which the thickness in the axial direction of the shaft 1 is at least partially thin, and is easily displaced with an extremely small force when a thrust load shown in the Y direction in FIG. 1 is applied. The tensile and compressive stiffnesses are designed to be large against the tangential force due to the drag torque acting in the X direction in FIG.

The thrust load generated on the shaft 1 is transmitted from the shaft 1 to the bearing 2 as a distributed load, and from the bearing 2 via the flange 6 and bolt 12 to the load point P of the load conversion member 9.
is transmitted from the strain-generating portion 9a of the load converting member 9 to the fixing bolt 10, and from the fixing bolt 10 to the bearing support member 8, where it is supported.

In the above-mentioned thrust load transmission process, the strain gauge 11 is displaced by the thrust load acting on the load conversion member 9, and this displacement is converted into an electric signal proportional to the magnitude of the thrust load and converted into an external force by a lead wire. It is extracted as an equivalent amount of information. The distributed loads acting on each load conversion member 9 are detected from the extracted electrical signals, and the average value thereof is displayed and recorded as a thrust load. If the thrust load acting on the shaft 1 is in the opposite direction, it is detected as a negative output. Since the gap _G1 between the flange 6 and the bearing support member 8 is larger than the displacement of the load point P of the load conversion member 9, the flange 6 is
There is no contact between the bearing support member 8 and the bearing support member 8, so there is no problem in measuring the thrust load.

As the shaft 1 rotates, rotational torque is generated in the flange 6 of the bearing 2 in the X direction (tangential direction) in FIG. In this case, if there is no drag prevention fitting 17, the relative positions of the flange 6 and the bearing support member 8 in the circumferential direction will change, and the portion of the bolt 12 that passes through the bearing support member 8 will come into contact with the inner periphery of the through hole 13, causing the bolt This may increase the frictional force between the through hole 12 and the through hole 13 and reduce the measurement accuracy of the thrust load. However, in the present invention, the tangle prevention fitting 17
is provided, and the anti-tangling fitting 17 resists the tangential force due to the tangling torque in the direction of the load along the tensile and compressive load axes, so the tensile and compressive rigidity becomes large and is sufficient to withstand the tangential force. A reaction force is generated that opposes the tangential displacement, and the displacement in the tangential direction can be suppressed to a small degree. Further, the anti-dangle fitting 17 is displaced by an extremely small reaction force against a thrust load. Therefore, more than 90% of the thrust load is transmitted to the load conversion member 9.

5 to 8 show a second embodiment of the present invention. In the previous embodiment, the load conversion member 9 and the strain gauge 11 were installed outside the bearing support member 8.
In this embodiment, a recess 19 is provided in the bearing support member 8,
The load conversion member 9 to which the strain gauge 11 is attached is housed in the recess 19, and the recess 19 is hermetically sealed with a lid 20. In the figure, 21 is a bolt that fixes the lid 20 to the bearing support member 8. With such a configuration, it becomes possible to protect the load conversion member 9 and the strain gauge 11 from direct attack of lubricating oil and mist.

9 and 10 show a third embodiment of the present invention,
In the first and second embodiments, the load converting member 9 had a cantilever shape, whereas in this embodiment, the load converting member 9 has a beam shape with both ends supported, so that a concentrated load acts on the center. There is. With such a configuration, it is possible to detect a thrust load larger than that in the first and second embodiments, and it is possible to detect twice as much load.

FIGS. 11 and 12 show a fourth embodiment of the present invention, in which a load conversion member 9 is shaped like a support beam at both ends, a recess 19 is provided in the bearing support member 8, and a strain gauge 11 is attached to the recess 19 at both ends. A support beam-shaped load conversion member 9 is housed, and the recess 19 is sealed with a lid 20. With such a configuration, it is possible to measure a large thrust load, and it is also possible to protect the load conversion member 9 and strain gauge 11 from direct attack by lubricating oil and mist.

Components in FIGS. 5 to 12 that are the same as those shown in FIGS. 1 to 4 are given the same reference numerals.

It should be noted that the present invention is not limited to the above-described embodiments, and it goes without saying that various changes can be made without departing from the gist of the present invention.

[Effects of the Invention] According to the bearing thrust load measuring device of the present invention, the thrust load can be measured by immersion in high-temperature oil, vibration,
Even repeated forces such as sudden loads and sudden releases are quickly and reliably transmitted to the load conversion member, allowing for highly accurate load detection.〈〉The load conversion member is attached to the bearing support member, Since there is no need for special parts for attaching the load converting member, the entire device becomes smaller and lighter. , which can improve the safety of the equipment, 〈〉 Prevents damage to the bearing, reduces the burden on other mechanical parts, and stabilizes the area around the bearing, making it possible to detect other abnormalities early. 〈〉 Strain gauges The attached load conversion member can be used repeatedly and is interchangeable, so it is easy to manufacture.〈〉Since the entire device can be handled as one unit, it is easy to inspect the malfunctioning part and check the load. Various excellent effects can be achieved, such as the ability to easily replace the conversion member.

[Brief explanation of the drawing]

FIG. 1 is an explanatory diagram of the first embodiment of the bearing thrust load measuring device of the present invention, and FIG. 2 is a diagram showing the − of FIG.
3 is a view taken in the negative direction of FIG. 2, FIG. 4 is a view taken in the negative direction of FIG. 2, and FIG. 5 is a second implementation of the bearing thrust load measuring device of the present invention. An explanatory diagram of an example, FIG. 6 is a view taken in the - direction arrow of FIG. 5, FIG. 7 is a view taken in the - direction arrow of FIG. 6, FIG. 8 is a view taken in the - direction arrow of FIG. 6, and FIG. 10 is an explanatory diagram of the third embodiment of the bearing thrust load measuring device of the present invention, FIG.
Figure 1 is an explanatory diagram of the fourth embodiment of the bearing thrust load measuring device of the present invention, and Figure 12 is an illustration of XII-XII of Figure 11.
It is a directional view. In the figure, 1 is a shaft, 2 is a bearing, 6 is a flange, 8 is a bearing support member, 9 is a load conversion member, 11, 11' are strain gauges, 13 is a through hole, 14 is a bolt, 17 is an anti-entanglement fitting, 18 indicates a through hole.

Claims (1)

[Claims] 1. A bearing support member disposed at a slight gap on the side of a flange fixed to the outer periphery of a bearing outer race fitted to a rotatable shaft, and a bearing support member disposed at approximately equal intervals in the circumferential direction of the bearing support member. a load converting member in the form of a cantilever beam or a beam supported at both ends to which a strain gauge is attached; a load transmitting member that transmits the thrust load acting on the bearing to the load converting member via the flange; a drag prevention fitting that is attached to the bearing support member and has at least partially reduced thickness in the axial direction of the shaft to support the tangential force due to drag torque acting in the circumferential direction; and a drag prevention fitting that acts on the flange. A thrust load measuring device for a bearing, characterized in that it is provided with a transmission member that transmits tangential force due to torque to an anti-entanglement fitting.