JP2001295610A - Non-rotating nut structure - Google Patents

Abstract

(57) Abstract: A bearing fixed to a shaft with a nut and a detent member can be reliably lubricated with oil supplied from an oil jet provided on the opposite side of the bearing with respect to the nut. A bearing (13) for rotatably supporting a shaft (12) on a case (14) is attached to the shaft (12) by a nut (20).
And the nut 20 is non-rotatably restrained to the shaft 12 by the rotation preventing member 22. The oil jetted from the nozzle 27a of the oil jet 24 is supplied to the bearing 13 from an oil reservoir 30 formed inside the detent member 22 via an oil hole 20g that passes through the nut 20 in the axial direction. Therefore, oil can be reliably supplied to the bearing 13 without being obstructed by the nut 20 interposed between the nozzle 27a and the bearing 13 and without forming an oil hole in the hollow shaft 12.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a nut which is screwed to an outer periphery of a shaft for fixing a bearing fitted to the outer periphery of the shaft in an axial direction by a detent member which is fitted to the outer periphery of the shaft. The present invention relates to a nut rotation preventing structure.

[0002]

2. Description of the Related Art When a shaft is rotatably supported on a casing via a bearing, an oil passage extending in the axial direction inside the shaft and an oil branched from the oil passage in a radial direction and opening on the outer surface of the shaft. A method of supplying oil to a bearing through a road is known. In addition, when an oil path cannot be formed inside the shaft, a method of directly ejecting oil from an oil jet toward a bearing is also known.

[0003]

By the way, when the latter method is adopted, when the position where the oil jet is provided cannot be freely selected, the nut for fixing the bearing to the shaft hinders the oil from the oil jet. A situation occurs in which the bearing cannot be supplied effectively.

[0004] The present invention has been made in view of the above circumstances, and a bearing fixed to a shaft by a nut and a detent member is provided by oil supplied from an oil jet provided on the opposite side of the bearing with the nut interposed therebetween. The purpose is to ensure lubrication.

[0005]

In order to achieve the above object, according to the first aspect of the present invention, a screw which is fitted on the outer periphery of a shaft is screwed around the outer periphery of the shaft to fix the bearing in the axial direction. In a nut detent structure in which a mating nut is detented by a detent member fitted to the outer periphery of the shaft, the detent member has a first engagement projection and a second engagement projection, and the first engagement projection is The nut is relatively non-rotatably engaged with the first engaged groove formed on the nut, and the second engagement projection is engaged with the second engaged groove formed on the shaft so as not to rotate relatively. An oil reservoir that is non-rotatably restrained by the shaft via the stopper member and that holds the oil ejected from the nozzle of the oil jet in a direction between the detent member and the shaft is formed inside the detent member,
A plurality of oil holes penetrating the nut in the axial direction, wherein an inlet end is opened to communicate with the oil reservoir, and an outlet end is opened to communicate with the bearing; A structure is proposed.

According to the above configuration, even if a nut is interposed between the oil jet and the bearing to be lubricated, the oil ejected from the nozzle of the oil jet can be guided to the bearing through the oil hole formed in the nut. Thus, the bearing can be sufficiently lubricated even during high-speed rotation of the shaft. Further, since the inlet end of the oil hole of the nut is opened in the oil reservoir formed inside the detent member, the oil can be supplied to the bearing without waste and without interruption. Also, since there is no need to form an oil hole inside the shaft, it can be applied to hollow shafts where it is difficult to form an oil hole. Therefore, there is no danger that the oil hole of the nut will be crushed by the load during crimping and the supply of oil will be hindered.

[0007]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described based on embodiments of the present invention shown in the accompanying drawings.

1 to 5 show an embodiment of the present invention. FIG. 1 is a longitudinal sectional view of a main part of a gas turbine engine, and FIG.
3 is a sectional view taken along line 2-2 of FIG. 1, FIG. 3 is a sectional view taken along line 3-3 of FIG. 1, FIG. 4 is a perspective view of a nut and a detent member, and FIG. 5 is a perspective view of a nut and a nut runner.

FIG. 1 shows a part of a gas turbine engine, and a hollow inner shaft 1 for supporting a low-pressure turbine blade and a low-pressure compressor blade (not shown).
1 and a hollow outer shaft 12 supporting a high-pressure turbine blade and a high-pressure compressor blade (not shown)
Are arranged coaxially, and the shaft end of the outer shaft 12 is supported by a bearing housing 14 via a roller bearing 13. The roller bearing 13 is used for the inner race 1 fitted on the outer peripheral surface of the outer shaft 12.
5, an outer race 16 fitted on the inner peripheral surface of the bearing housing 14, a number of rollers 17 arranged between the inner race 15 and the outer race 16, and a retainer 18 for preventing the rollers 17 from falling off. Be composed.

A male screw 1 is provided on the outer periphery of the outer shaft 12.
2a are formed, and the nut 20 is attached to the male screw 12a.
The female screw 20a formed on the inner periphery of is screwed. Nut 20
Presses the inner race 15 of the roller bearing 13 leftward in the figure, and presses the inner race 15 against the rear coupling 21 fitted on the outer periphery of the outer shaft 12 to fix the inner race 15 in the axial direction. And the outer shaft 12
The nut 20 screwed into the outer shaft 12 is stopped by a detent member 22 fitted on the outer periphery of the outer shaft 12.

2 to 4, the main body 20b of the nut 20 having the female thread 20a formed on the inner peripheral surface thereof is brought into contact with the inner race 15 at the front end (left side in FIG. 1). An annular pressing surface 20c is formed so as to be in contact therewith, and nine protrusions 20d on the outer periphery and nine first engaged grooves 20e are alternately formed in the circumferential direction. The nine first engaged grooves 20e extend in the axial direction, and the interval between them is constant and all are 40 °. Clip grooves 20f are formed on the inner peripheral surfaces of the protrusions 20d, respectively. The female screw 20 of the nut 20
Many oil holes 20g penetrate in the axial direction so as to surround the outside of a.

An annular detent member 22 fitted on the outer periphery of the outer shaft 12 includes an annular projection 22b projecting radially outward from an axially intermediate portion of an outer peripheral surface of a cylindrical main body 22a, and an annular projection 22b of the main body 22a. An annular projection 22c protruding radially inward from the rear end (the right side in FIG. 1) of the inner peripheral surface;
A step portion 22d formed on a front inner peripheral surface of the main body portion 22a,
Flange 2 extending radially outward from the front of step 22d
2e, three first engagement projections 22f projecting forward from a radially outer end of the flange 22e, and two second engagement projections projecting radially inward from an axially intermediate portion of the inner peripheral surface of the main body 22a. 2g projections 22g, 22g. The three first engagement protrusions 22f are formed at 120 ° intervals, and the two second
The engagement projections 22g, 22g are formed at 180 ° intervals.
45 ° behind the male screw 12a of the outer shaft 12
Eight second engaged grooves 12b are formed at an interval in the axial direction, and further behind these second engaged grooves 12b are 180
Two notches 12c, 12c are formed at intervals of °.

The oil jet 24 supported by the bearing housing 14 has a nozzle member 27 fixed by a bolt 26 below a support arm 25 projecting downward from the bearing housing 14, and is connected to an oil pump 28. An oil passage 25 a extending downward inside the support arm 25 communicates with a nozzle 27 a formed obliquely on the nozzle member 27. The contact portion between the support arm 25 and the nozzle member 27 is sealed by two seal members 29, 29. The nozzle 27
a is the outer peripheral surface of the outer shaft 12 and the detent member 22
Of the annular projection 22c is directed toward the tip of the annular projection 22c, and in front of the gap α, an annular shape surrounded by the main body portion 22a and the annular projection 22c of the detent member 22 and the outer peripheral surface of the outer shaft 12. An oil reservoir 30 is formed.

Oil hole 2 axially penetrating nut 20
0g... Communicates with the oil reservoir 30 and the front end communicates with a plurality of oil grooves 15a formed in the inner peripheral surface of the inner race 15 of the roller bearing 13 in the axial direction. A plurality of oil holes 15b extending radially from the oil grooves 15a communicate with the vicinity of the rollers 17.

Next, the operation of the embodiment of the present invention having the above configuration will be described.

In order to press and fix the roller bearing 13 fitted on the outer periphery of the outer shaft 12 to the left, the female screw 20a of the nut 20 is screwed to the male screw 12a of the outer shaft 12 using a nut runner 31 shown in FIG. I do. The socket 32 of the nut runner 31 is formed with nine projections 32 a. These projections 32 a are engaged with the nine first engagement grooves 20 e of the nut 20, so that the nut 20 is The roller bearing 13 can be fastened by rotating. Subsequently, the phases of the two second engagement projections 22g, 22g of the rotation preventing member 22 are changed to the two notches 12c, 12c at the shaft end of the outer shaft 12.
In this state, the rotation preventing member 22 is moved in the axial direction and fitted from the shaft end of the outer shaft 12.

Subsequently, the three first engagement protrusions 22f of the rotation preventing member 22 are connected to the nine first engagement grooves 20 of the nut 20.
e, and at the same time, the two second engaging projections 22g, 22g of the rotation preventing member 22 are engaged with the eight second engaged grooves 12b of the outer shaft 12. 2
Engage with book. Then, the clip 23 is compressed and engaged with the clip groove 20f of the nut 20 from the inside in the radial direction, and the rotation preventing member 22 is locked so as not to fall off the nut 20.

In the state in which the rotation is stopped, the two second engagement protrusions 22g of the rotation prevention member 22 are connected to two of the eight second engagement grooves 12b of the outer shaft 12. To the outer shaft 12
The rotation of the detent member 22 is restricted, and the three first engaging projections 22f of the detent member 22 are opposed to three of the nine first engaged grooves 20e of the nut 20. The rotation preventing member 22 engages with the rotation preventing member 22 so that the rotation of the nut 20 with respect to the rotation preventing member 22 is restricted. As a result, the nut 20 with respect to the outer shaft 12 is
Of the nut 20 is reliably prevented from loosening due to vibration or the like.

As described above, when the rotation of the nut 20 is stopped using the rotation stopping member 22, the rotation stopping member 22
It is not necessary to caulk the nut, and it is only necessary to lock the detent member 22 to the nut 20 with the clip 23. Therefore, the crimping operation of the detent member 22 after the nut 20 is screwed or the nut 20 once tightened In addition, the work of separating the swaged portion when loosening is not required, and not only the workability is greatly improved, but also the detent member 22 can be used repeatedly, thereby improving the economic efficiency. When the clip 23 is removed to separate the rotation preventing member 22 from the nut 20,
A tool is engaged with an annular projection 22b protruding from the outer periphery of the main body 22a of the rotation preventing member 22, and the outer shaft 12
Can be pulled out toward the shaft end.

The coupling phase between the nut 20 and the rotation-stopping member 22 is 360 °.
Can be adjusted at a pitch of 40 ° divided by 9, which is the number of the rotation stopper members 22 and the outer shaft 1
2 is 360 ° at the second phase of the outer shaft 12.
Since the pitch can be adjusted at a pitch of 45 ° divided by 8, which is the number of the engaged grooves 12b, the difference between 40 ° and 45 ° is 5
The amount of tightening of the nut 20 with respect to the outer shaft 12 can be finely adjusted at intervals of °.

The reason is that the first engaged groove 2 of the nut 20
0e... The first engagement protrusion 22f of the detent member 22
Are shifted in the left-right direction by 40 ° (that is, one pitch of the nine first engaged grooves 20e of the nut 20), the second engagement protrusions 22 of the rotation preventing member 22 are assumed.
The engagement of the second engaged grooves 12b... of the outer shaft 12 with the g, 22g is 45 ° (8 of the outer shaft 12).
Can be adjusted only at intervals of one pitch of the second engaged grooves 12b.
Is impossible to wear. Then, if the nut 20 and the detent member 22 integrally engaged with the nut 20 are rotated in the left-right direction by 5 °, the two second engagement projections 22 g of the detent member 22 become eight of the outer shaft 12. Are engaged with two of the second engaged grooves 12b, so that the rotation preventing member 22 can be mounted.

As described above, the phase adjustment pitch between the nut 20 and the detent member 22 (40 ° in the embodiment) and the phase adjustment pitch between the detent member 22 and the outer shaft 12 (45 ° in the embodiment) By making them different, the detent member 22 can be mounted without hindrance while finely adjusting the tightening amount of the nut 20 to the outer shaft 12 at intervals of 5 ° corresponding to the difference between the two pitches.

In short, the phase adjustment pitch between the nut 20 and the detent member 22 is P1 (40 ° in the embodiment), and the phase adjustment pitch between the detent member 22 and the outer shaft 12 is P2 (45 ° in the embodiment). When the difference between the pitch P1 and the pitch P2 is set to be smaller than the smaller one of the pitch P1 and the pitch P2, the tightening amount of the nut 20 with respect to the outer shaft 12 can be finely adjusted. Can be.
In the embodiment, the difference between the pitch P1 and the pitch P2 is 5 °.
Is the smaller of the pitch P1 and the pitch P2, the pitch P
Since it is set smaller than 1 (40 °), fine adjustment can be made at 5 ° intervals.

In the embodiment, the number of the second engaged grooves 12b of the eight outer shafts 12 is reduced to four,
When the phase adjustment pitch P2 between the detent member 22 and the outer shaft 12 is changed from 45 ° to 90 °, the difference between the pitch P1 and the pitch P2 is 50 ° and is smaller than the smaller pitch P1 (40 °). The phase adjustment pitch that was originally possible, that is, the phase adjustment pitch between the nut 20 and the rotation preventing member 22 is P1 (40
°) cannot be further reduced.

Now, in order to lubricate the roller bearings 13 that support the outer shaft 12 on the bearing housing 14, the oil supplied from the oil pump 28 to the oil jet 24 passes through the oil passage 25 a of the support arm 25 and the nozzle member 27. The oil is ejected from the nozzle 27 a and is supplied to the oil reservoir 30 through a gap α between the outer peripheral surface of the outer shaft 12 and the tip of the annular protrusion 22 c of the rotation preventing member 22.
The oil accumulated in the oil reservoir 30 is supplied from the oil holes 20g of the nut 20 to the rollers 17 via the oil grooves 15a of the inner race 15 of the roller bearing 13 and the oil holes 15b to provide lubrication of the roller bearing 13. Is done.

As described above, since the nut 20 is interposed between the roller bearing 13 to be lubricated and the oil jet cannot be supplied directly from the oil jet 24 to the roller bearing 13, the oil is supplied through the oil hole 20 g of the nut 20. Supply of oil to the outer shaft 12
The roller bearing 13 can be sufficiently lubricated even during the high-speed rotation of the roller bearing 13. This is particularly effective when the outer shaft 12 with which the nut 20 is screwed is a hollow shaft and an oil passage for supplying oil cannot be formed therein, as in the present embodiment.

Since the oil reservoir 30 faces the inlet of the oil hole 20g of the nut 20, the oil ejected from the nozzle 27a of the nozzle member 27 can be supplied to the roller bearing 13 without waste and without interruption. . In addition, since the swaging process is not required by employing the rotation preventing member 22 having the above configuration, there is no possibility that the oil holes 20g of the nut 20 are crushed by the load of the swaging process and the supply of the oil is hindered.

Although the embodiment of the present invention has been described in detail, various design changes can be made in the present invention without departing from the gist thereof.

For example, the detent structure of the present invention can be applied to any application other than a gas turbine engine. Also, the number of the first engaged grooves 20e of the nut 20, the number of the second engaged grooves 12b of the outer shaft 12, the first engaging projections 22f and the second engaging projections 22g of the rotation preventing member 22. Is not limited to the embodiment and can be changed as appropriate.

[0030]

As described above, according to the first aspect of the present invention, even if a nut is interposed between the oil jet and the bearing to be lubricated, the oil ejected from the nozzle of the oil jet is supplied to the nut. The bearing can be guided to the bearing through the oil hole formed in the shaft, and the bearing can be sufficiently lubricated even at the time of high-speed rotation of the shaft.
Further, since the inlet end of the oil hole of the nut is opened in the oil reservoir formed inside the detent member, the oil can be supplied to the bearing without waste and without interruption. Also, since there is no need to form an oil hole inside the shaft, it can be applied to hollow shafts where it is difficult to form an oil hole. Therefore, there is no danger that the oil hole of the nut will be crushed by the load during crimping and the supply of oil will be hindered.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a main part of a gas turbine engine.

FIG. 2 is a sectional view taken along line 2-2 of FIG.

FIG. 3 is a sectional view taken along line 3-3 in FIG. 1;

FIG. 4 is a perspective view of a nut and a detent member.

FIG. 5 is a perspective view of a nut and a nut runner.

[Explanation of symbols]

 Reference Signs List 12 outer shaft (shaft) 12b second engaged groove 20 nut 20e first engaged groove 20g oil hole 22 detent member 20f first engagement protrusion 20g second engagement protrusion 24 oil jet 27a nozzle 30 oil reservoir α Gap

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) F16B 39/10 F16B 39/10 D

Claims (1)

[Claims] 1. A shaft (1) for fixing a bearing (13) fitted on an outer periphery of a shaft (12) in an axial direction.
The nut (20) screwed to the outer periphery of 2) is attached to the shaft (1).
In the nut rotation preventing structure in which the rotation preventing member (22) fitted on the outer periphery of (2) is used to prevent the rotation, the rotation preventing member (22) is provided with the first engagement protrusion (22f) and the second engagement protrusion (22g). The first engagement protrusion (22
f) is a first engaged groove (20) formed in the nut (20).
e) and the second engagement protrusion (22)
g) is a second engaged groove (12) formed in the shaft (12).
b), the nut (2)
0) is a shaft (12) via a detent member (22).
The nozzle (2) of the oil jet (24) is directed toward the gap (α) between the rotation preventing member (22) and the shaft (12).
An oil reservoir (30) for holding oil spouting from 7a)
Is formed inside the detent member (22), and the nut (2
0) is opened so as to communicate with the oil sump (30), and the outlet end is opened so as to communicate with the bearing (13). A non-rotating structure for nuts.