JP2014009744A - Lubricant path structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To sufficiently supply oil to the depth of a main oil hole by rotation of a rotating shaft itself.SOLUTION: A lubricant path structure is provided in which a main oil hole 2 extending in an axial direction, and oil outlet holes 3A-3D radially extended and communicated with the main oil hole 2, are formed on a rotating shaft 1, an oil supply pipe 10 rotated integrally with the rotating shaft 1 is fitted in the main oil hole 2, communication holes 11A-11D communicating between the inside of the oil supply pipe 10 and the oil outlet holes 3A-3D are formed on the oil supply pipe 10, and a spiral guide groove 20 for flowing the oil supplied from one end side of the main oil hole 2 toward the other end side of the main oil hole 2 by being affected by inertia force in a tangential direction generated according to the rotation of the rotating shaft 1, is formed on an inner face of the oil supply pipe 10.

Description

  The present invention relates to a lubricating oil passage structure.

  As a lubricating oil passage structure using a rotating shaft, there is one in which a main oil hole extending in the axial direction is formed on the rotating shaft, and an oil outlet hole extending in the radial direction and communicated with the main oil hole is formed. In this case, the oil supplied to the main oil hole from one end side of the main oil hole is supplied through the oil outlet hole. When the rotating shaft is used for a transmission, for example, the oil outlet hole is formed at a position corresponding to, for example, a supporting portion (sliding portion) of the rotating shaft or various gear portions. Oil can be supplied to the part.

  Oil supply to the main oil hole is performed by oil pumping by an oil pump, and it is desired to reduce the oil pumping pressure as much as possible. Patent Document 1 discloses a lubricating oil passage structure in particular in a motorcycle transmission in which a long operation rod for engaging and disengaging a clutch mechanism is inserted into a main oil hole. Specifically, in Patent Document 1, in consideration of the fact that oil flows into the gap between the rotating shaft and the operating rod, a spiral ridge is formed on the outer periphery of the operating rod or the inner periphery of the main oil hole. Thus, there has been disclosed a structure in which oil is caused to flow to the back side of the main oil hole by a protruding line when the rotation shaft and the operation rod are relatively rotated.

JP-A-1-238769

  The thing of the said patent document 1 is what gets the function of a kind of screw type pumping mechanism by a protruding item | line when a rotating shaft and an operation rod rotate relatively, In this case, in a rotating shaft, On the other hand, an operation rod that is relatively rotated is required. However, for example, as represented by a general automobile transmission, in most cases, there is no long operation rod in the main oil hole of the rotating shaft, and the technique disclosed in Patent Document 1 cannot be used. It is. In addition, as described in Patent Document 1, it is practically extremely difficult to form a ridge on the inner peripheral surface of the main oil hole due to a problem in processing the rotating shaft.

  The present invention has been made in view of the above circumstances, and its purpose is to effectively rotate the rotating shaft even when there is no long non-rotating member such as an operating rod in the main oil hole. And to provide a lubricating oil passage structure that can sufficiently supply oil deep into the main oil hole.

In order to achieve the above object, the following solution is adopted in the present invention. That is, as described in claim 1,
A main oil hole extending in the axial direction and an oil outlet hole extending in the radial direction and communicating with the main oil hole are formed in the rotation shaft,
In the lubricating oil passage structure in which the oil supplied from one end side of the main oil hole into the main oil hole is discharged to the radially outer side of the rotating shaft through the oil outlet hole,
In the main oil hole, an oil supply pipe is fitted so as to rotate integrally with the rotary shaft,
A communication hole is formed in the oil supply pipe to communicate the oil supply pipe with the oil outlet hole.
A spiral guide groove is formed on the inner surface of the oil supply pipe to allow oil supplied from one end side of the main oil hole to flow toward the other end side of the main oil hole in accordance with the rotation of the rotating shaft. Being
It is like that.

  According to the above solution, the oil supply pipe is also rotated integrally with the rotation of the rotating shaft. The oil supplied into the oil supply pipe is pressed against the inner peripheral surface side of the oil supply pipe by the centrifugal force accompanying the rotation, and is sufficiently supplied into the spiral guide groove. And the oil in a guide groove will be guide | induced to the back | inner side of a main oil hole along a guide groove by the influence of the inertial force to a tangential direction accompanying rotation of a rotating shaft. In addition, since the spiral guide groove is formed in the oil supply pipe formed separately from the rotating shaft, it is processed as compared with the case where the guide groove is formed on the inner peripheral surface of the rotating shaft. This is much more advantageous in terms of cost and cost, and there is no problem in practical use.

A preferred mode based on the above solution is as described in claim 2 and the following. That is,
The guide groove is formed so as to pass through the communication hole (corresponding to claim 2). In this case, the oil is directly supplied from the guide groove to the oil outlet hole, which is preferable in order to achieve the effect corresponding to claim 1 more fully.

  The oil supply pipe is configured by joining half members having a substantially semicircular cross section divided into two in the radial direction (corresponding to claim 3). In this case, the guide groove can be easily formed as compared with the case where the spiral guide groove is formed on the inner peripheral surface of the annular (cylindrical) member.

The two half members are connected to each other by a hinge,
Of the two halved members, a locking portion is formed on one half member, and a locked portion on which the locking portion is locked is formed on the other half member.
The locking portion is locked to the locked portion in a state where the oil supply pipe having a substantially circular cross section is formed by overlapping the two halved members by rotation around the hinge. Thus, the combined state of the two halved members is maintained.
(Corresponding to claim 4). In this case, using the hinge, the two half members are easily overlapped to obtain a desired assembled state, and this assembled state is achieved by the locking action of the locking portion and the locked portion. Can be held.

The locking portion is a locking claw portion formed at the end opposite to the hinge,
The locked portion is formed at an end portion opposite to the hinge and is a locking hole portion into which the locking claw portion is inserted.
(Corresponding to claim 5). In this case, the assembly state of the oil supply pipe can be maintained using a general locking mechanism such as a locking claw and a locking hole.

  The outer diameter of the oil supply pipe including the hinge is set to be equal to or smaller than the inner diameter of the main oil hole in a state where the two halved members are coupled to each other (Claim 6). Correspondence). In this case, when inserting the oil supply pipe into the main oil hole, it is possible to surely prevent the hinge from interfering with the oil supply pipe, which is preferable for improving the assembly of the oil supply pipe to the rotating shaft. Become.

The two half members are formed separately from each other,
A locking claw is formed at each circumferential end of one half member,
A locking hole is formed at each circumferential end of the other half member,
From the state in which the two halved members are overlapped with each other in the axial direction, one halved member is moved with respect to the other halved member so that the two halved members coincide in the axial direction. By sliding and displacing in the axial direction, the locking claw portion is locked in the locking hole portion, and the coupled state between the two halved members is maintained.
(Corresponding to claim 7). In this case, since the two halved members are separately formed, the manufacture thereof becomes extremely easy. In addition, it is preferable to reliably prevent a situation where the two halved members in the coupled state are separated in the radial direction by the locking action utilizing the slide displacement in the axial direction.

A mounting recess is formed on the inner surface of the main oil hole,
On the outer surface of the oil supply pipe, there is formed a mounting projection that protrudes radially outward and fits into the mounting recess.
This is done (corresponding to claim 8). In this case, the oil supply pipe can be properly positioned in the radial direction and the axial direction with respect to the main oil hole by the fitting action of the mounting recess and the mounting projection.

On the outer peripheral surface of the oil supply pipe, an elastic protrusion that protrudes toward the radially outer side and is elastically deformable toward the radially inner side is formed.
In a state where the oil supply pipe is inserted into the main oil hole, the elastic protrusion is elastically in contact with the inner surface of the main oil hole.
(Corresponding to claim 9). In this case, the dimensional error in the radial direction of the oil supply pipe can be absorbed by the elastic protrusions, thereby preventing the oil supply pipe from unnecessarily rattling in the main oil hole.

A plurality of the oil outlet holes are formed at intervals in the axial direction of the rotating shaft,
A plurality of the communication holes formed in the oil supply pipe are formed at intervals in the axial direction corresponding to the plurality of oil outlet holes,
The spiral guide groove is formed continuously from one end side of the oil supply pipe to the other end side,
(Corresponding to claim 10). In this case, oil can be supplied to the plurality of oil outlet holes using the oil supply pipe. In addition, since the guide groove is continuous in the axial direction of the oil supply pipe, it is sufficient for the oil outlet hole (the corresponding communication hole) located on the farthest side without deteriorating the oil flow on the way. This is preferable for supplying oil to the tank.

  The oil supply pipe is formed of a synthetic resin (corresponding to claim 11). In this case, the oil supply pipe having the spiral guide groove is preferable for easy and inexpensive production, and also preferable for reducing the weight of the oil supply pipe.

  The rotary shaft has a transmission shape that is rotatably held in a transmission casing (corresponding to claim 12). In this case, the formation of the main oil hole and the oil outlet hole is suitable for supplying a sufficient amount of oil to a bearing portion, a gear portion, and the like of the rotating shaft by applying it to a general rotating shaft for a transmission. is there.

  According to the present invention, even when a long non-rotating member such as an operating rod does not exist in the main oil hole, the rotation of the rotating shaft itself is effectively used to sufficiently supply oil deep into the main oil hole. Can be supplied.

Side surface sectional drawing which shows the assembly completion state of the rotating shaft and oil supply pipe to which this invention was applied. The perspective view of the oil supply pipe | tube used for FIG. The disassembled perspective view of the oil supply pipe | tube shown in FIG. FIG. 3 is an exploded side sectional view of the oil supply pipe shown in FIG. 2. The principal part side view which shows the 1st procedure which couple | bonds two half members. The principal part side view which shows the 2nd procedure which couple | bonds two half members. The principal part side view which shows the 3rd procedure which couple | bonds two half members. The principal part enlarged view which looked at the attachment protrusion part for positioning from upper direction. The principal part expanded side surface sectional view which shows an elastic protrusion part. The sectional view in the direction which shows the cross-sectional shape of a guide groove and is orthogonal to the guide groove. The perspective view which shows the state from which oil is discharged from a communicating hole, while an oil supply pipe rotates. The 2nd Embodiment of the present invention is shown and an exploded perspective view of an oil supply pipe. The perspective view which shows the assembly state of the oil supply pipe | tube shown in FIG. The principal part expanded sectional view which shows the latching mechanism part of two half member shown in FIG. The principal part expanded sectional view which shows the positioning mechanism part of two half member shown in FIG. The third embodiment of the present invention is an exploded perspective view of an oil supply pipe. The perspective view which shows the assembly state of the oil supply pipe | tube shown in FIG. 16, and the state just before that. The perspective view which shows the hinge formed in the oil supply pipe | tube shown in FIG. The front view which showed the hinge and locking mechanism in the assembly state of FIG. 17, and looked at the oil supply pipe | tube from the axial direction. The hinge and locking mechanism in the middle of an assembly are shown, and radial sectional view of an oil supply pipe. The principal part expansion perspective view which shows the 4th Embodiment of this invention and shows the oil inlet opening vicinity. The figure which looked at the oil supply pipe | tube shown in FIG. 21 from the oil inlet side.

  In FIG. 1, reference numeral 1 denotes a rotating shaft, which in the embodiment is a main shaft in an automobile transmission. That is, the rotating shaft 1 is rotatably held by the transmission casing through two bearings (not shown) with two journal portions 1a and 1b. A plurality of gears (not shown) are held on the rotary shaft 1 at intervals in the axial direction between the journal portions 1a and 1b. In the embodiment, the rotating shaft 1 is for a main shaft in a manual transmission. That is, in the always-meshing manual transmission, a counter shaft (not shown) is disposed in parallel with the main shaft, and the transmission gear held on the main shaft and the transmission gear held on the counter shaft. However, the rotary shaft 1 is used as the main shaft.

  A main oil hole 2 extending in the axial direction is formed in the rotary shaft 1. In the main oil hole 2, one end side (left end side in FIG. 1) of the rotating shaft 1 is opened as an oil introduction port 2a, and the other end side is closed. A plurality of oil outlet holes 3 </ b> A to 3 </ b> D communicating with the main oil hole 2 are formed in the rotating shaft 1. Each oil outlet hole 3 </ b> A to 3 </ b> D is formed so as to penetrate through the axis of the rotating shaft 1 in the diametrical direction. Of course, the formation positions of the oil outlet holes 3A to 3D are formed at positions corresponding to parts required for lubrication or the like.

  An oil supply pipe 10 as shown in FIG. 2 is inserted into the main oil hole 2. The oil supply pipe 10 is made of a synthetic resin and has a substantially circular cross section, and is slightly shorter than the main oil hole 1. One end side (oil introduction port 2a side) of the oil supply pipe 10 is opened as an oil introduction port 10a, and the other end side is substantially closed (shape setting such that the other end side of the cylindrical member is closed).

  The oil supply pipe 10 has an oil passage 10b extending in the axial direction. The oil supply pipe 10 is formed with a plurality of communication holes 11A to 11D extending in the radial direction. The communication holes 11 </ b> A to 11 </ b> D are continuous with the oil passage 10 b and open to the outer surface side of the oil supply pipe 10. The formation positions of the communication holes 11 </ b> A to 11 </ b> D correspond to the formation positions of the oil outlet holes 3 </ b> A to 3 </ b> D of the rotating shaft 1. The effective opening area of the communication holes 11 </ b> A to 11 </ b> D is set so as to increase as it is located on the far side of the main oil hole 1.

  The oil passage 10b and the oil outlet hole 3A communicate with each other through the communication hole 11A. The oil passage 10b and the oil outlet hole 3B communicate with each other through the communication hole 11B. The oil passage 10b and the oil outlet hole 3C communicate with each other through the communication hole 11C. The oil passage 10b and the oil outlet hole 3D communicate with each other through the communication hole 11D.

  As will be described later, the oil supply pipe 10 has a mounting projection 12 formed on one end thereof fitted in a mounting opening 1 c as a mounting recess formed on one end of the rotating shaft 1. Thereby, the oil supply pipe 10 is positioned with respect to the rotating shaft 1 in the axial direction and the radial direction. The oil supply pipe 10 is slightly tightly fitted in the main oil hole 2 so that the rotary shaft 1 and the oil supply pipe 10 rotate integrally. The integral rotation function is more reliably ensured by the fitting to 1c.

  The oil supply pipe 10 is formed with a plurality of elastic protrusions 13 on one end side, as will be described later. A pair of the elastic protrusions 13 are provided at radially symmetric positions, and two pairs of the elastic protrusions 13 are provided at small intervals in the axial direction. The elastic protrusion 13 is set so that the maximum outer diameter of the oil supply pipe 10 in the portion including the elastic protrusion 13 is larger than the inner diameter of the main oil hole 2 when no external force is applied. When an external force inward in the direction is received, it is elastically deformed and the oil supply pipe 10 including the elastic protrusion 13 can be inserted into the main oil hole 1 as a whole. The elastic protrusion 13 reliably prevents rattling of the oil supply pipe 10 inserted and fitted into the main oil hole 2.

  A spiral guide groove 20 is formed on the inner surface of the oil supply pipe 10. The guide groove 20 is formed continuously from one end side to the other end side of the oil supply pipe 10. Specifically, the guide groove 20 has a length that starts from a side slightly closer to the oil introduction port 10a than the mounting projection 12 and reaches the communication hole 11A located on the farthest side. The guide groove 20 is formed so as to swirl gradually toward the far side of the oil passage 10a in either the clockwise or counterclockwise direction when viewed from the oil introduction port 10a side.

  As will be described later, the oil supply pipe 10 is constituted by joining half members 10A and 10B having a substantially semicircular cross section divided into two in the radial direction. FIG. 10 shows a cross-sectional shape of the guide groove 20 (a cross-sectional shape in a direction orthogonal to the guide groove 20) by paying attention to the half members 10A and 10B. As shown in FIG. 10, the inner surface of the guide groove 20 is formed by two circular arc surfaces with the bottom as a boundary, and is open so as to form an edge portion α with respect to the oil passage 10 b. (Improved oil drainage).

  A connection member (not shown) is connected to the oil introduction port 10a of the oil supply tube 10 (oil introduction port 2a of the main oil hole 2), and the oil supply tube 10 is connected to the oil supply tube 10 (not shown) via this connection member. Oil is pumped into the inside (that is, the oil passage 10b). The oil supplied into the oil passage 10b is discharged from the communication holes 11A to 11D through the oil outlet holes 3A to 3D and into the transmission casing, and the sliding parts and gears near the oil outlet holes 3A to 3D. The part is lubricated.

  Here, when the rotating shaft 1 is rotated, the oil supply pipe 10 is also rotated integrally with the rotating shaft 1. As a result, the oil in the oil supply pipe 10 is smoothly supplied along the spiral guide groove 20 to the back side of the oil supply pipe 10. That is, the oil in the oil passage 10b tends to be pressed against the inner surface of the oil supply pipe 10 by the centrifugal force generated with the rotation of the rotary shaft 1 (that is, the oil supply pipe 10), and the guide groove 20 is sufficiently Oil will be introduced. The oil in the guide groove 20 is guided to the back side of the oil passage 10b along the guide groove 20 by the action of a tangential component force with respect to the axis of the rotary shaft 1. Thereby, if the oil pumping pressure is the same, the oil flows more smoothly to the back side of the oil passage 10b. Further, if the fluidity of the oil toward the back side of the oil passage 10b is about the same as the conventional level, the oil pressure can be made smaller than the conventional level.

  The flow of oil along the guide groove 20 described above will be described with reference to FIG. First, consider the case where the rotating shaft 1, that is, the oil supply pipe 10 is rotated counterclockwise as viewed from the oil inlet 2a (10a) side. At this time, the spiral guide groove 20 is formed on the back side of the oil supply pipe 10 so as to rotate clockwise as viewed from the oil inlet 2a (10a) side. In this case, the oil in the guide groove 20 is subjected to an inertial force F that tries to stay in place with respect to the rotation of the rotary shaft 1, but as a component of the inertial force F, the oil in the direction orthogonal to the guide groove 20 is applied. A component force F1 and a component force F2 in the direction along the guide groove 20 are generated. Then, the component force F <b> 2 acts as a force that causes the oil in the guide groove 20 to flow to the back side of the oil supply pipe 20. The component force F2 is generated at any position of the guide groove 20, and as the extending direction of the guide groove 20 becomes closer to the axis of the oil supply pipe 10 (in FIG. 1, the guide with respect to the axis of the oil supply pipe 10). The smaller the inclination angle of the groove 20), the larger the component force F <b> 2, and the stronger the action of flowing oil toward the back side of the oil supply pipe 10. When viewed from the oil introduction port 2a side, when the rotation direction of the rotary shaft 1 is clockwise, the spiral guide groove 20 is positioned counterclockwise to the back side of the oil supply pipe 10. What is necessary is just to form.

  The oil discharged from the oil outlet holes 3A to 3D is directed substantially outward in the radial direction when the rotational speed of the rotary shaft 1 is low. And if the rotational speed of the rotating shaft 1 becomes large, as shown in FIG. 11, the oil discharged from oil outlet hole 3A-3D will be scattered widely in all directions. Of course, the number and set positions of the oil outlet holes 3A to 3D (the corresponding communication holes 11A to 1D) may be appropriately selected according to the desired lubrication position.

  Next, a specific structure and manufacturing point of the oil supply pipe 10 will be described with reference to FIGS. First, as described above, the oil supply pipe 10 is configured by joining two halved members 10A and 10B that are divided into two in the radial direction. 2 shows a coupled state (assembled state) of the two half members 10A and 10B, FIG. 3 shows an exploded state, and FIG. 4 shows a side sectional view in the exploded state. Each half member 10A and 10B is formed (for example, injection molding) by synthetic resin, respectively.

  In order to couple the two halved members 10A and 10B, a locking claw portion 31 as a locking portion is integrally formed at each circumferential end of one half member 10A. The locking claw portion 31 is formed so as to protrude from the circumferential end of the half member 10A.

  At each end in the circumferential direction of the other half member 10 </ b> B, a locking claw portion 32 as a locked portion is integrally formed corresponding to the locking claw portion 31. The locking claw 32 is formed so as not to protrude outward of the half member 10B. And the recessed part 33 is formed in the formation position of the latching claw part 32 so that the said latching claw part 31 can be located.

  The locking claws 31 and 32 are each formed to extend in the axial direction of the oil supply pipe 10. In order to lock both the locking claws 31 and 32, first, as shown in FIG. 5, the locking claws 31 are set in a positional relationship in which the two half members 10A and 10B are slightly shifted in the axial direction. Is the positional relationship shown in FIG. From the state of FIG. 5, the two half members 10 </ b> A and 10 </ b> B are brought close to each other, and the state of FIG. Thereafter, the two half members 10A and 10B are slid in the axial direction so that the locking claw portion 31 approaches the locking claw portion 32, and finally the locking claw portion 31 is locked. The claw portion 32 is locked. Thus, the assembled state shown in FIG. 2 is obtained in which the two half members 10A and 10B are coupled.

  In addition, the said latching claw part 31 and the latching claw part 32 are provided in the circumferential direction one end part side of the half members 10A and 10B, for example, with three spaces at intervals in the axial direction. Two are provided at intervals in the axial direction, but the number can be set as appropriate.

  FIG. 8 shows the details of the mounting projection 12 described above. That is, a leg portion 36 that extends short in the axial direction is formed by forming a U-shaped cutout portion 35 in a plan view at the central portion in the circumferential direction of the half member 10B. And the attachment protrusion part 12 which protrudes toward a radial direction outer side is integrally molded by the front-end | tip part of the leg part 36. As shown in FIG. Using the elastic deformation of the leg portion 36, the mounting projection 12 is fitted with a sense of moderation in the mounting opening 1c formed in the rotating shaft 1, and after the fitting, the fitted state is It will be maintained reliably. In the embodiment, only one mounting protrusion 12 and a corresponding mounting opening 1c are provided as a whole, but a plurality of mounting projections 12 are provided in the radial direction of the oil supply pipe 10 or spaced in the axial direction. A plurality can be provided with a gap. Note that the mounting opening 1c as the mounting recess may be a bottomed shape that is not penetrating without being formed as a penetrating hole.

  FIG. 9 shows the details of the elastic protrusion 13 described above. That is, a protrusion 13a that protrudes outward in the radial direction is formed on the half members 10A and 10B, while a cavity 13b is formed on the radially inner side of the protrusion 12a. . The cavity 13b extends longer in the axial direction than the protrusion 13a. Thereby, in the state which does not receive external force, although the protrusion part 13a protrudes to the radial direction outer side of the half member 10A, 10B, if the external force to radial direction inner side is received, the cavity part 13b will be diameter. As a result of being compressed and deformed in the direction (elastically deformed), the protrusion 13a is retracted radially inward. In a state where the oil supply pipe 10 is inserted into the main oil hole 2, the protrusion 13 a elastically contacts the inner surface of the main oil hole 2, and rattling of the oil supply pipe 10 with respect to the rotating shaft 1 is prevented. It will be. The elastic protrusions 13 as described above may be provided at each end of the oil supply pipe 10 or may be provided at an intermediate position, and the number of settings can be appropriately selected.

  As shown in FIG. 4, a locking claw portion 15 extending in the axial direction is formed on the back end wall portion of the half member 10 </ b> A, while extending in the axial direction on the back end wall portion of the half member 10 </ b> B. A locking hole 16 is formed. In the process of joining the two halved members 10A and 10B, the radial claw separation between the two halved members 10A and 10B is further enhanced by inserting the locking claw portion 15 into the locking hole portion 16. Regulated by

  12 to 15 show a second embodiment of the present invention. The same components as those in the above embodiment are given the same reference numerals, and redundant description thereof is omitted (this is described below). The same applies to the third embodiment).

  In the present embodiment, the two halved members 10 </ b> A and 10 </ b> B are coupled by approaching the oil supply pipe 10 in the radial direction. That is, as shown in FIG. 14, one half member 10 </ b> A is formed with a locking claw portion 41 as a locking portion, while the other half member 10 </ b> B has a locking portion as a locked portion. A locking hole 41 is formed. The halved members 10A and 10B are brought close to each other in the radial direction and locked in the locking claw portion 41 and the locking hole portion 42, so that the combined state of the halved members 10A and 10B is maintained. The setting positions of the number of the locking claws 41 and the locking holes 42 can be appropriately selected.

  Further, a positioning projection 43 is formed on one half member 10A, while a positioning hole 44 is formed on the other half member 10B. By fitting the positioning projection 43 to the positioning hole 44, the coupling in a state where the two half members 10A and 10B are positioned is ensured. The number and setting positions of the positioning protrusions 43 and the positioning holes 44 can be selected as appropriate. The guide groove 20 is formed with a smaller pitch than in the above-described embodiment (the setting is such that the component force F2 shown in FIG. 1 is smaller than in the above-described embodiment). In the present embodiment, the oil supply pipe 10 has a cylindrical shape whose ends are greatly opened.

  16 to 20 show a third embodiment of the present invention. In the present embodiment, the two half members 10A and 10B are integrally molded (for example, injection molded) including the hinge 51. That is, FIG. 16 shows a state immediately after being formed, and the one end portion in the circumferential direction of one half member 10 </ b> A and the one end portion in the circumferential direction of the other half member 10 </ b> B are connected via the hinge 51. It is assumed that it was done. From the state shown in FIG. 16, by turning the half member 10A so as to overlap the other half member 10B around the hinge 51 (rotating approximately 180 degrees), the solid line in FIG. The assembled state is as shown.

  In order to maintain (hold) the assembled state of FIG. 17, a locking claw portion 52 as a locking portion is provided on the other end portion of one half member 10 </ b> A and the other end portion of the other half member 10 </ b> B. And the locked portion 53 are integrally formed. The locking claw portion 52 extends in the circumferential direction, and in the coupled state, the locking claw portion 52 approaches the locked portion 53 from one side in the circumferential direction and finally locks to the locked portion 53. Is done. (The state is changed from the state of FIG. 20 to the state of FIG. 19). A plurality of such locking claws 52 and locked portions 53 are provided at intervals in the axial direction of the oil supply pipe 10, and the number and setting position thereof can be selected as appropriate.

  The hinge 51 is formed as a thin plate having a small axial width with a gap in the axial direction. As shown in FIG. 19, in the assembled state, the maximum outer diameter of the oil supply pipe 10 including the hinge 51 is set to be equal to or smaller than the inner diameter of the main oil hole 2. Specifically, the thickness in the vicinity of the hinge 51 of each of the half members 10A and 10B is made thin. In the present embodiment, the oil supply pipe 10 has a cylindrical shape whose ends are greatly opened.

  21 and 22 show a fourth embodiment of the present invention. In the present embodiment, six elastic protrusions 13 are provided in total, one at each of the left and right boundary portions between the half members 10A and 10B. As a result, in the circumferential direction of the oil supply pipe 10, there are a total of four elastic projections 13 at intervals of approximately 90 degrees, and when the oil supply pipe 10 is inserted and installed in the main oil hole 2. In addition, it is possible to more surely prevent radial backlash. The two elastic protrusions 13 provided at the boundary (divided) portion between the half members 10A and 10B are formed in a form divided into half members 10A and 10B. It is configured when combined with 10B. The number of elastic protrusions 13 around the circumferential direction of the oil supply pipe 10 and the number in the axial direction can be set as appropriate.

  Although the embodiment has been described above, the present invention is not limited to the embodiment, and can be appropriately changed within the scope described in the scope of claims. For example, the invention includes the following cases. . The oil supply pipe 10 may be integrally formed in an annular shape instead of half, or may be divided into three or more in the circumferential direction. The oil supply pipe 10 may be formed of a metal or a composite material. Appropriate structures can be adopted for the locking portions and the locked portions, and those shown in one embodiment can be applied to other embodiments. The rotary shaft 1 is not limited to a transmission, and the present invention can be applied to a rotary shaft in appropriate equipment.

  For example, two or more guide grooves 20 may be formed substantially parallel to each other. The guide groove 20 can also be formed as a divided guide groove in a plurality of parts divided in the axial direction of the oil supply pipe 10, and the axial ends of the divided guide grooves are not communicated with each other. It is good also as the arrangement | positioning relationship which overlaps in a direction. The guide groove 20 is preferably set so as to pass through the communication holes 11A to 11D, but may be set so as not to pass through the communication holes 11A to 11D. When the guide groove 20 does not pass through the communication hole, a spiral branch guide groove reaching the communication holes 11A to 11D may be branched from the guide groove 20 and formed. Of course, the object of the present invention is not limited to what is explicitly stated, but also implicitly includes providing what is substantially preferred or expressed as an advantage.

  The present invention is suitable, for example, as a lubricating oil path structure in the rotating shaft of a transmission.

1: Rotating shaft 1c: Mounting opening (mounting recess)
2: Main oil hole 2a: Oil inlet 3A-3D: Oil outlet 10: Oil supply pipe 10a: Oil inlet 10A, 10B: Half member 11A-11D: Communication hole 12: Mounting protrusion 13: Elastic protrusion 20: Guide groove 31: Locking claw part (locking part)
32: Locking claw part (locked part)
41: Inclined claw part (locking part)
42: Locking hole (locked part)
43: Positioning projection 44: Positioning hole 51: Hinge 52: Locking claw (locking)
53: Locked part

Claims (12)

A main oil hole extending in the axial direction and an oil outlet hole extending in the radial direction and communicating with the main oil hole are formed in the rotation shaft,
In the lubricating oil passage structure in which the oil supplied from one end side of the main oil hole into the main oil hole is discharged to the radially outer side of the rotating shaft through the oil outlet hole,
In the main oil hole, an oil supply pipe is fitted so as to rotate integrally with the rotary shaft,
A communication hole is formed in the oil supply pipe to communicate the oil supply pipe with the oil outlet hole.
A spiral guide groove is formed on the inner surface of the oil supply pipe to allow oil supplied from one end side of the main oil hole to flow toward the other end side of the main oil hole in accordance with the rotation of the rotating shaft. Being
Lubricating oil passage structure characterized by that. In claim 1,
The lubricating oil passage structure, wherein the guide groove is formed so as to pass through the communication hole. In claim 1 or claim 2,
The oil supply pipe is configured by joining two half members having a substantially semicircular cross section divided into two in the radial direction. In claim 3,
The two half members are connected to each other by a hinge,
Of the two halved members, a locking portion is formed on one half member, and a locked portion on which the locking portion is locked is formed on the other half member.
The locking portion is locked to the locked portion in a state where the oil supply pipe having a substantially circular cross section is formed by overlapping the two halved members by rotation around the hinge. Thus, the combined state of the two halved members is maintained.
Lubricating oil passage structure characterized by that. In claim 4,
The locking portion is a locking claw portion formed at the end opposite to the hinge,
The locked portion is formed at an end portion opposite to the hinge and is a locking hole portion into which the locking claw portion is inserted.
Lubricating oil passage structure characterized by that. In claim 4 or claim 5,
A lubricating oil passage characterized in that an outer diameter of the oil supply pipe including the hinge is set to be equal to or smaller than an inner diameter of the main oil hole in a state where the two half members are joined to each other. Construction. In claim 3,
The two half members are formed separately from each other,
A locking claw is formed at each circumferential end of one half member,
A locking hole is formed at each circumferential end of the other half member,
From the state in which the two halved members are overlapped with each other in the axial direction, one halved member is moved with respect to the other halved member so that the two halved members coincide in the axial direction. By sliding and displacing in the axial direction, the locking claw portion is locked in the locking hole portion, and the coupled state between the two halved members is maintained.
Lubricating oil passage structure characterized by that. In any one of Claims 1 thru | or 7,
A mounting recess is formed on the inner surface of the main oil hole,
On the outer surface of the oil supply pipe, there is formed a mounting projection that protrudes radially outward and fits into the mounting recess.
Lubricating oil passage structure characterized by that. In any one of Claims 1 thru | or 8,
On the outer peripheral surface of the oil supply pipe, an elastic protrusion that protrudes toward the radially outer side and is elastically deformable toward the radially inner side is formed.
In a state where the oil supply pipe is inserted into the main oil hole, the elastic protrusion is elastically in contact with the inner surface of the main oil hole.
Lubricating oil passage structure characterized by that. In any one of Claims 1 thru | or 9,
A plurality of the oil outlet holes are formed at intervals in the axial direction of the rotating shaft,
A plurality of the communication holes formed in the oil supply pipe are formed at intervals in the axial direction corresponding to the plurality of oil outlet holes,
The spiral guide groove is formed continuously from one end side of the oil supply pipe to the other end side,
Lubricating oil passage structure characterized by that. In any one of Claims 1 thru | or 10,
A lubricating oil passage structure, wherein the oil supply pipe is made of a synthetic resin. In any one of Claims 1 thru | or 11,
A lubricating oil passage structure characterized in that the rotating shaft has a shape for transmission that is rotatably held in a transmission casing.

Images