JP2006170404A - Oil supply structure for rotating shaft - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To secure an oil passage between hollow pipes while improving the assembling efficiency of the plurality of hollow pipes extending to the axial direction. <P>SOLUTION: An outside pipe 14 and an inside pipe 18 having a diameter smaller than the outside pipe 14 are nested and inserted in an axial hole 13 which is formed in a transmission counter shaft 12 of a belt type continuously variable transmission TM extending from the shaft end to the axial direction. The transmission counter shaft 12 has a first axial oil passage 21 extending between the outer peripheral face of the inside pipe 18 and the inner peripheral face of the outside pipe 14 and a second axial oil passage 22 extending into the inside pipe 18. A plurality of boss portions 41, 42, 43, 44 are formed on the inner peripheral face of the outside pipe 14 for abutting on the outer peripheral face of the inside pipe 18 in the state of being protruded to the radial inside of the outside pipe 14 by almost the same length to maintain the concentric conditions of the outside pipe 14 and the inside pipe 18. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an oil supply structure for a rotating shaft for supplying hydraulic oil, lubricating oil, and the like through a rotating shaft to a transmission disposed on the rotating shaft, such as a rotating shaft of a transmission.

  In a transmission or the like, a pulley, a clutch, a gear, and the like are disposed on a rotating shaft, and the operation of the pulley and the like is controlled by oil pressure supplied through the rotating shaft, and similarly by oil supplied through the rotating shaft. The clutch, gear, etc. are lubricated. For this reason, it is necessary to provide a plurality of oil supply passages on the rotating shaft, and an axial hole extending in the axial direction from the end of the rotating shaft is formed, and a hollow tube is inserted into the axial hole, A plurality of oil supply passages are configured by dividing into an oil passage extending and an oil passage extending and surrounded by the outer peripheral surface of the hollow tube and the inner peripheral surface of the axial hole. This is also described in, for example, Patent Document 1 and Patent Document 2.

Further, if the hollow tube is configured by inserting a small-diameter inner tube into a large-diameter outer tube in a nested manner, an oil passage extending through the inner tube, an outer peripheral surface of the inner tube, and an inner periphery of the outer tube An oil passage that is surrounded by a surface can be formed, and even with such a configuration, it is possible to provide a plurality of oil supply passages on the rotating shaft.
Japanese Patent Laid-Open No. 11-63176 JP 2001-124189 A

  By the way, each of the outer tube and the inner tube as described above is fixed in a state where one end of each is attached to a housing provided in the transmission, and the other end is in a cantilever state in which the other end can be freely moved to some extent. These tubes are assembled by inserting the other end of the shaft into the axial hole of the rotating shaft. However, when the ends of the outer tube and the inner tube are inserted into the axial hole of the rotating shaft in such a state that one end of the outer tube and the inner tube is attached to the housing, the concentricity of the outer tube and the inner tube is not always maintained. When the axial direction of the outer tube deviates with respect to the direction, the end surface of the outer tube may get caught by contacting the mounting bush provided in the axial hole of the rotating shaft. There was a problem that it was difficult to attach.

  In view of the problems as described above, the oil that extends between the outer peripheral surface of the inner tube and the inner peripheral surface of the outer tube after improving the assembly of the outer tube and the inner tube to the transmission countershaft. An object of the present invention is to provide an oil supply structure for a rotating shaft with a supply path secured.

  In order to solve the above-mentioned problems, the oil supply structure for a rotating shaft according to the present invention is a shaft formed by extending in the axial direction in a rotating shaft (for example, the transmission countershaft 12 in the embodiment) that is rotatably supported. In an oil supply structure for delivering oil to and from the outer peripheral side of a rotating shaft through a directional oil passage, a first hollow tube is formed in an axial hole formed by extending the rotating shaft from the shaft end portion in the axial direction. (For example, the outer tube 14 in the embodiment) and a second hollow tube having a diameter smaller than that of the first hollow tube (for example, the inner tube 18 in the embodiment) are telescopically inserted, and the second hollow tube A first axial oil passage extending and surrounded by an outer peripheral surface of the tube and an inner peripheral surface of the first hollow tube, and a second axial oil passage extending in the second hollow tube; , Concentricity maintaining means for maintaining the concentric state of the first and second hollow tubes in the first axial oil passage (example) Has a projection 41, 42, 43, 44) in the field embodiment.

  Further, in the oil supply structure of the rotating shaft configured as described above, the concentricity maintaining means is provided at a plurality of locations on the inner peripheral surface of the first hollow tube and protrudes to substantially the same length radially inward of the first hollow tube. It is preferable that the protrusion is formed so as to contact the outer peripheral surface of the second hollow tube in this state.

  On the other hand, in the oil supply structure of the rotating shaft configured as described above, the concentricity maintaining means is provided at a plurality of locations on the outer peripheral surface of the second hollow tube and protrudes to substantially the same length outward in the radial direction of the second hollow tube. The protrusion part formed so that it might contact | abut to the internal peripheral surface of a 1st hollow tube in the state may be sufficient.

  Furthermore, in the oil supply structure of the rotating shaft having the above-described configuration, the protrusion is formed of a pair of protrusions formed in axial symmetry with respect to the first hollow tube on the inner peripheral surface of the first hollow tube. One inner protrusion (for example, the protrusion 41 and the protrusion 42 in the embodiment) and the first hollow tube at a position away from the protruding position of the first inner protrusion in the axial direction of the first hollow tube The second inner protrusions (e.g., the protrusion 43 and the protrusion 44 in the embodiment) formed of a pair of protrusions that are axially symmetrical with respect to the first and second inner protrusions, Position where the direction of the straight line connecting the second inner protrusions is a direction rotated about 90 ° around the axis of the first hollow tube with respect to the direction of the straight line connecting the first inner protrusions It is preferable to form it.

  On the other hand, in the oil supply structure of the rotating shaft having the above-described configuration, the first protrusion includes a pair of protrusions formed symmetrically with respect to the second hollow tube on the outer peripheral surface of the second hollow tube. Outer projections (for example, the projection 45 and the projection 46 in the embodiment) and the second hollow tube at a position away from the projection position of the first outer projection in the axial direction of the second hollow tube. The first and second outer protrusions include a second outer protrusion (for example, the protrusion 47 and the protrusion 48 in the embodiment) formed of a pair of protrusions that are axially symmetrical with respect to the first protrusion. The direction of the straight line connecting the two outer protrusions is in a position rotated about 90 ° around the axis of the second hollow tube with respect to the direction of the straight line connecting the first outer protrusions. It may be formed.

  According to the oil supply structure of the rotary shaft relating to the present invention, by forming a plurality of protrusions protruding to substantially the same length on the inner peripheral surface of the first hollow tube or the outer peripheral surface of the second hollow tube. When the second hollow tube is telescopically inserted into the first hollow tube, one of the first hollow tube and the second hollow tube has the first hollow tube. And the other of the second hollow tubes abuts against the other of the second hollow tube and an outer circumferential surface of the first hollow tube so that a uniform gap is generated in the circumferential direction. The concentricity of the hollow tube and the second hollow tube is maintained. And in the state where the concentricity of both the pipes is maintained in this way, when the both pipes are inserted for mounting in the rotation shaft hole of the transmission countershaft, the outer first hollow tube is the rotation shaft. Since it is not caught by the bush etc. in a hole, it becomes possible to mount | wear both pipes smoothly. That is, the protrusion as a spacer maintains the concentricity of the first hollow tube and the second hollow tube, so that the mounting property of both tubes to the transmission countershaft can be improved.

  In addition, since both tubes are always held so that a uniform gap is generated in the circumferential direction between the inner peripheral surface of the first hollow tube and the outer peripheral surface of the second hollow tube, The oil passage extending between the inner peripheral surface of the hollow tube and the outer peripheral surface of the second hollow tube is not blocked. That is, by securing a plurality of oil supply passages on the rotating shaft, it becomes possible to supply the working oil to the pulley and the lubricating oil to the gear and the like through the rotating shaft without any delay.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings. FIG. 1 shows a belt type continuously variable transmission TM using a rotary shaft having an oil supply structure according to the present invention, and FIG. 2 shows a skeleton diagram thereof.

  The belt-type continuously variable transmission TM is provided between a belt-type continuously variable transmission 4 that shifts and outputs power input from an engine (motor) (not shown), and the engine and the belt-type continuously variable transmission 4. And a torque converter 30 for transmitting power. The belt-type continuously variable transmission 4 is housed in the transmission housing 2, and the transmission input shaft S1, the primary shaft 11, the transmission countershaft 12, and the left and right axle shafts 8a and 8b are each a transmission. It is rotatably supported by a bearing attached in the housing 2. Here, the transmission input shaft S1 and the primary shaft 11 are disposed on the same axis, and the transmission countershaft 12 is located at a predetermined distance in parallel with the transmission input shaft S1 (or the primary shaft 11). ing. Further, the left and right axle shafts 8 a and 8 b are disposed on the same axis and are located in parallel with the transmission countershaft 12 and separated by a predetermined distance.

  Power from an engine (not shown) is input to the transmission input shaft S1 via the torque converter 30. The torque converter 30 includes a pump impeller 31, a turbine runner 32, and a stator 33. The pump impeller 31 is integrated with a converter cover 34 that covers the outer periphery thereof.

  The torque converter 30 is provided with a lock-up mechanism 50. The lock-up clutch piston 51 is pressed against the inner surface of the converter cover 34 to engage both members 51 and 34, and the power from the engine is directly transmitted to the transmission input shaft S1. Can be communicated to. Such an operation of the lockup clutch piston 51 is formed on the turbine runner 32 side of the two oil chambers formed by partitioning the space in the torque converter 30 by the lockup clutch 51, that is, the lockup clutch 51. This is performed by supplying and discharging oil to and from the oil chamber (the turbine side oil chamber 52) and the oil chamber (with the cover side oil chamber 53) formed closer to the converter cover 34 than the lockup clutch piston 51.

  The power of the transmission input shaft S1 is transmitted to the primary shaft 11 via the forward / reverse switching mechanism 3, and the power of the primary shaft 11 is driven by a drive pulley 71 provided on the primary shaft 11 and a transmission countershaft 12. This is transmitted to the transmission countershaft 12 via a belt-type continuously variable transmission 4 comprising a driven pulley 75 provided above and a V-belt 79 spanned between these pulleys 71, 75.

  The drive pulley 71 includes a fixed pulley half 72 fixed to the primary shaft 11, and a movable pulley half 73 provided so as to be axially slidable on the primary shaft 11 so as to face the fixed pulley half 72. The movable pulley half 73 is moved by supplying and discharging oil into a cylinder chamber (not shown) to change the interval (pulley width) between the fixed pulley half 72 and the movable pulley half 73. Is possible. The driven pulley 75 has a fixed pulley half 76 fixed to the transmission countershaft 12 and a movable pulley slidably mounted on the transmission countershaft 12 so as to face the fixed pulley half 76. The pulley half body 77 is configured to move the movable pulley half body 77 by supplying and discharging oil into and from the cylinder chamber 78 (see FIG. 3), so that the fixed pulley half body 76 and the movable pulley half body 77 It is possible to change the interval (pulley width). Then, by adjusting the pulley width of both the pulleys 71 and 75, the winding radius of the V-belt 79 can be changed, so that the gear ratio between the shafts 11 and 12 can be changed steplessly. It is.

  The power input to the transmission countershaft 12 is transmitted to the differential mechanism 7 via the reduction gear train 6. The differential mechanism 7 divides and transmits the input power to the left and right front axle shafts 8a and 8b, and drives left and right wheels (front wheels) (not shown) provided at the ends of the shafts 8a and 8b.

  In the transmission TM configured as described above, the oil supply structure according to the present invention is used for the transmission countershaft 12. In order to show the oil supply structure in detail, FIG. 3 shows the transmission countershaft 12, the driven pulley 75, the reduction gear train 6 and the like arranged thereon, which will be described in combination with this figure. .

  A driven pulley 75 is fixed to the transmission countershaft 12, and the transmission countershaft 12 is rotatable with respect to the transmission housing 2 by bearings 17 a and 17 b disposed on both sides of the driven pulley 75. It is supported by. In FIG. 3, a first reduction gear 61 constituting the reduction gear train 6 is rotatably supported on the transmission countershaft 12 on the right side of the bearing 17a. The first reduction gear 61 is a second reduction gear 61. It meshes with the reduction gear 62.

  The driven pulley 75 is coupled to the transmission counter shaft 12 and provided with a piston 51, and the piston 51 rotates integrally with the transmission counter shaft 12. The driven pulley 75 receives an operating pressure supplied into a cylinder chamber 78 formed by being surrounded by the movable pulley half 77 of the driven pulley 75, the transmission countershaft 12, and the piston 51. , The distance between the fixed pulley half 76 and the movable pulley half 77 changes. For this reason, if the supply control of the oil supplied into the cylinder chamber 78 is performed, it is possible to change the winding radius of the driven pulley 75 of the V belt 79.

  A return spring 52 is disposed between the movable pulley half 77 and the piston 51 in the cylinder chamber 78. When the hydraulic fluid supplied from the transmission countershaft 12 side is controlled so that the hydraulic pressure in the cylinder chamber 78 is low, the movable pulley half 77 is moved to the right in FIG. The distance between the fixed pulley half 76 and the movable pulley half 77 is increased.

  It is necessary to supply oil for operating the movable pulley half 77 and the like, lubricating the gear, and cooling the driven pulley 75 and the reduction gear train 6 having such a configuration. And since these hydraulic oil, lubricating oil, etc. are independently controlled by hydraulic pressure setting, it is necessary to supply them through different oil passages. For this reason, the transmission countershaft 12 is formed with an axial hole 13 extending in the axial direction from the left end thereof. An outer tube 14 having protrusions 41 to 44 described later is inserted into the axial hole 13, and one end thereof is fixed to the axial hole 13 by a mounting bush 23. Further, a long inner tube 18 having a smaller diameter than the inner tube 18 is inserted into the outer tube 14 in a nested manner, and one end thereof is fixed to the axial hole 13 by a mounting bush 24. A first axial oil passage 21 for supplying hydraulic oil into the cylinder chamber 78 for operating the movable pulley half 77 is surrounded by the outer periphery of the inner tube 18 and the inner periphery of the outer tube 14. A second axial oil passage 22 is formed in the inner pipe 18 for supplying lubricating oil to the gears of the reduction gear train 6.

  The outer pipe 14 and the inner pipe 18 are respectively formed with flange portions 14a and 18a at one end, and are fixed in a housing 19 provided in the belt type continuously variable transmission TM via the flange portions 14a and 18a. Further, the mounting bush 23 that fixes the outer tube 14 is sealed so that the oil flowing in the first axial oil passage 21 does not flow outside, and the second bushing 24 that fixes the inner tube 18 fixes the second axial oil. Oil flowing through the passage 22 is prevented from flowing into the first axial oil passage 21, and oil flowing through the first axial oil passage 21 is prevented from flowing into the second axial oil passage 22. It has become so.

  The transmission countershaft 12 is formed with a plurality of radial oil passages extending in the radial direction. Among these, the radial oil passage 25 communicates with the cylinder chamber 78, and the oil flowing through the first axial oil passage 21 flows into the cylinder chamber 78. On the other hand, the radial oil passage 26 communicates with the outside of the transmission countershaft 12 so as to lubricate the first reduction gear 61 and the like.

  Here, the protrusions formed on the inner tube 18 will be described with additional reference to FIG. As shown in FIG. 4, a plurality of protrusions 41, 42, 43, 44 (inner protrusions) are formed on the inner peripheral surface of the outer tube 14 so as to protrude substantially inward in the radial direction. Among these, a pair of protrusions composed of the protrusion 41 and the protrusion 42 protrude so as to face each other symmetrically with respect to the outer tube 14 (see FIG. 4C), and the protrusion 43 and the protrusions. 44 are opposed to each other in an axially symmetrical manner with respect to the outer tube 14 at a position away from the position where the protrusion 41 and the protrusion 42 protrude in the axial direction of the outer tube 14 (leftward in FIG. 4A) (See FIG. 4B).

  Further, the protrusion 43 and the protrusion 44 are arranged such that the direction of the straight line L2 (see FIG. 4B) connecting the protrusion 43 and the protrusion 44 is a straight line L1 connecting the protrusion 41 and the protrusion 42 (FIG. 4A). ))), The outer tube 14 is formed in a position rotated about 90 ° around the axis. And the outer peripheral surface is contact | abutted and hold | maintained by the projection parts 41-44 which have the above positional relationship, as the inner side pipe | tube 18 inserted in the outer side pipe | tube 14 is shown with a dashed line. Therefore, concentricity between the outer tube 14 and the inner tube 18 is maintained, and a first axial oil passage 21 extending in the axial direction is secured between the inner peripheral surface of the outer tube 14 and the outer peripheral surface of the inner tube 18. Will be. Therefore, the oil flowing in the first axial oil passage 21 can be sent to the right in FIG.

  Here, the effects achieved in the present invention are summarized as follows. That is, in the oil supply structure of the rotating shaft according to the present invention, a plurality of protrusions or the like that protrude to substantially the same length are formed on the inner peripheral surface of the first hollow tube or the outer peripheral surface of the second hollow tube. Thus, when the second hollow tube is telescopically inserted into the first hollow tube, one protrusion of the first hollow tube and the second hollow tube There is a uniform gap in the circumferential direction between the outer peripheral surface of the second hollow tube and the inner peripheral surface of the first hollow tube in contact with the other of the hollow tube and the second hollow tube. As a result, the concentricity of the first hollow tube and the second hollow tube is maintained. And in the state where the concentricity of both the pipes is maintained in this way, when the both pipes are inserted for mounting in the rotation shaft hole of the transmission countershaft, the outer first hollow tube is the rotation shaft. Since it is not caught by the bush etc. in a hole, it becomes possible to mount | wear both pipes smoothly. That is, the protrusion as a spacer maintains the concentricity of the first hollow tube and the second hollow tube, so that the mounting property of both tubes to the transmission countershaft can be improved.

  In addition, since both tubes are always held so that a uniform gap is generated in the circumferential direction between the inner peripheral surface of the first hollow tube and the outer peripheral surface of the second hollow tube, The oil passage extending between the inner peripheral surface of the hollow tube and the outer peripheral surface of the second hollow tube is not blocked. That is, by securing a plurality of oil supply passages on the rotating shaft, it becomes possible to supply the working oil to the pulley and the lubricating oil to the gear and the like through the rotating shaft without any delay.

  Although the preferred embodiments of the present invention have been described so far, the scope of the present invention is not limited to the above-described embodiments. For example, a plurality of (for example, three) protrusions protruding from the inner peripheral surface of the outer tube 14 to substantially the same length may be formed at equal intervals in the circumferential direction of the outer tube 14. In this way, the outer peripheral surface of the inner tube 18 inserted into the outer tube 14 abuts against the three protrusions, so that the outer tube 14 and the inner tube 18 can be reliably concentric at the three abutting portions. Can be held.

  Further, the plurality of protrusions are not necessarily formed on the inner peripheral surface of the outer tube 14 as in the above embodiment. That is, as shown in FIG. 5, an outer protrusion that protrudes to substantially the same length outside the inner tube 18 in the radial direction may be formed on the outer peripheral surface of the inner tube 18. In such a case, a plurality of protrusions protruding from the inner tube 18 can abut on the inner peripheral surface of the outer tube 14 to keep the outer tube 14 and the inner tube 18 concentric.

  In this case, a pair of projecting portions including the projecting portion 45 and the projecting portion 46 are formed symmetrically with respect to the inner tube 18 on the outer peripheral surface of the inner tube 18 (see FIG. 5C). Another pair of protrusions 48 is separated from the position where the pair of protrusions 45 and 46 protrudes in the axial direction of the inner tube 18 (to the left in FIG. 5A). In position, it is formed axially symmetrically with respect to the inner tube 18 (see FIG. 5B). Further, the protrusion 47 and the protrusion 48 have a straight line L3 (see FIG. 5A) in which the direction of the straight line L4 (see FIG. 5B) connecting the protrusion 47 and the protrusion 48 is connected to the protrusion 45 and the protrusion 46. ))), And a direction rotated approximately 90 ° around the axis of the inner tube 18 is formed. In this way, an axial oil passage extending in the axial direction can be secured between the outer peripheral surface of the inner tube 18 and the inner peripheral surface of the outer tube 14.

It is sectional drawing which shows the structure of the transmission which has the oil supply structure of the rotating shaft which concerns on this invention. It is a skeleton figure which shows the structure of the said transmission. It is sectional drawing which shows the structure around the transmission countershaft in the said transmission. It is a figure explaining the projection part provided in the outer side pipe inserted in the said transmission countershaft, (a) is a sectional side view of an outer side pipe | tube, (b) was along arrow BB of (a). It is sectional drawing, (c) is sectional drawing along the arrow AA. It is a figure explaining the projection part of a form different from the said projection part provided in the inner pipe inserted in the said transmission countershaft, (a) is a sectional side view of an inner pipe, (b) is (a). (C) is sectional drawing along the arrow CC.

Explanation of symbols

TM Belt type continuously variable transmission 6 Reduction gear train 12 Transmission countershaft (rotary shaft)
13 Axial hole 14 Outer tube (first hollow tube)
18 Inner tube (second hollow tube)
21 First axial oil passage (axial oil passage)
22 Second axial oil passage (axial oil passage)
25 radial oil passage 41 protrusion (first inner protrusion, concentricity maintaining means)
42 Protrusion (first inner protrusion, concentricity maintaining means)
43 Protrusion (second inner protrusion, concentricity maintaining means)
44 Protrusion (second inner protrusion, concentricity maintaining means)
45 Protrusion (first outer protrusion, concentricity maintaining means)
46 Protrusion (first outer protrusion, concentricity maintaining means)
47 Protrusion (second outer protrusion, concentricity maintaining means)
48 protrusion (second outer protrusion, concentricity maintaining means)
71 Drive-side pulley 75 Driven-side pulley 76 Fixed pulley half 77 Movable pulley half 78 Cylinder chamber

Claims (5)

In an oil supply structure for delivering oil to and from the outer peripheral side of the rotary shaft through an axial oil passage formed extending in the axial direction in a rotary shaft that is rotatably supported,
A first hollow tube and a second hollow tube having a smaller diameter than the first hollow tube are nested in the axial hole formed by extending the rotating shaft from the axial end in the axial direction. Inserted,
A first axial oil passage extending and surrounded by an outer peripheral surface of the second hollow tube and an inner peripheral surface of the first hollow tube; and a second axial oil passage extending in the second hollow tube. And
An oil supply structure for a rotating shaft, wherein concentricity maintaining means for maintaining the concentric state of the first and second hollow tubes is provided in the first axial oil passage.   The concentricity maintaining means is provided at a plurality of locations on the inner peripheral surface of the first hollow tube, and protrudes to substantially the same length radially inward of the first hollow tube. The oil supply structure for a rotary shaft according to claim 1, wherein the oil supply structure is a protrusion formed so as to be in contact with the outer peripheral surface of the rotating shaft.   The concentricity maintaining means is provided at a plurality of locations on the outer peripheral surface of the second hollow tube, and protrudes to substantially the same length on the radially outer side of the second hollow tube. The oil supply structure for a rotating shaft according to claim 1, wherein the oil supply structure is a protrusion formed so as to be in contact with the inner peripheral surface. A first inner protrusion formed of a pair of protrusions formed symmetrically with respect to the first hollow tube on the inner peripheral surface of the first hollow tube;
A first pair of protrusions formed symmetrically with respect to the first hollow tube at a position away from the protruding position of the first inner protrusion in the axial direction of the first hollow tube. 2 inner protrusions,
The first and second inner protrusions are configured so that a direction of a straight line connecting the second inner protrusions is relative to a direction of a straight line connecting the first inner protrusions. 3. The oil supply structure for a rotating shaft according to claim 2, wherein the oil supplying structure is formed at a position that is rotated by approximately 90 [deg.] Around the axis. A first outer protrusion formed of a pair of protrusions formed symmetrically with respect to the second hollow tube on the outer peripheral surface of the second hollow tube;
A first pair of protrusions formed symmetrically with respect to the second hollow tube at a position away from the protruding position of the first outer protrusion in the axial direction of the second hollow tube. Two outer protrusions,
The first and second outer protrusions are configured such that the direction of a straight line connecting the second outer protrusions is relative to the direction of a straight line connecting the first outer protrusions. 4. The oil supply structure for a rotary shaft according to claim 3, wherein the oil supply structure is formed at a position that is rotated by approximately 90 [deg.] Around the axis.

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