JP5848688B2 - Lubricating structure of driving force transmission device - Google Patents

Description

  The present invention relates to a lubrication structure that lubricates elements constituting a driving force transmission device in a driving force transmission device that transmits driving force from a driving source.

  A driving force transmission device such as an automatic transmission provided in an automobile includes, for example, a gear or a clutch (friction engagement element) that shifts and outputs a driving force from an input shaft (rotating shaft) as disclosed in Patent Document 1, for example. A transmission mechanism is provided. In such a driving force transmission device, a hollow shaft oil passage extending in the axial direction is provided inside the input shaft as an oil passage for guiding lubricating oil (oil) to each part of the transmission mechanism, and a radial direction from the shaft oil passage. A plurality of radial oil passages (oil holes) penetrating to the outer side are formed. Then, along with the rotation of the input shaft, the lubricant oil is led out (scattered) from the plurality of radial oil passages through the shaft oil passage and the plurality of radial oil passages of the input shaft. Lubricating oil derived from this radial oil passage passes through the lubricating oil passage formed in the gap between the components constituting the clutch and gear installed on the outer diameter side of the input shaft, for example, each part of the transmission mechanism, for example, It is supplied to a bearing (bearing), a fitting portion between the input shaft and the gear, and the like, and also supplied to a friction engagement element such as a clutch.

  The flow rate of the lubricating oil supplied to each part of the transmission mechanism and the friction engagement element varies depending on the rotational speed of the input shaft. That is, when the rotation speed (the number of times of driving) of the oil pump increases in accordance with the increase in the rotation speed of the input shaft, the flow rate of the lubricating oil supplied to the shaft oil passage provided inside the input shaft increases. Furthermore, when the centrifugal force accompanying the rotation of the input shaft increases, the flow rate of the lubricating oil that is derived from the radial oil passage of the input shaft and scatters also increases.

  At this time, as the rotational speed of the rotating shaft increases, the flow rate of the lubricating oil led out from the radial oil passage increases rapidly. Exclusion of the oil film from the friction surface is deteriorated, which may lead to a delay in engagement. Even in the non-engaged state, a large amount of lubricating oil flows into the clutch due to an increase in the rotational speed of the rotating shaft, which may lead to dragging of the clutch. Therefore, a means for suppressing an excessive increase in the amount of lubrication accompanying an increase in the rotational speed of the rotating shaft is required.

  Further, the amount of lubricating oil supplied to each part of the transmission mechanism and the friction engagement element also varies depending on the size of the lubricating oil passage formed in the gap between the above-described components. That is, the larger the size of the lubricating oil passage, the larger the flow rate of the lubricating oil flowing through the lubricating oil passage.

JP 2002-81512 A

  However, the size of the lubricating oil passage formed in the gap between the components as described above is determined by the machining dimensions of the components. Therefore, the flow rate of the lubricating oil flowing through the lubricating oil passage only increases unilaterally as the rotational speed of the rotating shaft increases. That is, in the conventional lubrication structure, the passage through which the lubricating oil that has flowed out from the radial oil passage of the input shaft circulates is not provided with a function for adjusting the flow rate of the lubricating oil as the rotational speed of the rotating shaft increases. It was.

  The present invention has been made in view of the above problems, and in a lubrication structure in which lubricating oil is supplied from the inside of the rotating shaft to the outer diameter side by the rotation of the rotating shaft, lubrication accompanying an increase in the number of rotations of the rotating shaft. It is an object of the present invention to provide a lubricating structure for a driving force transmission device that can effectively suppress an excessive increase in the amount of oil.

  In order to solve the above problems, the present invention is configured as follows.

Further, the lubricating structure of the driving force transmission device, the annular member (60) supports the thrust surface of the part (21) for relative rotation with respect to the rotation axis (2) on the rotary shaft (2) member It may be. For the section material having the ability to support the thrust surfaces of the parts relative rotation and mounted on a rotary shaft which conventional transmission mechanism comprises, according to the arrangement of the present invention, the thrust surface on the member In addition to the function of supporting the oil, a function of adjusting the flow rate of the lubricating oil flowing out from the radial oil passage of the rotating shaft can be added. Therefore, it is possible to provide a lubrication structure capable of optimizing the flow rate of the lubricating oil while keeping the number of parts of the driving force transmission device small and simplifying the configuration.

  According to such a configuration, in the lubricating structure in which the lubricating oil is supplied from the inside of the rotating shaft to the outer diameter side by the rotation of the rotating shaft, the lubricating oil is led out from the lubricating oil passage and lubricated as the rotational speed of the rotating shaft increases. It is possible to suppress an increase in the flow rate of the lubricating oil that is supplied to a place that requires a more than necessary. Therefore, it is possible to effectively prevent problems such as malfunction due to excessive supply of lubricant at the supply destination of lubricant derived from the lubricant passage. In addition, by appropriately setting the initial flow area of the lubricating oil passage (the area in which the flow area is not reduced by the flow rate adjusting member) and the urging force of the urging means, the rotational speed of the rotating shaft can be reduced. It is possible to adjust the flow rate of the lubricating oil to each of the corresponding elements.

  In the lubrication structure for the driving force transmission device, the annular member (60) supports the thrust surface of the component (21) that rotates relative to the rotation shaft (2) on the rotation shaft (2). It may be a washer. The thrust washer installed on the rotating shaft provided in the conventional speed change mechanism is a component having only a function of supporting the thrust surface of the relatively rotating component installed on the rotating shaft. Accordingly, in addition to the function of supporting the thrust surface on the thrust washer, it is possible to add a function of adjusting the flow rate of the lubricating oil discharged from the radial oil passage of the rotating shaft. Therefore, it is possible to provide a lubrication structure capable of optimizing the flow rate of the lubricating oil while keeping the number of parts of the driving force transmission device small and simplifying the configuration.

  In the lubricating structure of the driving force transmission device, the flow rate adjusting member (63) is disposed in a slit (69) extending radially inward from the outer peripheral surface (65c) of the main body (65). A flat plate portion (63a) and a protruding piece (63b) protruding in the axial direction of the rotating shaft (2) on the inner diameter side of the plate portion (63a) are integrally provided, and the urging means (67) The coil spring (67) is disposed between the main body (65) and the projecting piece (63b) and is disposed in the groove (61a, 62a) provided in the main body (65). ) Is compressed to a predetermined value or more, the coil spring (67) is compressed, and the plate portion (63a) of the flow rate adjusting member (63) is moved from the outer peripheral surface (65c) of the main body (65) to the lubricating oil passage (90). ) May protrude.

  According to this, it is possible to realize a flow rate adjusting mechanism capable of adjusting the opening degree of the lubricating oil passage by the centrifugal force generated by the rotation of the rotating shaft with a simple configuration with a reduced number of parts. In addition, since the plate portion of the flow rate adjusting member is configured to protrude from the outer peripheral surface of the main body portion of the annular member to the lubricating oil passage, the lubricating oil passage is circulated when the rotational speed of the rotating shaft exceeds a predetermined value. It is possible to reliably suppress an increase in the flow rate of the lubricating oil.

  In the lubricating structure of the driving force transmission device, the friction material (81a, 81b) provided between the clutch inner (42) and the clutch outer (85) disposed on the outer peripheral side of the rotating shaft (2) is provided. And a lubricating oil passage (90) formed in a gap between the outer peripheral surface (65c) of the annular member (60) and the inner peripheral surface (42c) of the clutch inner (42). In this case, the lubricating oil that has passed through the lubricating oil passage (90) may be guided to the friction material (81a, 81b).

  According to such a configuration, with the lubricating structure according to the present invention, it is possible to optimize the amount of lubricating oil with respect to the friction material of the clutch that should suppress excessive supply of lubricating oil when the rotating shaft rotates at high speed. It becomes. Therefore, it is possible to avoid deterioration of the oil film removal from the friction surface during the clutch engagement process when performing a shift by the transmission mechanism, and to prevent a delay in engagement. Further, when the clutch is in a non-engaged state, a large amount of lubricating oil can be prevented from flowing into the clutch due to an increase in the rotational speed of the rotating shaft, and the drag of the clutch can be effectively prevented.

  In addition, the code | symbol in said parenthesis shows the code | symbol of the component in embodiment mentioned later as an example of this invention.

  According to the lubricating structure of the driving force transmission device according to the present invention, in the lubricating structure in which the lubricating oil is supplied from the inside of the rotating shaft to the outer diameter side by the rotation of the rotating shaft, the amount of lubricating oil accompanying the increase in the rotational speed of the rotating shaft is increased. Excessive increase can be effectively suppressed.

It is a sectional side view which shows the structural example of the driving force transmission apparatus which concerns on embodiment of this invention. It is a figure which shows the path | route through which the lubricating oil in a driving force transmission device flows. It is a sectional side view which shows a thrust washer. It is a disassembled perspective view which shows the component of a thrust washer. It is a figure for demonstrating operation | movement of the flow volume adjustment mechanism which a thrust washer has. It is a figure for demonstrating operation | movement of the flow volume adjustment mechanism which a thrust washer has.

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

  FIG. 1 is a side sectional view showing a configuration example of a driving force transmission device including a lubrication structure according to an embodiment of the present invention. FIG. 2 is a diagram showing a path through which the lubricating oil flows in the driving force transmission device, and is a partially enlarged view of a portion X in FIG. The driving force transmission device shown in FIG. 1 is an input shaft (rotary shaft) 2 provided in an automatic transmission mounted on a vehicle and a part of the periphery thereof. The input shaft 2 shown in the figure is rotated by a driving force from a driving source such as an engine. The input shaft 2 is formed with a hollow shaft oil passage 3 extending in the axial direction inside the input shaft 2 and a plurality of radial oil passages 3a to 3g penetrating radially outward from the shaft oil passage 3. ing. Lubricating oil is introduced into the shaft oil passage 3 of the input shaft 2 from the space surrounded by the casing 10 and the plate 20. The lubricating oil introduced into the shaft oil passage 3 of the input shaft 2 opens on the outer peripheral side surface of the input shaft 2 through the plurality of radial oil passages 3 a to 3 g from the shaft oil passage 3 as the input shaft 2 rotates. Are discharged from the openings of the radial oil passages 3a to 3g. In the description of FIGS. 1 and 2, the axial direction refers to the axial direction of the input shaft 2.

  The ball bearing 30 is fixed to the casing 10 that is a member on the fixed side, and rotatably supports the end of the input shaft 2. The clutch gear (input gear) 40 is installed on the input shaft 2, and external teeth are formed on the outer periphery. A needle bearing 21 is interposed between the clutch gear 40 and the input shaft 2, and the clutch gear 40 can rotate relative to the input shaft 2. A retainer 21 a of the needle bearing 21 is installed on one end face of the clutch gear 40. A cage 21 b of the needle bearing 21 is also interposed between the other end surface of the clutch gear 40 and the protruding portion 2 a of the input shaft 2.

  A thrust washer 60 is fixed by spline fitting at a position adjacent to the clutch gear 40 on the input shaft 2. The thrust washer 60 is a member that supports the thrust surface (rolling surface) of the cage 21 a of the needle bearing 21 that relatively rotates on the input shaft 2. Further, another gear (output gear) 50 is installed at a position adjacent to the clutch gear 40 on the input shaft 2. The gear 50 is splined to the outer periphery of the input shaft 2.

  The clutch 80 includes a clutch inner (gear hub) 42 that is integral with the clutch gear 40, a clutch outer 85 that is disposed opposite to the outer diameter side of the clutch inner 42, and a plurality of friction members 81a that are attached to the clutch outer 85 side. And a plurality of other friction materials 81b attached to the clutch inner 42 side, and a friction engagement type engagement element in which the plurality of friction materials 81a and the friction materials 81b are alternately stacked along the axial direction. The clutch 80 includes a pressure plate 82 that can move in the axial direction by the hydraulic pressure of the piston chamber 94, and a coil spring 92 that is interposed between the pressure plate 82 and a locking member 91 installed on the input shaft 2. . When hydraulic pressure is applied to the piston chamber 94, the pressure plate 82 moves toward the friction materials 81a and 81b against the biasing force of the coil spring 92, thereby pressing the friction materials 81a and 81b in the axial direction. ing. Accordingly, the friction members 81 a and 81 b are engaged with each other, and the clutch inner 42 and the clutch gear 40 are locked with respect to the clutch outer 85.

  When the pressure plate 82 presses the friction materials 81a and 81b in the axial direction, the rotational force transmitted to the clutch gear 40 meshing with the input side gear (not shown) is applied to the friction materials 81a and 81 of the clutch inner 42 and the clutch 80. It is transmitted to the clutch outer 85 via 81b and transmitted to the input shaft 2 to which the clutch outer 85 is fixed. The rotational force of the input shaft 2 is transmitted to the gear 50 that is spline-fitted to the input shaft 2 and is output to an output gear (not shown) that meshes with the gear 50.

  The clutch 80 is a wet friction engagement element to which lubricating oil is supplied from the input shaft 2 side. The clutch inner (gear hub) 42 is formed with a plurality of oil holes 42a for guiding lubricating oil to the friction materials 81a and 81b. Therefore, as shown in FIG. 2, the lubricating oil derived from the radial oil passages 3 a and 3 c of the input shaft 2 passes from the gap between the thrust washer 60 and the clutch gear 40 to the gap between the thrust washer 60 and the clutch inner 42. Through the formed lubricating oil passage 90, the oil is introduced into the oil hole 42a of the clutch inner 42, and is guided from the oil hole 42a to the friction materials 81a and 81b.

  Of the plurality of radial oil passages 3a to 3g provided on the input shaft 2 shown in FIG. 1, the radial oil passages 3a and 3b and the radial oil passages 3c and 3d are mainly friction materials 81a and 81b of the clutch 80. And a lubricating oil supply passage for supplying lubricating oil to the needle bearing 21. The radial oil passage 3 e is a lubricating oil supply passage for supplying lubricating oil to the needle bearing 21. The radial oil passage 3 f is a lubricating oil supply passage for supplying lubricating oil to the spline fitting portion 50 a of the gear 50, and the radial oil passage 3 g is for supplying lubricating oil to the ball bearing 30. Lubricating oil supply path.

  In the lubrication structure of the present embodiment, the thrust washer 60 is provided with a flow rate adjusting mechanism for adjusting the flow rate of the lubricating oil flowing through the lubricating oil passage 90. Hereinafter, the configuration of the thrust washer 60 having the flow rate adjusting mechanism will be described with reference to FIGS. 3 and 4. FIG. 3 is a side sectional view showing the thrust washer 60. FIG. 4 is an exploded perspective view showing components of the thrust washer 60.

  As shown in FIGS. 3 and 4, the thrust washer 60 is installed on the input shaft 2 and rotates with the circular annular main body 65 (washer base 61 and washer cover 62) integrally with the input shaft 2, A flow rate adjusting plate (flow rate adjusting member) 63 that is provided so as to be movable in the radial direction with respect to the main body 65 and can adjust the opening degree of the lubricating oil passage 90, and between the main body 65 and the flow rate adjusting plate 63. And a coil spring (biasing means) 67 that urges the flow rate adjusting plate 63 toward the inner side in the radial direction. The main body 65 includes a circular annular washer base 61 having a shaft hole 61d with spline teeth 61e formed on the inner peripheral surface thereof, and a washer cover 62 installed over one end surface of the washer base 61. In this structure, the washer base 61 and the washer cover 62 are overlapped and fixed together by fastening bolts 68 (see FIG. 3). In FIG. 4, the bolt 68 is not shown. The washer base 61 and the washer cover 62 are formed with groove portions 61a and 62a for accommodating a protruding piece 63b of a flow rate adjusting plate 63 and a coil spring 67, which will be described later. Further, in a state where the washer base 61 and the washer cover 62 are overlapped with each other, a slit 69 (see FIG. 3) described later is formed in the gap therebetween.

  The flow rate adjusting plate 63 includes a plate portion 63a formed in a substantially arc-shaped flat plate shape, and a protruding piece 63b protruding in the axial direction of the input shaft 2 on the inner diameter side of the plate portion 63a. The protruding piece 63b has a tip bent at a substantially right angle in the axial direction, and an abutting portion 63d for abutting one end of the coil spring 67 on the inner surface of the tip is provided. The plate portion 63a is disposed in a slit 69 that extends from the outer peripheral surface 65c of the main body portion 65 of the thrust washer 60 toward the inside in the radial direction.

  The coil spring 67 is disposed in groove portions 61a and 62a provided in the washer base 61 and the washer cover 62 (main body portion 65), and is installed between the main body portion 65 and the protruding piece 63b. When the rotational speed of the input shaft 2 exceeds a predetermined value, the flow rate adjusting plate 63 moves against the urging force of the coil spring 67 due to the centrifugal force generated by the rotation of the input shaft 2, and the outside of the plate portion 63a. The peripheral edge 63c and the vicinity thereof protrude from the outer peripheral surface 65c of the main body 65 to the lubricating oil passage 90, so that a part of the lubricating oil passage 90 (a part on the inner diameter side) is closed. Yes. At the position where the protruding piece 63b comes into contact with the stopper portion 62g provided at the inner diameter end of the groove portion 62a in the washer cover 62, the movement of the flow rate adjusting plate 63 outward in the radial direction is stopped.

  A plurality of the flow rate adjusting plates 63 and the coil springs 67 having the above-described configuration are installed at equal intervals along the circumferential direction of the thrust washer 60 (four at 90 ° intervals in the figure) (see FIG. 5). In FIG. 4, only one of the four flow rate adjustment plates 63 and the coil springs 67 is illustrated, and the others are not illustrated. The plate portions 63a of the respective flow rate adjusting plates 63 are formed in an arc shape that is continuous with each other in the circumferential direction along the outer peripheral surface of the thrust washer 60, and the plate portions 63a of the respective flow rate adjusting plates 63 are formed in the thrust direction. The lubricating oil passage 90 is arranged in the entire peripheral area located on the outer periphery of the washer 60.

  Lubricating oil flowing through the shaft oil passage 3 of the input shaft 2 is derived from the radial oil passages 3a and 3c as shown by arrows in FIG. Part of this lubricating oil is supplied to the needle bearing 21 of the clutch gear 40, and the other part passes through the lubricating oil passage 90 from the gap between the thrust washer 60 and the clutch gear 40, and the friction materials 81 a and 81 b of the clutch 80. Led to.

  Here, the operation of the flow rate adjusting mechanism provided in the thrust washer 60 will be described. 5 and 6 are diagrams for explaining the operation of the flow rate adjusting mechanism. FIG. 5 is a cross-sectional view of the thrust washer 60. FIG. 6 is a partially enlarged cross-sectional view showing a part of the lubricating oil passage 90 and the clutch 80. FIG. When the input shaft 2 rotates, the thrust washer 60 that is spline-fitted on the input shaft 2 rotates integrally. Along with the rotation of the thrust washer 60, a centrifugal force Fc acts on the flow rate adjustment plate 63 in the radial direction of the input shaft 2. This centrifugal force Fc is expressed as Fc = mc · r · ω · ω (ω = 2πNs / 60). mc is the mass of the flow rate adjusting plate 63, r is the distance from the center line of the input shaft 2 to the center of gravity of the flow rate adjusting plate 63, and ω is the angular velocity of the input shaft 2. Further, it is expressed as Fspg = kδ. k represents a spring constant of the coil spring 67, and δ represents a deformation amount (compression deformation amount) of the coil spring 67.

When the centrifugal force Fc is smaller than the urging force Fspg of the coil spring 67 (Fc <Fspg), the plate part 63a of the flow rate adjusting plate 63 is slit as shown in FIGS. It is held at a position retracted in 69. In this case, an opening area S of the lubricating oil passage 90 (a cross-sectional area of a portion of the lubricating oil passage 90 that is not blocked by the plate portion 63a of the flow rate adjusting plate 63) is S = S ₀ (maximum area). ing.

In this state, when the rotational speed of the input shaft 2 increases, the centrifugal force Fc acting on the flow rate adjusting plate 63 in the radial direction of the input shaft 2 also increases. When the rotational speed of the input shaft 2 is equal to or higher than the predetermined rotational speed, the centrifugal force Fc is larger than the urging force Fspg of the coil spring 67 (Fc> Fspg). Then, as shown in FIGS. 5B and 6B, the flow rate adjusting plate 63 moves radially outward in the slit 69, and the outer peripheral edge 63 c of the plate portion 63 a is the outer peripheral surface of the main body 65. Projects outward from 65c. As a result, the opening area S of the lubricating oil passage 90 is widened (increased) by the portion blocked by the plate portion 63a of the flow rate adjusting plate 63, so that the area S ₁ narrower than the opening area So in the case of Fc <Fspg. (S ₀ > S ₁ ). Furthermore, as the rotational speed of the input shaft 2 increases, the centrifugal force Fc further increases and the opening area S becomes further narrower.

  As described above, when the rotational speed of the input shaft 2 increases, the flow rate adjusting plate 63 moves to the outer diameter side against the urging force of the coil spring 67, thereby reducing the opening area S of the lubricating oil passage 90. Therefore, as the rotational speed of the input shaft 2 increases, the flow rate of the lubricating oil passing through the lubricating oil passage 90 is limited, and an increase in the amount of lubricating oil supplied to the friction materials 81a and 81b of the clutch 80 is suppressed.

  As described above, the lubrication structure provided in the driving force transmission device of the present embodiment includes the hollow shaft oil passage 3 formed in the input shaft 2 and the radial direction penetrating from the shaft oil passage 3 to the outside in the radial direction. An oil passage 3a; a thrust washer 60 having a circular annular outer peripheral surface 65c installed on the input shaft 2; and a clutch inner 42 having a circular annular inner peripheral surface 42c provided on the outer diameter side of the thrust washer 60. The lubricating oil derived from the radial oil passage 3c by the rotation of the input shaft 2 passes through the lubricating oil passage 90 formed in the gap between the outer peripheral surface 65c of the thrust washer 60 and the inner peripheral surface 42c of the clutch inner 42, and the clutch. The lubrication structure is supplied to 80 friction materials 81a and 81b.

  The thrust washer 60 is installed on the input shaft 2 and rotates integrally with the input shaft 2, and is provided so as to be movable along the radial direction with respect to the main body 65. A flow rate adjusting plate 63 capable of adjusting the flow rate of the lubricating oil flowing through 90, and a coil that is interposed between the main body 65 and the flow rate adjusting plate 63 and biases the flow rate adjusting plate 63 inward in the radial direction. And the flow rate adjusting plate 63 moves toward the closing of the lubricating oil passage 90 against the urging force of the coil spring 67 by the centrifugal force generated by the rotation of the input shaft 2. The area S is reduced, and an increase in the flow rate of the lubricating oil flowing through the lubricating oil passage 90 is suppressed.

With such a configuration, it is possible to suppress an unnecessarily increase in the flow rate of the lubricating oil derived from the lubricating oil passage 90 as the rotational speed of the input shaft 2 increases. Therefore, it is possible to effectively prevent problems such as malfunction due to excessive supply of the lubricating oil in the clutch 80 that is the supply destination of the lubricating oil led out from the lubricating oil passage 90. Further, by appropriately setting the size of the opening area S (S ₀ ) in the initial stage of the lubricating oil passage 90 (not closed by the flow rate adjusting plate 63), the biasing force of the coil spring 67, and the like, the input shaft 2 Even when the number of rotations increases, an optimal flow rate of lubricating oil from the lubricating oil passage 90 to the clutch 80 can be ensured. Therefore, an excessive increase in the amount of lubricating oil accompanying an increase in the rotational speed of the input shaft 2 can be effectively suppressed.

  In the above embodiment, the flow rate of the lubricating oil flowing through the lubricating oil passage 90 is adjusted to the thrust washer 60 that supports the thrust surface of the cage 21 a of the needle bearing 21 that rotates relative to the input shaft 2. A flow rate adjusting mechanism is provided. The thrust washer installed on the rotating shaft of the conventional speed change mechanism is a component having only the function of supporting the thrust surface of the relatively rotating component installed on the rotating shaft. The thrust washer 60 has a function of adjusting the flow rate of the lubricating oil that has come out of the radial oil passage 3c in addition to the function of supporting the thrust surface of the cage 21a (clutch gear 40) of the needle bearing 21. . Therefore, the lubrication structure is capable of optimizing the flow rate of the lubricating oil supplied to the clutch 80 while reducing the number of parts of the driving force transmission device (transmission) and reducing the number of parts.

  In the lubrication structure of the driving force transmission device, the flow rate adjusting plate 63 includes a flat plate portion 63a disposed in a slit 69 formed in the main body portion 65 of the thrust washer 60, and the plate portion 63a. A projecting piece 63b connected to the inner diameter side and projecting in the axial direction of the input shaft 2 is integrally provided, and the coil spring 67 is disposed in the groove portions 61a and 62a provided in the main body portion 65 so as to project from the main body portion 65. It is installed between the piece 63b. When the rotational speed of the input shaft 2 exceeds a predetermined value, the coil spring 67 is compressed, and the plate portion 63a of the flow rate adjusting plate 63 is configured to protrude from the outer peripheral surface 65c of the main body portion 65 to the lubricating oil passage 90. ing.

  According to this, a flow rate adjusting mechanism capable of adjusting the opening degree of the lubricating oil passage 90 by the flow rate adjusting plate 63 by the centrifugal force generated by the rotation of the input shaft 2 can be realized with a simple configuration with a reduced number of parts. Further, since the plate portion 63a of the flow rate adjusting plate 63 is configured to protrude from the outer peripheral surface 65c of the main body portion 65 to the lubricating oil passage 90, when the rotational speed of the input shaft 2 exceeds a predetermined value, the lubricating oil An increase in the flow rate of the lubricating oil flowing through the passage 90 can be reliably suppressed.

  In particular, in the clutch 80, if the lubricating oil is excessively supplied when the friction materials 81a and 81b are engaged, the oil film evacuation performance deteriorates on the friction surfaces of the friction materials 81a and 81b, resulting in a delay in engagement. In addition, even when the clutch 80 is not engaged, excessive supply of lubricating oil leads to dragging of the clutch 80 as the rotational speed of the rotating shaft increases. Therefore, in the lubrication of the friction materials 81a and 81b of the clutch 80, it is required to suppress excessive supply of lubricating oil at the time of high rotation. On the other hand, the lubricating structure of the present embodiment is configured such that when the rotational speed of the input shaft 2 increases, the flow rate of the lubricating oil guided to the clutch 80 via the lubricating oil passage 90 is limited accordingly. When the input shaft 2 rotates at a high speed, excessive supply of lubricating oil to the friction members 81a and 81b of the clutch 80 can be effectively suppressed.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the claims and the technical idea described in the specification and drawings. Can be modified. For example, in the above embodiment, the case where the thrust washer 60 installed on the input shaft 2 is provided with the flow rate adjusting mechanism for adjusting the flow rate of the lubricating oil flowing through the lubricating oil passage 90 has been described. The parts provided with are not limited to the thrust washer described above, and may be other types of parts installed on the rotating shaft (for example, rotating parts such as bearings and gears).

  In the above embodiment, the lubricating oil passage that is provided in the gap between the thrust washer and the clutch inner is shown as the lubricating oil passage that adjusts the flow rate by the flow rate adjusting mechanism provided in the thrust washer 60. As long as the lubricating oil flowing out from the radial oil passage of the rotating shaft circulates, the lubricating oil passage is not limited to the above-described lubricating oil passage, and may be a lubricating oil passage provided in a gap between other components.

  Further, in the above embodiment, the friction materials 81a and 81b of the clutch 80 are cited as the supply destination of the lubricating oil that has passed through the lubricating oil passage 90. Other elements such as a clutch and a brake may be used.

  Further, a general transmission includes a plurality of shafts (shafts), for example, a main shaft connected to an engine crankshaft (engine output shaft), a motor output shaft, and the like, and secondary shafts parallel to the main shaft. An idle shaft, a reverse shaft (reverse shaft), and the like are provided, but the flow rate adjusting mechanism having the above-described configuration can be provided for components such as a thrust washer installed on any of these shafts.

DESCRIPTION OF SYMBOLS 1 Transmission mechanism 2 Input shaft 3 Shaft oil path 3a-3g Radial direction oil path 21 Needle bearing 30 Ball bearing 40 Clutch gear 42 Clutch inner 42a Oil hole 42c Inner peripheral surface 50 Gear 60 Thrust washer 61 Washer base 61a Groove part 61d Shaft hole 61e Spline teeth 62 Washer cover 62a Groove 62g Stopper 63 Flow rate adjustment plate (flow rate adjustment member)
63a Plate part 63b Projection piece 63c Outer peripheral edge 63d Abutting part 65 Main part 65c Outer peripheral surface 67 Coil spring (biasing means)
68 Bolt 69 Slit 80 Clutch 81a Friction material 81b Friction material 82 Pressure plate 85 Clutch outer 90 Lubricating oil passage 91 Locking member 92 Coil spring 94 Piston chamber

Claims (4)

A rotating shaft that rotates by a driving force from a driving source;
A speed change mechanism that shifts and outputs the rotation by the driving force from the drive source;
A hollow shaft oil passage extending in the axial direction inside the rotating shaft;
A radial oil passage penetrating radially outward from the axial oil passage;
An annular member having an annular outer peripheral surface installed on the rotating shaft;
And another member having an annular inner peripheral surface provided on the outer diameter side of the annular member,
Lubricating oil derived from the radial oil passage by rotation of the rotating shaft passes through the lubricating oil passage formed in the gap between the outer peripheral surface of the annular member and the inner peripheral surface of the other member, and the transmission mechanism Including a lubrication structure of a driving force transmission device supplied to a location requiring lubrication,
The annular member is
A main body that is installed on the rotating shaft and rotates integrally with the rotating shaft, and a flow rate of the lubricating oil that is provided so as to be movable along the radial direction with respect to the main body and that flows through the lubricating oil passage is adjusted. A possible flow rate adjusting member, and an urging means interposed between the main body portion and the flow rate adjusting member to urge the flow rate adjusting member toward the inside in the radial direction,
The flow rate adjusting member moves toward the lubricating oil passage against the urging force of the urging means by centrifugal force due to the rotation of the rotating shaft, thereby reducing the flow passage area of the lubricating oil passage, A lubricating structure for a driving force transmission device, characterized in that an increase in the flow rate of lubricating oil flowing through the lubricating oil passage is suppressed. The lubricating structure for a driving force transmission device according to claim 1, wherein the annular member is a member that supports a thrust surface of a component that rotates relative to the rotation shaft on the rotation shaft. The flow rate adjusting member protrudes in the axial direction of the rotary shaft on a flat plate portion disposed in a slit extending inward in the radial direction from the outer peripheral surface of the main body portion, and on the inner diameter side of the plate portion. Providing integrally with the protruding piece,
The biasing means is a coil spring disposed in a groove provided in the main body portion and installed between the main body portion and the protruding piece,
The said coil spring is compressed when the rotation speed of the said rotating shaft becomes more than predetermined, The said plate part of the said flow volume adjustment member protrudes from the outer peripheral surface of the said main-body part to the said lubricating oil channel | path. 3. A lubricating structure for a driving force transmission device according to 1 or 2. A clutch having a friction material provided between the clutch inner and the clutch outer disposed on the outer peripheral side of the rotating shaft;
The lubricating oil passage is a lubricating oil passage formed in a gap between an outer peripheral surface of the annular member and an inner peripheral surface of the clutch inner, and the lubricating oil that has passed through the lubricating oil passage is guided to the friction material. The lubrication structure of the driving force transmission device according to any one of claims 1 to 3.

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