JP5968199B2 - 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.

  An automatic transmission (driving force transmission device) included in an automobile includes a transmission mechanism that shifts and outputs a driving force from an input shaft (rotating shaft) with a gear, and a clutch or the like is provided on the outer diameter side of the gear in the transmission mechanism. Some of the engagement elements (friction engagement elements) are arranged so as to overlap each other in the radial direction. In such a configuration, a hollow shaft oil passage extending in the axial direction as an oil passage for guiding lubricating oil (oil) and a plurality of radial directions penetrating radially outward from the shaft oil passage inside the input shaft An oil passage (oil hole) is formed. As the input shaft rotates, the lubricating oil passes through the shaft oil passages of the input shaft and the plurality of radial oil passages, and is led out (scattered) from the openings of the plurality of radial oil passages. Lubricating oil derived from the radial oil passage is supplied to a bearing (bearing), a fitting portion between the input shaft and the gear, and the like, and is also supplied to a friction engagement element such as a clutch.

  The flow rate of the lubricating oil supplied to each of the above parts 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 diameter dimension of the radial oil passage formed on the input shaft. That is, the larger the radial dimension of the radial oil passage, the greater the amount of lubricating oil derived from the radial oil passage. Therefore, the diameter dimension of each radial oil passage (specifications of each radial oil passage) is determined by the optimal distribution of the lubricating oil amount to be supplied to each part of the transmission mechanism and the friction engagement elements, and every running state of the vehicle. (In other words, it is determined on the assumption of the rotational speed of the input shaft according to the running state).

  Thus, by changing the setting of the radial dimension of the radial oil passage, it is possible to adjust so as to obtain the optimum amount of lubricating oil in each part. However, even in that case, each radial oil passage does not have a function for adjusting the flow rate of the lubricating oil accompanying the increase in the rotational speed of the rotary shaft. Therefore, when the number of rotations of the rotating shaft increases, the amount of lubricating oil in one part may become excessive, or the amount of lubricating oil in another part may become insufficient. As a result, there are concerns about the increase in friction (friction) and drag (rotation resistance) due to the lubricating oil in areas where the amount of lubricating oil is excessive. The risk of seizure increases.

  Patent Document 1 discloses an oil drain plug used for an oil pan of an automobile engine. In this oil drain plug, a normally closed valve is built in a through hole provided as an oil drain passage, and this normally closed valve is opened by assembling a dedicated jig for oil drain, and the oil in the oil pan is negatively pressurized. I try to suck it out.

  However, the oil drain plug described in Patent Document 1 is configured only to open the normally closed valve and drain the oil in the oil pan by assembling a dedicated jig for oil drain, It is not configured to adjust the amount of oil that passes through the hole. Therefore, it cannot be used as a mechanism for adjusting the flow rate of the lubricating oil derived from the radial oil passage provided on the rotating shaft as described above.

Japanese Patent No. 4351747

  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.

The lubricating structure of the driving force transmission device according to the present invention includes a rotating shaft (2) that rotates by a driving force from a driving source, and a speed change mechanism (40, 50, 80), a hollow shaft oil passage (3) extending in the axial direction of the rotation shaft inside the rotation shaft (2), and a radial oil passage (piercing from the shaft oil passage (3) to the outside in the radial direction ( 3a to 3g), and a transmission mechanism (40, 50, 80) in which lubricating oil derived from the radial oil passages (3a to 3g) by rotation of the rotating shaft (2) is installed on the outer peripheral side of the rotating shaft ) Including a flow rate adjusting valve (100) installed in the radial oil passage (3c), and the flow rate adjusting valve (100) A main body (110) having a hollow cylindrical housing (116) extending in the axial direction of the radial oil passage (3c); Cylindrical side wall portion (131) and a circular plate-shaped bottom wall (132) and is formed into a bottomed cylindrical housing portion (116) in slidably to the axial direction of the radial oil passage having An installed valve body (130), an oil inflow hole (113) formed in a side surface of the main body (110) and penetrating through the housing (116), and an urging means (120) for urging the valve body the provided, oil inflow hole by moving in the axial direction of the radial oil passage against the biasing force of the valve body by a centrifugal force (130) biasing means (120) by rotation of the rotary shaft (2) ( 113), the area of the radial oil passage (3c) through which the lubricating oil flows is reduced and the portion of the radial oil passage (3c) through which the lubricating oil flows is reduced, and is led out from the radial oil passage (3c). This is characterized in that an increase in the flow rate of the lubricating oil is suppressed.

  According to such a structure, it can suppress that the flow volume of the lubricating oil derived | led-out from a radial direction oil path increases more than needed with the increase in the rotation speed of a rotating shaft. Therefore, it is possible to effectively prevent problems such as malfunction due to excessive supply of the lubricating oil at the supply destination of the lubricating oil derived from the radial oil passage. In addition, by appropriately setting the size of the initial channel area (the area of the channel that has not been reduced because it is blocked by the valve body) and the biasing force of the biasing means, etc. In addition, it is possible to adjust the flow rate of the optimum lubricating oil to each element.

  In the lubricating structure of the driving force transmission device, the speed change mechanism includes a friction engagement element (80) disposed on the outer peripheral side of the rotating shaft (2), and a diameter on which the flow rate adjusting valve (100) is installed. The directional oil passage (3c) may be a radial oil passage for supplying lubricating oil to the friction engagement element (80). According to such a configuration, with the regulating valve according to the present invention, it is possible to optimize the amount of lubricating oil with respect to the friction engagement element for which excessive supply of lubricating oil is desired to be suppressed when the rotating shaft rotates at a high speed. Become. Accordingly, it is possible to avoid deterioration of the oil film removal from the friction surface during the engagement of the friction engagement element when performing a shift by the transmission mechanism, and to prevent a delay in engagement. In addition, when the friction engagement element is in a non-engagement state, it is possible to prevent a large amount of lubricating oil from flowing into the friction engagement element due to an increase in the rotational speed of the rotating shaft, thereby effectively preventing dragging of the friction engagement element. it can.

  In the lubricating structure of the driving force transmission device, a plurality of radial oil passages (3a to 3g) are provided on the rotating shaft (2), and the plurality of radial oil passages (3a to 3g) are provided. The flow regulating valve (100) may be provided in whole or in part. According to such a configuration, the radial dimensions of the plurality of radial oil passages provided on the rotating shaft are processed so as to be the same, and the present invention is applied only to a portion where adjustment of the flow rate of the lubricating oil is necessary. A regulating valve may be installed. Accordingly, it is possible to optimize the flow rate of the lubricating oil for the portion requiring lubrication while simplifying the machining process, reducing the number of work steps, and reducing the cost in manufacturing the rotating shaft.

  In the lubrication structure of the driving force transmission device, the flow rate adjusting valve (100) includes a cylindrical main body (110) in which the urging means (120) and the valve body (130) are installed. The outer peripheral surface of the part (110) and the inner peripheral surface of the radial oil passages (3a to 3g) may be formed with threads and screw grooves that are screwed together. According to such a configuration, the adjustment valve can be attached to the radial oil passage simply by screwing the plug into the radial oil passage. Therefore, the adjustment valve can be installed efficiently according to the present invention. It becomes possible.

  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 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 lubricating oil flows in a driving force transmission apparatus. FIG. 3 is a partial enlarged cross-sectional view of a radial oil passage and its periphery in an input shaft of a driving force transmission device. It is a sectional side view which shows the structural example of an oil quantity adjustment plug. It is a disassembled perspective view which shows the component of an oil quantity adjustment plug. It is a figure for demonstrating operation | movement of an oil quantity adjustment plug.

  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 according to an embodiment of the present invention. FIG. 2 is a diagram illustrating a path through which the lubricating oil flows in the driving force transmission device. In the automatic transmission (driving force transmission device) 1 shown in FIGS. 1 and 2, an input shaft (rotating shaft) 2 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. As shown in FIG. 2, the 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 interposed between the thrust washer 11 fixed to the input shaft 2 by spline fitting and 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. 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 an oil hole 42a for guiding lubricating oil to the friction materials 81a and 81b. Accordingly, the lubricating oil derived from the radial oil passage 3c of the input shaft 2 passes through the gap between the thrust washer 11 and the clutch gear 40 and the gap between the thrust washer 11 and the clutch inner 42, and then the oil hole of the clutch inner 42 42a is introduced into the friction material 81a, 81b from the oil hole 42a.

  Of the plurality of radial oil passages 3 a to 3 g provided on the input shaft 2, the radial oil passages 3 a and 3 b and the radial oil passages 3 c and 3 d mainly include the friction materials 81 a and 81 b of the clutch 80 and the needle bearing 21. This is a lubricating oil supply passage for supplying lubricating oil to the tank. 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 lubricating structure of the present embodiment, an oil amount adjusting plug (flow rate adjusting valve) 100 for adjusting the flow rate of the lubricating oil flowing through the radial oil passage 3c is installed in the radial oil passage 3c. Yes. Hereinafter, the configuration of the oil amount adjusting plug 100 will be described with reference to FIGS. FIG. 3 is a partial enlarged cross-sectional view (partial enlarged view of a portion X in FIG. 1) of the radial oil passage 3c and its periphery in the input shaft 2 of the driving force transmission device. FIG. 4 is a side sectional view showing a configuration example of the oil amount adjusting plug 100. FIG. 5 is an exploded perspective view showing components of the oil amount adjustment plug 100.

  As shown in FIGS. 4 and 5, the oil amount adjusting plug 100 includes a cylindrical plug body (main body portion) 110, a coil spring (biasing means) 120, and a cap (valve body) 130. Yes. As shown in FIGS. 3 to 5, the plug main body 110 has a substantially cylindrical shape, and includes a head 111 constituting an upper portion in the axial direction (upper half portion shown in FIGS. 3 to 5) and a lower portion in the axial direction. The cylindrical part 112 which comprises (lower half part shown in FIGS. 3-5) is integrally formed. Further, the outer diameter (outer diameter) of the cylindrical portion 112 is configured to be slightly smaller than the outer diameter (outer diameter) of the head 111. A screw thread 111 a is formed on the outer peripheral side surface of the head 111. In addition, a screw groove (not shown) that is screwed into the screw thread 111a is formed on the inner side surface of the radial oil passage 3c.

  A hollow through hole 114 extending in the axial direction is formed in the plug body 110. As shown in FIGS. 4 and 5, two circular oil inflow holes 113 and 113 penetrating from the outside (outer peripheral surface) to the through hole 114 are formed at positions facing each other on the side surface of the cylindrical portion 112. ing.

  The upper end of the through hole 114 and the vicinity thereof are hexagonal holes 115 for inserting a hexagonal tool such as a hexagon wrench, and the lower part of the through hole 114 from the hexagonal hole 115 is a coil spring 120 and a cap. A cylindrical accommodation portion 116 in which 130 is accommodated is formed. The inner diameter of the hexagonal hole 115 (the diameter of the inner circumference of the hexagon) is configured to be smaller than the inner diameter (the diameter of the inner circumference of the circle) of the accommodating portion 116, and the inner diameter of the hexagonal hole 115 and the inner diameter of the accommodating portion 116 are configured. The one end (upper end) of the coil spring 120 housed in the housing portion 116 is locked by the step 117.

  At the lower end portion of the cylindrical portion 112, a crimping portion 118 that is crimped so as to bend the lower end portion inward is provided. In a state where the coil spring 120 and the cap 130 are housed in the housing portion 116, the coil spring 120 and the cap 130 are held so as not to come out of the housing portion 116 by bending the caulking portion 118 inward and crimping.

  The cap 130 is formed in a bottomed cylindrical shape (cup shape) having a cylindrical side wall 131 and a circular flat bottom wall 132. The outer diameter of the side wall 131 in the cap 130 is set to be slightly smaller than the inner diameter of the accommodating portion 116 of the plug main body 110. As a result, the cap 130 is fitted into the accommodating portion 116. The inner diameter of the side wall 131 in the cap 130 is set to be larger than the outer diameter of the coil spring 120. Further, the upper end surface of the cap 130 is opened by the opening 133.

  The assembly of the oil amount adjusting plug 100 having the above-described configuration is performed as follows. First, the coil spring 120 and the cap 130 are accommodated in this order from the opening 119 provided at the lower end of the plug main body 110 (cylindrical portion 112) into the accommodating portion 116. As a result, the opening of the housing portion 116 is closed by the bottom wall portion 132 of the cap 130. Then, the coil spring 120 and the cap 130 are held inside the housing portion 116 by bending the crimping portion 118 provided at the periphery of the opening 119 inward and crimping. At this time, the upper end of the coil spring 120 abuts on the step 117 and is locked. As a result, the coil spring 120 biases the bottom wall portion 132 of the cap 130 downward in the axial direction. For this reason, the cap 130 is locked in a state where the bottom wall portion 132 of the cap 130 is in contact with the crimping portion 118. Further, in a state where the cap 130 is held inside the accommodating portion 116, the side wall portion 131 of the cap 130 covers only a part of the lower side of the oil inflow holes 113, 113, and the remaining oil inflow holes 113, 113 remain. This part (the upper part) is open.

  Next, a process of attaching the oil amount adjustment plug 100 to the radial oil passage 3c of the input shaft 2 will be described. In order to attach the oil amount adjusting plug 100 to the radial oil passage 3c, first, the oil amount adjusting plug 100 is inserted into the radial oil passage 3c from the cylindrical portion 112 side. Next, by rotating a hexagon wrench (not shown) inserted into the hexagonal hole 115 of the oil amount adjusting plug 100, the thread 111a and the radial oil passage 3c provided on the head 111 of the oil amount adjusting plug 100 are rotated. The screw groove provided on the inner surface is screwed together, and the oil amount adjusting plug 100 is made to enter the inside (back side) of the radial oil passage 3c. As shown in FIG. 3, a hex wrench is rotated until the cylinder part 112 of the oil amount adjusting plug 100 protrudes from the inner side surface 4 of the shaft oil passage 3, so that the oil amount adjusting plug 100 is connected to the radial oil passage 3c. To enter inside. Thus, the installation of the oil amount adjustment plug 100 is completed.

  Lubricating oil flowing in the shaft oil passage 3 of the input shaft 2 flows from the oil inflow hole 113 of the oil amount adjusting plug 100 into the accommodating portion 116 and the through hole 114 as indicated by arrows in FIG. The lubricating oil that has flowed into the accommodating portion 116 and the through hole 114 is led out (scattered) from the hexagonal hole 115 to the outside of the oil amount adjusting plug 100. Part of this lubricating oil is supplied to the needle bearing 21, and the other part is guided to the clutch 80 through the gap between the thrust washer 11 and the clutch gear 40.

  Here, the operation of the oil amount adjusting plug 100 will be described. FIG. 6 is a view for explaining the operation of the oil amount adjustment plug 100. When the input shaft 2 rotates, the oil amount adjusting plug 100 inserted in the radial oil passage 3c of the input shaft 2 rotates. As the oil amount adjusting plug 100 rotates, a centrifugal force Fc acts on the cap 130 of the oil amount adjusting plug 100 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 cap 130, r is the distance from the center line of the input shaft 2 to the center of gravity of the cap 130, and ω is the angular velocity of the input shaft 2. Further, it is expressed as Fspg = kδ. k represents the spring constant of the coil spring 120, and δ represents the amount of deformation of the coil spring 120.

When the centrifugal force Fc is smaller than the urging force Fspg by the coil spring 120 (Fc <Fspg), the cap 130 is held at the position where it abuts against the crimping portion 118 and does not move inside the housing portion 116. In this case, the opening area (flow channel area) S of the oil inflow holes 113, 113 (the area of the oil inflow hole 113 that is not blocked by the side wall 131 of the cap 130) is S = S ₀ (maximum Area).

In this state, when the rotational speed of the input shaft 2 increases, the centrifugal force Fc acting on the cap 130 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 by the coil spring 120 (Fc> Fspg). Then, the cap 130 moves to the outside (the head 111 side) along the axial direction (the axial direction of the oil amount adjusting plug 100, that is, the radial direction of the input shaft 2) in the housing portion 116. In this case, since the opening area S of the oil inflow hole 113 is widened (increased) by the portion blocked by the side wall 131 of the cap 130, the area S ₁ (which is narrower than the opening area S ₀ in the case of Fc <Fspg). S ₁ <S ₀ ). Further, the centrifugal force Fc is further increased as the rotational speed of the input shaft 2 is increased, further narrows the opening area S _0.

  As described above, when the rotational speed of the input shaft 2 increases, the cap 130 moves against the urging force of the coil spring 120, so that the opening area S of the oil inflow hole 113 is reduced and the oil amount from the oil inflow hole 113 is reduced. The amount of lubricating oil flowing into the adjustment plug 100 (the accommodating portion 116 and the through hole 114) is reduced. Therefore, as the rotational speed of the input shaft 2 increases, the flow rate of the lubricating oil passing through the oil amount adjusting plug 100 is limited, and an increase in the amount of lubricating oil supplied to the needle bearing 21 and the clutch 80 is suppressed.

  As described above, according to this embodiment, the flow rate of the lubricating oil flowing through the radial oil passage 3c in the radial oil passage 3c of the input shaft 2 is adjusted according to the rotational speed of the input shaft 2. An oil amount adjusting plug 100 is installed. The oil amount adjusting plug 100 moves the cap 130 in the radial oil passage 3 a by closing the oil inflow hole 113 against the urging force of the coil spring 120 by the centrifugal force generated by the rotation of the input shaft 2. The opening area S is reduced, and an increase in the flow rate of the lubricating oil led out from the radial oil passage 3c is suppressed.

According to such a structure, it can suppress that the flow volume of the lubricating oil derived | led-out from the radial direction oil path 3c increases more than needed with the increase in the rotation speed of the input shaft 2. FIG. Therefore, it is possible to effectively prevent problems such as malfunction due to excessive supply of the lubricating oil in the needle bearing 21 and the clutch 80 that are the supply destination of the lubricating oil derived from the radial oil passage 3c. Further, by appropriately setting the size of the initial opening area S (S ₀ ), the biasing force of the coil spring 120, and the like, even when the rotational speed of the input shaft 2 is increased, the radial oil passage 3c is passed to each element. The optimum lubricating oil flow rate 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.

  Further, according to the above-described embodiment, the opening area of the oil inflow hole 113 is obtained by moving the oil amount adjusting plug 100 in the axial direction inside the housing portion 116 with the rotation of the input shaft 2. Since S is configured to decrease, the opening area of the oil inflow hole 113 (the opening area can be changed by changing the diameter and shape of the oil inflow hole 113) S, the side wall portion of the cap 130 By appropriately setting the height dimension of 131, the urging force of the coil spring 120, and the like, even when the rotational speed of the input shaft 2 is increased, it is possible to ensure an optimal flow rate of lubricating oil to each part.

  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. Further, even when the clutch 80 is not engaged, if the lubricant is supplied excessively, dragging is caused by an increase in the number of rotations of the rotating shaft. 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 oil amount adjusting plug 100 according to the present embodiment is configured such that when the rotational speed of the input shaft 2 increases, the supply amount of the lubricating oil is limited accordingly, so that the input shaft 2 is rotated at a high speed. When this occurs, excessive supply of lubricating oil to the friction materials 81a and 81b of the clutch 80 can be effectively suppressed.

  Note that the oil amount adjusting plug 100 shown in the above embodiment is configured such that when the rotational speed of the input shaft 2 increases, the increase in the amount of lubricating oil supplied is limited (suppressed) accordingly. However, as the oil amount adjusting plug 100 according to the present invention, in addition to this, when the rotational speed of the input shaft 2 increases, the supply amount of the lubricating oil increases with an increase in the rotational speed of the normal input shaft 2. It is possible to increase the rate at a rate higher than the rate. That is, although detailed illustration and description are omitted, contrary to the above embodiment, as the rotation of the input shaft 2 increases, the cap 130 moves in the axial direction in the housing portion 116 and the oil inflow hole 113 is removed. It is possible to increase the opening area S. According to such a configuration, not only an increase in friction (friction) and drag due to the lubricating oil with respect to a portion where the supply amount of the lubricating oil becomes excessive as the rotation of the input shaft 2 increases, It is possible to prevent the occurrence of deterioration or seizure due to an excessive temperature rise of the parts with respect to the portion where the amount of the lubricating oil is insufficient with the rotation of 2.

  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 said embodiment, although the case where the oil quantity adjustment plug 100 was installed only in the radial direction oil path 3c was shown among several radial direction oil paths 3a-3g provided in the input shaft 2, in addition to this, The oil amount adjusting plug 100 may also be installed in the other radial oil passages 3a, 3b, 3d to 3g.

  In the above embodiment, as a method for adjusting the amount of lubricating oil in accordance with the rotational speed of the input shaft 2, the opening area of the oil inflow hole 113, the height of the side wall 131 of the cap 130, and the biasing force of the coil spring 120 are adjusted. The strength (spring constant) and the like are arbitrarily set, but these are only examples, and other means such as the axial length of the plug body 110 and the diameter of the through hole 114 are set. You may make it do.

  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 oil amount adjusting plug 100 having the above configuration can be applied to a radial oil passage formed in any of these shafts. The oil amount adjusting plug 100 can also be applied to the radial oil passage formed in the countershaft that forms the output shaft. Further, the position of the radial oil passage in the input shaft 2 and the element to be lubricated can be appropriately changed according to the configuration of the automatic transmission.

1 Automatic transmission (driving force transmission device)
2 Input shaft (rotary shaft)
3 shaft oil passages 3a to 3g radial oil passage 21 needle bearing 30 ball bearing 40 clutch gear 50 gear 80 clutch (friction engagement element)
100 Oil level adjustment plug (regulation valve)
110 Plug body (main body)
120 Coil spring (biasing means)
130 Cap (Valve)

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 of the rotary shaft inside the rotary shaft ;
A radial oil passage penetrating radially outward from the axial oil passage,
A lubricating structure of a driving force transmission device that supplies lubricating oil derived from a radial oil passage by rotation of the rotating shaft to a place where lubrication is required, including the speed change mechanism installed on the outer peripheral side of the rotating shaft,
Comprising a flow regulating valve installed in the radial oil passage;
The flow rate adjusting valve has a bottomed cylindrical shape having a main body portion having a hollow cylindrical housing portion extending in the axial direction of the radial oil passage, a cylindrical side wall portion, and a circular flat bottom wall portion. A valve body formed so as to be slidable in the axial direction of the radial oil passage in the housing portion; an oil inflow hole formed in a side surface of the main body portion and penetrating into the housing portion; and the valve body And a biasing means for biasing
The valve body is blocked by the valve body in the oil inflow hole when the valve body moves in the axial direction of the radial oil passage against the urging force of the urging means by centrifugal force due to rotation of the rotating shaft. Is configured such that the flow passage area through which the lubricating oil flows in the radial oil passage is reduced, and an increase in the flow rate of the lubricating oil derived from the radial oil passage is suppressed. Lubricating structure of the driving force transmission device. The speed change mechanism includes a friction engagement element disposed on an outer peripheral side of the rotating shaft,
The radial oil passage in which the flow rate adjustment valve is installed, the lubrication of the driving force transmission device according to claim 1, wherein a friction radial oil passage for supplying lubricating oil to the coupling elements Construction. The said radial direction oil path is provided with two or more by the said rotating shaft, The said flow volume adjustment valve is provided in all or one part of this plurality of radial direction oil paths. Lubricating structure of the driving force transmission device. 4. The driving force transmission according to claim 2, wherein the outer peripheral surface of the main body and the inner peripheral surface of the radial oil passage are formed with screw threads and screw grooves that are screwed together. 5. Lubrication structure of the device.

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