JP2007024234A - Lubricating device for transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To correct axial imbalance (excessive upstream and short downstream) of lubricating oil in a high-speed rotating state by adding simple constitution in a lubricating device for a transmission for supplying the lubricating oil to a plurality of lubrication required parts in an axial direction around a shaft 9 via a hollow part (an axis part oil passage 41) in the rotating shaft 9. <P>SOLUTION: A pipe 62 arranged to extend from one end side of the shaft 9 to the other end side in the axial direction and fixed is provided in the hollow part, and the pipe 62 is provided with oil holes 72-86 in a plurality of parts to penetrate from the inner peripheral surface to the outer peripheral surface. The lubricating oil is fed into the pipe 62 from the one end side, and the fed lubricating oil flows out into the hollow part via the oil holes and further flows out to the periphery of the shaft 9 through radial oil holes 42-56 of the shaft 9. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a lubricating device that supplies lubricating oil to a plurality of lubricating portions positioned around a rotating shaft in a transmission of an automobile via the shaft.

  As an automobile transmission, a so-called automatic transmission using a planetary gear mechanism is widely used. In this automatic transmission, the rotation of the engine is input to an input shaft via a torque converter, and further shifted by a speed change mechanism including a plurality of planetary gear mechanisms and output to the output shaft. In this type of transmission, the transmission mechanism rotates the input shaft according to a shift position according to a specific gear (sun gear, planetary gear, or ring gear) or carrier (planetary gear) constituting the planetary gear mechanism. In order to transmit the rotation of a specific gear or carrier to an output shaft as appropriate, or to appropriately restrict the rotation of a specific gear or carrier, a plurality of frictional engagements such as clutches and brakes are usually used. It has a combination element. A rotation shaft such as the input shaft or further the output shaft is disposed on the shaft center line of the speed change mechanism. Around the rotation shaft, the gear, the carrier, the friction engagement element, and the friction engagement element are arranged. Rotating bodies such as drums, hubs, and hollow shafts that transmit rotation between the gears above are arranged in a dense and complex manner so as to be folded, and bearings that support these rotating bodies (ball bearings and sliding bearings) Is provided at a plurality of locations.

  And as for the said gear, a friction engagement element, and a bearing, it is necessary to lubricate the rolling part and a sliding part (lubrication required part) with oil, As a conventional lubricating device for that, for example, patent documents 1-1 The one disclosed in No. 3 is general. The basic configuration of this lubricating device is that lubricating oil discharged from an oil pump driven by engine rotation is introduced into a rotating shaft such as the output shaft in the transmission, and a hollow portion in the rotating shaft (hereinafter referred to as the case) Lubrication on the outer peripheral side of the rotating shaft from an oil hole (hereinafter referred to as a branch oil passage) extending in a radial direction from a predetermined position in the longitudinal direction of the axial center oil passage. It is the structure supplied to a part.

In addition, the apparatus of patent document 1 can be read that there is only one branch oil passage and there is also one lubrication target.
Further, the apparatus of Patent Document 2 inserts a plurality of pipes having different lengths and diameters into a rotating shaft concentrically, and seals between the pipes with a ring-shaped member called a bush, thereby supplying an oil supply location ( A shaft center oil passage in the rotation shaft is partitioned for each lubrication-necessary portion and clutch hydraulic oil chamber. And if it sees for every division area | region, there will be only one branch oil passage and the object of lubrication is one place.
On the other hand, the device of Patent Document 3 is provided with a plurality of branch oil passages in the axial direction communicating with a common hollow portion of the unrotated rotating shaft, and supplies oil to a plurality of locations in the axial direction. Yes. By doing in this way, it becomes possible to supply oil from the same axial part oil passage (hollow part of a rotating shaft) to a plurality of lubrication required parts from which an axial direction position differs, compared with a device like patent documents 2. There is an advantage that the structure is extremely simplified.

JP-A-60-143272 Japanese Utility Model Publication No. 2-136823 JP-A-9-159015

  By the way, in the lubricating device having a configuration as described in Patent Document 3 (a plurality of branch oil passages extending in the axial direction extending from a common axial center oil passage in the rotation shaft), the rotational speed of the rotation shaft is reduced. When the centrifugal force acting on the oil increases with the increase, the amount of lubricating oil discharged from the upstream branch oil passage in the longitudinal direction of the rotating shaft increases, and the downstream side tends to decrease conversely. That is, when the rotational speed of the rotating shaft is not so high, the actual flow rate is larger than the required flow rate on both the upstream side and the downstream side, but when the rotational speed becomes high, the actual flow rate on the upstream side increases rapidly, The actual flow rate on the downstream side decreases rapidly. Such a tendency will cause the lubricating oil to be discharged on the upstream side, and may cause insufficient lubrication on the downstream side. Further, as shown in FIG. 3 (c), the inflow amount of the lubricating oil into the rotating shaft tends to be insufficient in the high rotating range with respect to the total discharge amount from the oil hole of the rotating shaft. There is also a problem that the capacity of the O / P has to be increased even though there is a margin in the amount of lubricating oil flowing into the rotating shaft.

In addition, as mentioned above, it is considered as follows that the oil amount is biased by high-speed rotation. That is, in the rotating state, as shown in FIG. 3B, on the relatively downstream side, the oil 3 is brought close to the inner surface side of the axial center oil passage 2 in the rotating shaft 1 by centrifugal force to form a layer. To do. For this reason, the centrifugal force P applied to the branch oil passage 4 is set to r is the inner diameter of the axial center oil passage 2, m is the mass of the oil layer at the location of the branch oil passage 4, and ω is the rotational speed of the rotary shaft 1. In this case, P = mrω ^2, which is proportional to the square of the rotational speed ω and proportional to the oil layer thickness t (= t∝m). When there are a plurality of branch oil passages 4 in the axial direction, the amount of oil flowing downstream of the axial center oil passage 2 is sequentially reduced by the amount discharged in each branch oil passage, so the thickness of the layer As shown in FIG. 4, t naturally decreases toward the downstream side. Then, the centrifugal force P of each branch oil passage 4 naturally decreases toward the downstream side (the right end side of the rotating shaft 1 in FIG. 4), and accordingly, the radial outer periphery from each branch oil passage 4 Naturally, the amount of oil discharged to the side also decreases toward the downstream side. Therefore, when the rotary shaft 1 rotates at a high speed, the oil amount rapidly increases on the upstream side where the thickness t of the oil layer is thick even in the high-speed rotation state, and accordingly, the decreasing tendency of the thickness t on the downstream side. As a result, the thickness t becomes extremely thin on the downstream side, and as shown in FIG. 4, the centrifugal force and the amount of oil are extremely reduced on the downstream side.

It is possible to reduce the oil amount by narrowing the inner diameter of the branch oil passage 4 toward the upstream side to reduce the oil amount in a high-speed rotation state. However, in this case, in the low-speed rotation state, the amount of oil on the upstream side may be insufficient, and the drilling man-hours of the branch oil passage 4 are increased, which is not a sufficient solution.
Patent Document 3 discloses a configuration in which a flow rate appropriate means for correcting such an unbalance of lubricating oil distribution is provided. The flow rate appropriate means is a valve mechanism including a spool that restricts the oil amount on the upstream side in accordance with an increase in hydraulic pressure due to centrifugal force. With this configuration, it is possible to suppress unevenness in the amount of oil in the high-speed rotation state and to supply a good oil even in the low-speed rotation state. However, since a valve mechanism must be provided around or around the rotating shaft, there is a problem that the structure becomes complicated and the cost increase is relatively large. In particular, when there are many branch oil passages over the entire axial length of the long rotating shaft, it is not sufficient to provide the valve mechanism only at one upstream position, and thus it is necessary to provide a plurality of valve mechanisms. Not practical.
Accordingly, an object of the present invention is to provide a lubricating device for a transmission in which the imbalance of the lubricating oil is corrected by adding a simple configuration.

In the transmission lubrication device of the present application, lubricating oil is fed from one end side of the shaft into the hollow portion of the rotating shaft in the transmission, and a plurality of oil holes penetrating from the hollow portion of the shaft to the outer peripheral surface of the shaft are formed. In the lubricating device of the transmission for supplying the lubricating oil to each of the plurality of lubrication necessary parts located around the shaft by causing the lubricating oil fed to flow out around the shaft,
A pipe fixed in a state of being inserted into the hollow portion from one end side of the shaft is provided, and a plurality of oil holes penetrating from the inner peripheral surface to the outer peripheral surface are provided in the pipe in the axial direction, and the lubricating oil is The configuration is such that the lubricating oil fed into the pipe from the one end side flows out into the hollow portion through the oil hole, and further flows out around the shaft through the oil hole. A lubricating device for a transmission.

Here, the “lubrication required part” may be a friction engagement element such as a clutch or a brake, a bearing, a gear, or the like.
In a more preferred aspect of the present invention, as described in claim 2, the diameters of the plurality of oil holes are made equal.
Further, as described in claim 3, the relationship between the number of the oil holes and the number of the oil holes may be a one-to-multiple configuration.

  In the lubrication device for a transmission according to the present application, oil can be satisfactorily supplied to the lubrication-necessary portion around the shaft while having a relatively simple configuration in which a pipe fixed in the shaft is inserted. That is, as the rotational speed of the shaft increases, even if the centrifugal force acting on the oil in the hollow portion of the shaft increases, there is no bias in the axial position of the amount of lubricating oil discharged from each oil hole, In the high-speed rotation state, the phenomenon that the oil amount becomes excessive on the upstream side and becomes insufficient on the downstream side can be solved.

In addition, as described in claim 2, when the diameters of the plurality of oil holes are equal, processing of the oil holes is facilitated.
Further, as described in claim 3, when the number of the oil holes and the number of the oil holes is one to plural, the number of the oil holes is reduced and the number of processing steps of the pipe can be reduced.

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a partial cross-sectional view of the automatic transmission of this example, and FIG. 2 is a diagram for explaining the operation of this example.
First, the overall configuration will be described with reference to FIG. For convenience, in FIG. 1, the right side (side closer to the engine) is the engine side, and the left side (side far from the engine) is the non-engine side.
The automatic transmission of this example includes a torque converter (not shown), an oil pump (not shown), and a transmission mechanism 10 in a case that is a casing. The case includes a casing 10a, a side cover 10b fixed to the opposite side of the casing 10a, and a housing (not shown) fixed to the engine side of the casing 10a. The transmission mechanism 10 is mainly provided in the side cover 10b and the casing 10a.

The torque converter is disposed on the front side (inside the housing) of the speed change mechanism 10 and is a well-known device that appropriately decelerates the rotation of the engine and transmits it to the input shaft 9 described later.
The oil pump is disposed at a position between the torque converter and the speed change mechanism 10. The oil pump is driven by the rotation of the engine transmitted through the rear cover of the torque converter, and sucks oil in an oil pan (not shown) attached to the lower surface side of the transmission mechanism 10 to generate a predetermined hydraulic pressure. . The oil pressure generated by the oil pump is regulated as necessary in a control valve unit (not shown) (usually disposed in the oil pan) and then supplied to various places.

  As shown in FIG. 1, the transmission mechanism 10 has an input shaft 9 disposed on the central axis, and includes three planetary gear mechanisms 11 to 13 around the input shaft 9, and changes the rotation of the input shaft 9. The output is output from the output gear 14 that functions as an output shaft. Although detailed description is omitted, the speed change mechanism 10 transmits the rotation of the input shaft 9 or the like to a specific gear or carrier constituting the planetary gear mechanisms 11 to 13 according to the shift position, or to a specific gear. Alternatively, in order to transmit the rotation of the carrier to the output gear 14 or the like as appropriate, or to restrain the rotation of a specific gear or carrier as appropriate, in this case, three clutches 15 to 17 and two brakes 18 and 19 (multi-plate type) Frictional engagement elements). Further, around the input shaft 9, there are rotating bodies such as a gear, a carrier, the friction engagement element, and a drum, a hub, and a hollow shaft that transmit rotation between the friction engagement element and the gear (for example, The hollow shafts 20 to 22 shown in FIG. 1 and the like (other reference numerals are omitted) are densely and complicatedly arranged so as to be folded, and further support bearings (for example, the bearings 25 to 31 shown in FIG. 1). , And others are omitted).

An axial center oil passage 41 (hollow portion) is formed in the input shaft 9 so as to extend from the one end surface on the side opposite to the engine to the axial center line, and the axial direction oil passage 41 is radially extending from the axial center oil passage 41 in a plurality of axial directions. Branch oil passages 42 to 56 (oil holes) extending to the outer peripheral surface are formed. These branch oil passages 42 to 56 allow the lubricating oil to flow out around the input shaft 9, and respectively supply the lubricating oil to a plurality of necessary lubrication parts (the gears, friction engagement elements, and bearings) located around the shaft 9. It is for supply. In addition, although a code | symbol is abbreviate | omitted, also in the rotary bodies, such as a drum, a hub, and a hollow shaft mentioned above, the same oil hole is formed in various places as needed, and from the input shaft 9 (namely, axial center part oil path 41). From the above, the spilled lubricating oil is sequentially supplied to the outside in the radial direction.
In addition, it is desirable that the inner diameter dimensions of the branch oil passages 42 to 56 are equal regardless of the axial position from the viewpoint of ease of processing. Thus, even if the inner diameter dimensions are the same, a satisfactory lubricating oil can be supplied by the action described later. However, depending on the specification of the lubrication required part, the required oil amount is different, and therefore the size of the branch oil passage (oil hole) may be varied accordingly.

A concave chamber 61 is formed on the axial center line on the inner surface of the side cover 10 b (a position facing one end surface of the input shaft 9), and a pipe 62 is fixedly provided in the concave chamber 61. . One end of the pipe 62 on the side opposite to the engine is inserted into the opening of the concave chamber 61, and many portions including the other end on the engine side are on the axial center line in the input shaft 9 (in the axial center oil passage 41). In a state of being inserted into the side cover 10b, the side cover 10b is fixed. In this case, the other end of the pipe 62 extends to the vicinity of the back end surface in the axial center oil passage 41. The pipe 62 has a bottomed cylindrical shape, and one end inserted into the opening of the concave chamber 61 is opened, and the other end inserted near the back end surface in the axial center oil passage 41 is closed. (Excluding oil holes 86 described later).
The fixing structure of the pipe 62 is not particularly limited, but as one structure, a thread groove (not shown) is formed on the inner surface of the opening of the concave chamber 61 and the outer periphery of one end of the pipe 62, and one end of the pipe 62 is formed. There may be a structure in which the portion is screwed into the opening of the concave chamber 61. Alternatively, there may be a structure in which a flange portion (not shown) formed on one end side outer periphery of the pipe 62 is screwed to the side cover 10b. Further, a seal portion 63 is formed between one end of the pipe 62 and the opening of the concave chamber 61, and the concave chamber 61 is sealed in a state where it communicates only with the pipe 62. Here, the seal portion 63 may be formed by fitting a packing made of rubber or resin, or may be formed by a sealant that is cured after application.

A cylindrical bush 64 that supports the other end side of the pipe 62 is inserted between the other end side of the pipe 62 and the inner peripheral surface of the input shaft 9 (axial center oil passage 41). . The bush 64 is made of a material functioning as a sliding bearing, and allows the input shaft 9 to rotate relative to the fixed pipe 62. Instead of the bush 64, a rolling bearing (for example, a needle roller bearing) may be provided.
The pipe 62 is provided with oil holes 72 to 86 penetrating from the inner surface to the outer surface at a plurality of positions in the axial direction. In this case, these oil holes 72 to 86 are provided in a one-to-one correspondence relationship corresponding to the branch oil passages 42 to 56 described above. The oil holes 72 to 85 excluding the oil hole 86 on the end surface are provided in the radial direction so as to penetrate from the inner peripheral surface to the outer peripheral surface, and the positions in the axial direction coincide with the branch oil passages 42 to 55. . That is, for example, the oil hole 72 is aligned with the branch oil passage 42 in the axial direction.
It is desirable that the inner diameters of the oil holes 72 to 86 be equal regardless of the axial position from the viewpoint of ease of processing. Thus, even if the inner diameter dimensions are the same, a satisfactory lubricating oil can be supplied by the action described later. However, depending on the specifications of the lubrication required part, the required oil amount is different, so the size of the oil hole may be varied accordingly.

  In the case of this example, the oil supplied from the input shaft 9 to the lubrication required portion around the input shaft 9 is supplied through the following route. That is, lubricating oil generated by the above-described oil pump and supplied through the control valve unit is supplied into the above-described recessed chamber 61 via an oil passage (or external piping) provided in the side cover 10b or the like. The lubricating oil flows into the pipe 62 from one end side, flows into the hollow portion of the input shaft 9 (that is, the shaft center oil passage 41) via the oil holes 72 to 86, Furthermore, it is the structure which flows out to the circumference | surroundings of the shaft 9 through the branch oil paths 42-56. In the steady state in which the oil pump or the like is operating, the inner diameters of the oil holes 72 to 86 are set so that the pipe 62 is filled with oil. In addition, since the pipe 62 is fixed (it does not always rotate), centrifugal force is not added to the oil in the pipe 62, and it is easy to realize the above-mentioned full state.

  According to the automatic transmission of the present example described above, the oil is supplied to the lubrication required portion around the input shaft 9 while having a relatively simple configuration in which the pipe 62 fixed in the input shaft 9 is inserted. It becomes possible well. That is, even if the centrifugal force acting on the oil in the hollow portion (axial center oil passage 41) of the shaft 9 increases as the rotational speed of the input shaft 9 increases, the oil is discharged from the branch oil passages 42 to 56. There is no deviation of the amount of lubricating oil in the axial position (due to centrifugal force), and the phenomenon of excess oil amount on the upstream side and shortage on the downstream side can be solved in the high speed rotation state.

  The above operation will be described below with reference to FIG. In FIG. 2, for convenience of explanation, branch oil passages and oil holes are illustrated as simple holes (denoted by reference numerals 94 and 95) provided at regular intervals, but the principle is the same. In this case, the pipe 62 is filled with the oil 3, and no centrifugal force is applied to the oil 3 in the pipe 62. Therefore, the oil discharged from the oil holes 95 (corresponding to the oil holes 72 to 86 in FIG. 1) of the pipe 62 toward the inlets of the branch oil passages 94 (corresponding to the branch oil paths 42 to 56 in FIG. 1). The amount is basically slightly different due to the difference in pipe resistance or oil viscosity due to the difference in the axial position, and is constant regardless of the rotational speed of the shaft 9. Thereby, the thickness t of the oil layer formed at the inlet of each branch oil passage 94 is constant regardless of the rotational speed of the shaft 9, and the difference depending on the axial position is relatively small (basically, the above-mentioned There are differences in pipe resistance or oil viscosity). Therefore, as a result, the oil pressure at the inlet of each branch oil passage 94 and the amount of oil discharged from each branch oil passage 94 are less biased due to the axial position as shown in FIG. Is maintained regardless of the rotational speed of the shaft 9. That is, the phenomenon that the oil amount is excessive on the upstream side and is insufficient on the downstream side in the high-speed rotation state can be solved.

  In addition, if the deviation of the oil amount can be prevented regardless of the rotation speed in this way, the oil amount is not wasted. Therefore, the capacity of the oil pump that has been increased in capacity to allow for the deviation in the high speed rotation state is reduced. There is an advantage that it becomes possible. In addition, the size of the hole in the branch oil passage can be made the same size in consideration of the ease of processing, or it can be relatively easily made larger than the surroundings where a large amount of lubricating oil is required. There is also an effect of improving the degree of freedom of design. Further, the degree of freedom for rotating the shaft 9 at a higher speed is also increased.

The present invention is not limited to the above-described embodiments, and various modifications and applications are possible.
For example, in the above-described embodiment, the relationship between the number of oil holes provided in the pipe and the number of oil holes provided in the shaft is 1: 1, but for example, as shown in FIG. It may be many-to-one. If it is one-to-many, the number of oil holes is reduced and the number of processing steps of the pipe can be reduced.

  Further, the present invention can be applied to any transmission as long as it has a structure that needs to supply lubricating oil to a plurality of axial locations around the rotating shaft. For example, the belt-type continuously variable transmission It goes without saying that the present invention can also be applied to (CVT). The shaft of the present invention is not limited to the input shaft, and may be an output shaft or an intermediate shaft.

It is a fragmentary sectional view of an automatic transmission. It is a figure explaining the effect | action of this invention. (A) is a figure which shows the modification of this invention, (b) is a figure explaining the oil_pressure | hydraulic by centrifugal force, (c) is a figure explaining the shortage tendency of the oil quantity in a prior art. It is a figure explaining the conventional problem.

Explanation of symbols

9 Input shaft (rotating shaft)
10 Speed change mechanism 41 Shaft center oil passage (hollow part)
42-56, 94 Branch oil passage (oil hole)
62 Pipe 72-86, 95 Oil hole

Claims (3)

Lubricating oil is fed into the hollow portion of the rotating shaft in the transmission from one end side of the shaft, and the fed lubricating oil is passed through a plurality of oil holes penetrating from the hollow portion of the shaft to the outer peripheral surface of the shaft. In a lubricating device for a transmission that supplies lubricating oil to each of a plurality of lubrication necessary parts located around the shaft by causing the oil to flow around the shaft,
A pipe fixed in a state of being inserted into the hollow portion from one end side of the shaft is provided, and a plurality of oil holes penetrating from the inner peripheral surface to the outer peripheral surface are provided in the pipe in the axial direction, and the lubricating oil is The configuration is such that the lubricating oil fed into the pipe from the one end side flows out into the hollow portion through the oil hole, and further flows out around the shaft through the oil hole. A lubricating device for a transmission. 2. The transmission lubrication device according to claim 1, wherein the plurality of oil holes have the same diameter. 3. The transmission lubrication device according to claim 1, wherein the number of the oil holes and the number of the oil holes is one to plural.

Images