JP2592087Y2 - Transmission lubrication system - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a lubricating device for a transmission.

[0002]

2. Description of the Related Art As a conventional lubricating device for a transmission, there is one disclosed in JP-A-60-143272 as a conventional example. The transmission lubrication system shown here
After the lubricating oil is cooled by the external oil cooler, it is introduced into the transmission, and is supplied to each part by dividing into a plurality of branch pipes in the direction orthogonal to the axis through the oil passage of the drive shaft. It has become so.

[0003]

However, the conventional lubricating device for a transmission as described above has a problem that the ratio of the oil supplied to each part changes according to the change in the rotation speed of the drive shaft. There is a point. That is, as the rotational speed of the drive shaft increases, the centrifugal force acting on the oil increases, and the oil easily flows out from the branch pipes. At this time, the flow passage cross-sectional areas of the respective branch pipes are all the same. In this case, the outflow flow rate increases in the upstream branch (closer to the oil inlet of the drive shaft). For this reason, the amount of oil supplied to the components arranged on the upstream side increases, and the amount of oil supplied to the components arranged on the downstream side is increased although some parts are discharged as a waste flow rate. May be reduced and some parts may have poor lubrication. FIG. 6 shows a result of measurement of a flow rate actually passing through each branch pipe line by the present inventors. In the figure, as the most representative example, two branch pipes on the upstream side and the downstream side are shown.
The actual flow rate 2 for the required flow rate 1 on the upstream side and the actual flow rate 4 for the required flow rate 3 on the downstream side are plotted. While the rotation speed of the drive shaft is not very high, the actual flow rate is larger than the required flow rate on both the upstream and downstream sides, but the actual flow rate 2 on the upstream side suddenly increases at a certain rotation speed. It can be seen that the actual flow rate 4 on the downstream side suddenly decreases at a rotational speed lower than this. Note that the amount of oil supplied to the shaft center oil passage of the drive shaft does not become proportional to the rotation speed, and has a tendency substantially similar to the case of the actual flow rate 4 on the downstream side. That is, the amount of supplied oil tends to decrease in inverse proportion to an increase in the rotation speed at a certain rotation speed. This is because the centrifugal force caused by the rotation of the drive shaft causes the oil in the shaft center oil passage to move outward from the shaft center as described above, but this force resists the oil flowing in from the inflow port. This is because it acts as a force. Therefore, above a certain rotation speed, the higher the rotation speed, the smaller the amount of inflow into the shaft center oil passage.If the flow is not properly distributed, the supply flow will be insufficient and lubrication failure will occur. This is likely to happen. As a similar vehicle refueling system,
There is one as disclosed in Japanese Patent Application Laid-Open No. 64-6460. This
This means that the faster the input shaft 11 rotates, the more
1b, the flow rate of the oil flowing out increases, and the supply flow rate becomes insufficient.
To prevent poor lubrication.
, Sliding body biasing means 16 and sliding body driving means
17, the more the input shaft 11 rotates at a high speed,
Slide the sliding body 14 in a direction to close the discharge hole 11b.
It is like that. However, such a configuration
Now, the sliding body 14, the sliding body biasing means 16 and the sliding body drive
Since the means 17 is provided on the outer periphery of the input shaft 11,
There is a problem that the radial dimension of the speed unit becomes large. The purpose of the present invention is to solve the above problems.

[0004]

SUMMARY OF THE INVENTION The present invention solves the above-mentioned problems by providing a drive shaft with a device for adjusting the flow rate according to the rotational speed in a branch pipe upstream of the drive shaft.
That is, the lubricating device for a transmission according to the present invention is configured such that the oil supply port (10b) of the drive shaft (10) of the transmission is connected to the shaft center oil passage (10).
a) and a plurality of branch pipes (1) in a direction orthogonal to the oil path axis.
0c, 10d, 10e, 12b, 12c, 12d and 1
2e) to supply lubricating oil to the transmission components in each part outside the drive shaft (10) through the drive shaft (10), and to the upstream side near the oil supply port (10b) of the drive shaft (10). The branch pipe line (10c) has an inward seating surface (18).
a) having a sheet member (18);
a) a valve body (22) having a valve surface (22a) movably disposed in a direction to be seated on a) or away from the seat surface (18a), and the valve body (22) to the seat surface of the seat member (18). (18a) is provided with an elastic member (28) that exerts a force so as to forcibly separate it from the valve (18a). At a predetermined rotation speed of the drive shaft (10), the centrifugal force of the valve element (22) itself and the centrifugal force of oil acting on the valve element (22) are balanced with the valve element pressing force. I have. In addition, the valve body (22) of the above-mentioned flow control device has a valve face (22a) with a branch pipe (10).
c) is formed by a conical outer peripheral surface having a smaller diameter toward the outer side and a larger diameter toward the inner side, and the seat member (18) has a seat surface (18a) having a valve body (22). It is preferable that the elastic member (28) is a coil spring formed by a conical inner peripheral surface corresponding to the valve surface (22a). In addition, the code | symbol in a parenthesis shows the corresponding member of an Example.

[0005]

Until the drive shaft reaches a predetermined rotational speed, the force in the flow path closing direction due to the centrifugal force is smaller than the force in the flow path opening direction due to the elastic force of the elastic member. Therefore, it does not operate, and the flow rate of the same ratio as in the past passes through each branch conduit to lubricate each component. When the rotation speed of the drive shaft is higher than a predetermined rotation speed, the force in the flow path closing direction due to the centrifugal force acting on the valve element is larger than the force in the flow path opening direction due to the elastic force of the elastic member, and the valve element It starts to operate in the flow path closing direction, the flow path is narrowed according to the rotation speed, and the flow rate through the branch pipe line provided with the flow rate control device is reduced. Thereby, in the rotation speed range above a predetermined value, the flow rate passing through the branch pipe on the downstream side can be increased as compared with the case where the flow rate adjusting device is not provided, and each part can be reliably lubricated. It becomes possible.

[0006]

FIG. 1 shows an embodiment of the present invention. The drive shaft 10 of the transmission is formed with a shaft portion oil passage 10a, an oil supply port 10b, and a plurality of branch conduits 10c, 10d, and 10e. A shaft member 12 is integrally rotatably fitted to an inner end portion of the drive shaft 10 at an open end on the left end side in the drawing, the inner diameter portion communicating with the shaft portion oil passage 10a. The shaft member 12 includes a shaft center portion oil passage 12a, a plurality of branch pipelines 12b, 12c, and 12d.
And 12e are respectively formed. The drive shaft 1
The pipe 10f formed on the most upstream side of the shaft 0 functions as an air inlet, and the pipe 12f formed on the most downstream side of the shaft member 12 functions as an air outlet. The drive shaft 10 is
It is designed to be driven to rotate via the shaft member 12.
A branch pipe 10c closest to the oil supply port 10b of the drive shaft 10 has a seat 10g at the outer end on the upper end side in the figure (see FIG. 2).
Are formed, and the flow rate adjusting device 14 is attached. As shown in FIG.
Is a cylindrical member 16 fitted in the branch pipe 10c on the most upstream side, a conical tubular sheet member 18 accommodated in the inner diameter of the cylindrical member 16, a lower end of the cylindrical member 16 and a large-diameter end of the sheet member 18. The disk-shaped support plate 20 is integrally fixed to the support plate 20, the truncated cone-shaped valve body 22 placed on the support plate 20, and the support plate 20. (Road closing) Guide member 24 capable of guiding movement in the downward (flow path opening) direction, fixing bar 26 integrally fixed to the lower end of cylindrical member 16 and the small-diameter end of sheet member 18, and fixing bar 26
And a spring (elastic member) 28 which is arranged between the lower end surface in the figure and the upper end surface of the valve body 22 in the figure and acts so as to move the valve body 22 away from the fixing bar 26. I have. A valve surface 22a is formed by the conical outer peripheral surface of the valve body 22. Also, the sheet member 18
The sheet surface 18a is formed by the conical inner peripheral surface of the above. Seats for receiving springs 28 are formed on the lower end surface of the fixing bar 26 in the drawing and the upper end surface of the valve body 22 in the drawing. The spring 28 has a centrifugal force acting on the valve body 22 and a centrifugal force of oil acting on the bottom surface of the valve body 22 when the spring force (force in the valve opening direction) is a predetermined rotation speed of the drive shaft 10. It is set so as to balance with the force based on the sum of the forces (force in the valve closing direction). The cylindrical member 16 has an inner pawl 16a extending from the lower end in the drawing and an outer pawl 16b extending from the upper end in the drawing. Inner pawl 16
“a” is bent in the outer circumferential direction, and the outer pawl portion 16 b is swaged in the outer circumferential direction of the cylindrical member 16. The flow adjusting device 14 is positioned and fixed to the branch conduit 10c of the drive shaft 10 by the inner pawl 16a and the outer pawl 16b. The space between the inner diameter of the cylindrical member 16 and the outer diameter of the sheet member 18 is oil-tight. The oil in the shaft portion oil passage 10 a is
The fluid flows out of the branch line 10c through a conical annular gap between the valve body 8a and the valve surface 22a of the valve body 22. When the rotation speed of the drive shaft 10 is equal to or higher than a predetermined speed, the valve body 2
2 is pushed outward (upward in the state of FIG. 2) by the centrifugal force against the force of the spring 28, so that the gap between the seat surface 18a of the seat member 18 and the valve surface 22a of the valve body 22 is increased. The cross-sectional area of the conical annular passage formed in the groove is reduced, and the oil flow can be reduced. The guide member 24 can be configured as shown in FIG.
That is, the column-shaped guide members 24 are attached to four places on the circumference of the disk-shaped support plate 20. In the case shown in FIG. 1A, the guide members 24 are rectangular prisms having a rectangular cross section. The one shown in FIG. 1B has a columnar shape.

Next, the operation of this embodiment will be described. In order to assemble the flow control device 14, a support plate to which the guide member 24 is fixed in advance in a state where the inner pawl portion 16a of the cylindrical member 16 is not bent but straightened as shown by a broken line in FIG. 20 is fixed to the lower end of the cylindrical member 16 in the figure. Next, the valve element 22 is lowered from above the support plate 20 while being guided by the guide member 24, and is mounted on the support plate 20. After fitting one end of the spring 28 into the seat of the support plate 20 and the other end into the seat of the fixing bar 26, the fixing bar 26 is fixed to the upper end of the cylindrical member 16 in the figure. Thus, the assembly of the flow rate adjusting device 14 is completed. To attach the flow control device 14 to the branch pipe 10c of the drive shaft 10, the cylindrical member 16 is fitted into the hole of the branch pipe 10c. Next, the oil passage 10a of the shaft center of the shaft member 10
Inserting the caulking jig from the side to insert the inner claws 16a in FIG.
Bend to the position shown by the solid line. In addition, the outer claws 16
The cylindrical member 16 is fixed to the hole of the branch conduit 10c by caulking and fixing b to the seat 10g of the shaft member 10. As described above, the flow control device 14 is attached to the branch pipe 10c of the drive shaft 10. Driving the transmission, drive shaft 1
0, oil is sucked from the oil supply port 10b into the shaft center portion oil passage 10a, and the branch lines 10c, 10d, and 10e of the drive shaft 10 and the branch lines 12b to Oil is respectively discharged from 12f. Thereby, oil is supplied to each part around each branch pipe line, and each part is lubricated. It should be noted that air is sucked in from the most upstream pipe 10f of the shaft member 12 in response to the oil being discharged from the downstream branch pipe sequentially from the upstream branch pipe. That is, in a state where the oil is discharged from each branch conduit, the air passage 13 is formed at the axial center of the axial oil passage 10a as shown in FIG. While the rotation speed of the drive shaft 10 is equal to or lower than a predetermined value, in the case of the branch conduit 10c, the force of the spring 28 is greater than the outward force acting on the valve body 22.
As shown by the solid line, the valve body 22 is separated from the seat member 18 and pressed against the support plate 20 (valve open position).
Therefore, the cross-sectional area of the conical annular passage remains at a predetermined size, and the flow rate of the oil passing through the flow rate adjusting device 14 is also as set. When the rotation speed of the drive shaft 10 becomes larger than a predetermined value, the outward force acting on the valve body 22 increases, and the valve body 22 separates from the support plate 20 against the force of the spring 28, and Being guided,
It moves outward as indicated by the broken line in FIG. 2 and stops at a position balanced with the force of the spring 28. That is, the cross-sectional area of the conical annular passage of the branch conduit 10c is reduced, and the flow rate of the oil passing therethrough is reduced. Therefore, the flow rate of the oil passing through the branch pipes other than the branch pipe 10c increases accordingly. In this way, the amount of oil supplied to each part can be made as set, and each part can be sufficiently lubricated.

(Test Results) In order to compare with the conventional oil discharge amount shown in FIG. 6, a flow regulating device 14 is attached to a branch pipe 10c on the upstream side of the drive shaft 10 used in the test of FIG. The test was performed under the same conditions as in the case of No. 6. FIG. 5 shows the results. The actual flow rate 6 slightly exceeds the required flow rate 5 on the upstream side generally over the entire rotation speed range of the drive shaft 10, and similarly, the required flow rate 7 on the downstream side
It can be seen that the actual flow rate 8 is slightly higher. From this, it can be seen that the components can be sufficiently lubricated over the entire rotation speed range of the drive shaft 10.

In the description of the above embodiment, the flow control device 14 is provided only in the most upstream branch pipe 10c. A flow control device may be used. In this case, each spring may be set such that the spring force increases as the flow rate adjusting device is located farther from the upstream side.

[0010]

[Effects of the Invention] As described above, according to the present invention ,
Without increasing the radial dimension of the transmission, the lubricating oil supplied to the components inside the transmission can be reduced during high-speed rotation of the drive shaft.
Can also be prevented from being insufficient, it is possible to reliably lubricate various parts.

[Brief description of the drawings]

FIG. 1 is a diagram showing an embodiment of the present invention.

FIG. 2 is a diagram illustrating the structure of a flow rate adjusting device.

FIG. 3 is a diagram showing a cross section of a guide member attached to a support plate.

FIG. 4 is a perspective view of a flow control device.

FIG. 5 is a diagram showing the relationship between the rotation speed of the drive shaft and the amount of oil discharged from the branch pipe when the present invention is implemented.

FIG. 6 is a diagram showing a relationship between the rotation speed of a conventional drive shaft and the amount of oil discharged from a branch pipe line.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Drive shaft 14 Flow control device 16 Cylindrical member 18 Seat member 20 Support plate 22 Valve body 24 Guide member 26 Fixing bar 28 Spring

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. ⁶ , DB name) F16H 57/04 F16K 17/04

Claims (2)

(57) [Scope of request for utility model registration] An oil supply port of a drive shaft of a transmission passes through a shaft center oil passage and a plurality of branch pipes extending in a direction orthogonal to the oil passage shaft center to a transmission component at each portion outside the drive shaft. In a lubrication device for a transmission that supplies lubricating oil, a branch member on the upstream side near the oil supply port of the drive shaft includes a seat member having an inward facing seat surface, and a seating direction on the seat surface. Or a valve body having a valve surface movably arranged in a direction away from the seat surface; and an elastic member forcing a force to push the valve body away from the seat surface of the seat member. The elastic member has a valve body pressing force which is the sum of the centrifugal force of the valve body itself and the centrifugal force of oil acting on the valve body at a predetermined drive shaft rotation speed. Transmission lubrication characterized by being balanced with apparatus. 2. The valve body of the flow control device according to claim 1, wherein a valve surface of the valve body is formed by a conical outer peripheral surface having a smaller diameter toward the outer side of the branch pipe line and a larger diameter toward the inner side. The lubrication of a transmission according to claim 1, wherein the seat member has a seat surface formed by a conical inner peripheral surface corresponding to a valve surface of the valve body, and the elastic member is a coil spring. apparatus.