JPH04194445A - Lubricating oil supply device for automatic transmission - Google Patents

Abstract

PURPOSE:To sufficiently supply lubricating oil to friction connecting elements so as to improve durability of a friction member of the friction connecting elements by providing a lubricating oil supply means in a position upper from a rotary shaft of an automatic transmission in a case member of the automatic transmission. CONSTITUTION:A lubricating oil supply means 10 for supplying lubricating oil from peripheral sides of friction connecting elements 104, 108 is provided in a position upper from a rotary shaft (output shaft) 101 of an automatic transmission in a case member 109 of the automatic transmission. By this lubricating oil supply means 10, the lubricating oil is sufficiently supplied to the friction connecting elements to improve durability of a friction member.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) □ The present invention relates to an FR oil supply device for an automatic transmission equipped with a lubricating oil supply means for supplying lubricating oil to frictional engagement elements.

[Conventional technology]

Conventionally, r! As a structure for supplying full U oil, for example, the structure shown in Japanese Patent Laid-Open No. 62-288753 is known.

FIG. 12 is a sectional view of a main part of such an automatic transmission A. In the figure, the output shaft 101 is provided with a hollow portion 101a and a passage 102 that communicates the hollow portion 101a with the surface of the output shaft 101. Lubricating oil is pumped into the hollow part 101a, and the 1IvlW4 oil is supplied from the passage 102 to the row one-way clutch 103 and the low-and-reverse brake 104 as a friction engagement element by the centrifugal force generated by the rotation of the output shaft 101. has been done.

The input shaft 105 is provided with a hollow part 105a that communicates with the hollow part 101a, and lubricating oil is pumped therein similarly to the hollow part 101a. The hollow portion 105a also has a passage 106 communicating between the hollow portion 105a and the surface of the output shaft 105.
The lubricating oil is supplied from the passage 106 to the reverse clutch 107 and the band brake 108 as frictional engagement elements by the centrifugal force generated by the rotation of the output shaft 105.

Here, the low and reverse brake 104 includes a low and reverse brake hub 104a as a rotating member, a drive plate 104b provided on the low and reverse brake hub 104a, and a transmission case 109 as a case member. A driven plate 104C and a piston 104d that presses the driven plate 104c against the drive plate 104b.
It is composed of. Although not shown, the drive plate 104b is provided with a facing as a friction member. Furthermore, a pressure chamber 104e is defined between the piston 104d and the transmission case 109. Then, the hydraulic oil acts on the pressure chamber 104e and moves the piston 104d to the left in the figure, thereby bringing the drive plate 104b and the driven plate 104C into pressure contact, and the low and reverse brake 104 is activated and the O-and The reverse brake hub 104a is stopped from rotating.

Further, the band brake 108 includes a reverse clutch drum 107a as a rotating member, and a brake band 108 provided on the outer periphery of the reverse clutch drum 107a.
(not shown) on the surface where the brake band 108a contacts the reverse clutch drum 107a. A facing is provided as a rubbing member.

When the band brake 108 is operated, hydraulic oil acts on a band servo (not shown), so that the brake band 108a tightens the reverse clutch drum 107a to stop its rotation.

In addition, automatic transmission l! A is the first speed from the low speed side for forward movement.

It has four gears: 2nd, 3rd, and 4th gears, and the shift lever (not shown) operated by the driver has P and R gears.

Six ranges are provided: N, D, and 2.1.

Here, when the R range is selected, the rotational force input from the engine (not shown) is reversed, and the rotational force for moving the vehicle backwards acts on the drive wheels. Further, when the lunge is selected, the gear position is fixed to 1st speed when the lunge is less than a predetermined value. The low and reverse brake 104 is activated when the R range is selected and when the lunge is selected, and when the vehicle is in a state of confusion, and the band brake 108 is activated when the gear is in the 2nd gear and in the 4th gear. operates at times.

[What the invention attempts to solve! Title]

However, in such conventional automatic transmissions, like the 0-and-reverse brake 104 and the band brake 108, sufficient lubricating oil was not supplied during operation, and the Wl friction member was not cooled sufficiently. .

This will be explained by taking the low and reverse brake 104 as an example of a frictional engagement element.

FIG. 13 is a sectional view taken along line XI-XI in FIG. 12.

A sprag 103b is provided between the inner race 103a and the low and reverse brake hub 104a, and the τ row one-way clutch 103 is constituted by the inner race 103a, the sprag 103b, and the low and reverse brake hub 104a.

As shown by the arrow in FIG. 13, the lubricating oil supplied from passage 1()2 moves downward in the figure due to gravity, but 0-
When the and reverse brake 104 is operating, the drive plate 104b does not rotate. Therefore, the lubricating oil is applied to the drive plate 104b and the driven plate 104.
The lubricating oil is mainly supplied only to the lower portion in the figure, and the lubricating oil is not sufficiently supplied to the entire low and reverse brake 104.

On the other hand, as the 0-and-reverse brake 104 operates, the temperature of the contact surface changes as shown in the time chart of FIG. That is, when the operation of the low and reverse brake 104 is started at time t1, the drive plate 104b and the driven plate 104C are pressed against each other, and the rotational speed of the low and reverse brake hub 104a is reduced. As a result, heat generation occurs, and when the operation of the drive plate 104b and the driven reverse brake 104 is completed from the moment t-shock, the operation occurs. The temperature T of the contact surface reaches its maximum value in the case of timepieces.

In this way, the temperature of the contact surface increases as the low-and-reverse brake 104 operates, but on the other hand, as the rotational speed of the low-and-reverse brake hub 104a decreases, the temperature of the entire 0-and-reverse brake 104 increases. Since lubricating oil is not sufficiently supplied to the facing, there is a problem in that the facing is not cooled sufficiently and the durability of the facing is reduced. In particular, when the low and reverse brake 104 is repeatedly activated and released in a short period of time, the temperature IT of the contact surface further increases in accordance with the number of repetitions of activation and release, as shown in FIG. There was a risk that the durability would further deteriorate.

The eleventh object of the present invention is to provide a lubricating oil supply means for an automatic transmission that can sufficiently cool a friction member even when the friction engagement element is in operation.

[Means for Solving Problem 11] In order to solve the above problem, in the invention according to claim 1j1, in an automatic transmission having a friction engagement element, lubricating oil is supplied from the outer peripheral side of the male coupling element. The automatic transmission is characterized in that the oil supply means is provided at a position above the rotating shaft of the automatic transmission in the case member of the automatic transmission.

Further, the invention as set forth in claim 2 is characterized in that a rib extending in the direction of the zero rotation axis is provided on the outer periphery of the case member of the automatic transmission, and an Il oil supply means is provided on the rib.

Further, in the invention according to claim 113, there is provided an operation start detection means for detecting the start of operation of the friction engagement element, and the a lubricant supply means detects the start of operation of the friction engagement element by the operation start detection means. The lubricating oil is supplied to the frictional engagement element for a predetermined period of time starting from the time when the lubricating oil is applied.

Further, in the invention according to claim 4, the lubricating oil supplying means has a temperature detection means for detecting the temperature of the frictional engagement element, and the lubricating oil supplying means is provided when the temperature detected by the temperature detection means is equal to or higher than a predetermined value. , characterized in that lubricating oil is supplied to the frictional engagement element.

(Operation) In the invention described in claim 1, the lubricating oil supply means provided in the case member of the automatic transmission at a position above the rotating shaft of the automatic transmission supplies lubricating oil by 1 ffl from the outer circumferential side of the friction engagement element. Lubricating oil is supplied.

In the invention as set forth in claim 2, the lubricating oil is rubbed by the lubricating oil supply means provided at the rear! ! ! supplied to the fastening element.

In the invention according to claim 3, the RA lubricant is supplied to the friction engagement element from the IF lubricant supply means for a predetermined period of time from the time when the start of operation of the friction engagement element is detected by the operation start detection means. Ru.

In the invention according to claim 4, lubricating oil is supplied from the lubricating oil supplying means to the *m fastening element until the temperature of the ms+ fastening element is equal to or higher than a predetermined value by the s thinning detection means.

〔Example〕

Hereinafter, one embodiment of the present invention will be explained based on the drawings. Note that the same components as those of the prior art described above are given the same reference numerals to simplify the explanation.

FIG. 1 is a mock-up showing the configuration of a first embodiment of the present invention. Reference numeral 1 denotes a lubricating oil supply source, which supplies lubricating oil to the passage 2 by introducing line pressure for operating a fastening element in the automatic transmission 11A.

3 is a pressure reducing valve, which is provided between the passage 2 and the passage 4. The pressure reducing valve 3 adjusts the supply pressure of lubricating oil supplied to the passage 4 to a predetermined value.

A two-position electromagnetic switching valve 5 is provided between the passage 4 and the passage 6. The electromagnetic switching valve 5 is at the position shown in the figure in its initial state! S, which cuts off passage 4 and passage 6; however, when a drive current is applied to solenoid 58 from controller 11, it becomes position (3), and passage 4 and passage 6 are communicated with each other.

A two-position electromagnetic switching valve 7 is provided between the passage 6 and the lubricating oil supply passages 8a and 8b.

In the initial state, the electromagnetic switching valve 7 is at the position IIB shown in the figure.
The passage 6 and the lubricating oil supply passage 8b are connected to each other, but when the drive current from the controller 11 is applied to the solenoid 7a, fR, which communicates between the passage 6 and the lubricating oil supply passage 8a. Lubricating oil supply passage 8a
and Bbt are lubricating oil supply ports 9a, 9d, 9c, 9
d are provided to supply lubricating oil to the low and reverse brake 104 and the band brake 108, respectively. Note that the lubricating oil supply means 1 is supplied from the arR oil supply passages 8a, 8b and the lubricating oil supply ports 9a, 9b, 9C, 9d.
0 is configured.

Reference numeral 11 denotes a controller, which receives a hydraulic oil pressure signal PR for the pressure chamber 104e detected by a pressure sensor 12 as an operation start detection means, and a hydraulic oil for the band servo detected by a pressure sensor 13 as an operation start detection means. The electromagnetic switching valve 5.7 is controlled according to the pressure signal PB, and the control is specifically performed based on the flowchart shown in FIG.

In step 811, the pressure signal PR from the pressure sensor 12 is
However, a pressure signal PB is input from the pressure sensor 13.

In step 812, the pressure signal PR reaches the predetermined value Pg'''.
It is determined whether the limit has been exceeded or not. -- If P611, proceed to step 813; otherwise, proceed to step 316.

In step S13, a drive current is output to the solenoid 5a of the electromagnetic switching valve 5, and the process proceeds to step S314.

In step 314, it is determined whether a predetermined time has elapsed since the drive current was output to the solenoid 5a. Here, the predetermined W8III is the band brake 10
This is the time required to cool down the 8 facings. If the predetermined time has elapsed, the process proceeds to step 815; otherwise, step 814 is repeatedly executed.

In step 815, the output of the drive current to the solenoid 5a is stopped.

On the other hand, in step 816, the pressure signal PR is set to a predetermined value "PR".
It is determined whether or not the value has been exceeded. -i book〒person*
%-”-’PR＞
PR'', the process advances to step 317, and otherwise, step 811 is repeatedly executed.

In step 317, the electromagnetic switching valve 5. A drive current is output to the solenoid 5a of the solenoid 5a and the solenoid 7a of the electromagnetic switching valve 7, and the process proceeds to step 818.

In step 318, it is determined whether a predetermined time has elapsed since the drive current was output to the solenoid 5a. Here, the predetermined Ill is the time required to cool down the seven brakes of the low and reverse brake 104. If the predetermined time has passed, step 819
If not, step 818 is repeatedly executed.

In step 319, the output of drive current to solenoid 5a and solenoid 7a is stopped.

FIG. 3 is a sectional view of the automatic transmission A corresponding to FIG. 12.

As shown in the figure, 1fflW4 oil supply passage Qa.

8b is provided on the inner peripheral side of the truss 5 transmission case 109 as a case member. And m in Figure 3
As shown in FIG. 4, which is a V-IV sectional view, three lubricating oil supply passages 8a and 8b are provided above the output shaft 101.

Next, the operation of this embodiment will be explained.

■ A pressure signal PR of the hydraulic oil acting on the pressure chamber 104e of the low and reverse brake 104 and the band brake 108 when not in operation, and a pressure/force signal PB of the hydraulic oil acting on the band servo.
do not exceed the predetermined values PR'' and Pa'', respectively, so no drive current is output to the solenoid 5a of the electromagnetic switching valve 5, and the electromagnetic switching valve 5 remains at the position IfS. Therefore, the lubricating oil supply passage f3a.

Since no lubricating oil is supplied to brake 8b, no lubricating oil is supplied to low and reverse brake 104 or band brake 108.

■ Operation of the band brake 108 In step 81, the brake band 108a tightens the reverse clutch drum 107a with respect to the band servo.
1.812.813 is executed. Therefore, the driving flow is output to the solenoid 5a of the electromagnetic switching valve 5, and the electromagnetic switching valve 5 is in the position T, and the lubricating oil supply passage 8b is in the position I! When lubricant oil is supplied and it is determined from the lubricant oil supplies 09C and 9d that a predetermined time has elapsed since the band brake operation, step S15 is executed, and the output of the drive current to the solenoid 5a of the electromagnetic switching valve 5 is stopped. The electromagnetic switching valve 5 is in position Is. As a result, rII oil supply passage 8b
The supply of lubricating oil to the band brake 10 is stopped.
The supply of lubricating oil to 8 is also stopped.

■ When the low and reverse spray rake 104 is activated, hydraulic oil for operating the piston 104d is supplied to the pressure chamber 104e, and the pressure signal changes to ``PR-41-predetermined value PR'' in the super-P controller 11. S11.312. S16.817 is executed. Therefore, a driving current is output to the solenoid 5-8 of the electromagnetic switching valve 5 and the solenoid 7a- of the electromagnetic switching valve 7, and the electromagnetic switching valve 5 is in the position [L]
iR, and 1IWi oil is supplied to the mFR oil supply passage 88, so the lubricating oil supply port 9a.

111 oil is supplied to the low and reverse brake 104 from 9b. Then, when it is determined in step 818 that a predetermined time has elapsed since the activation of the low and reverse brake 104, step 819 is executed, and the output of the drive current to the solenoid 5a and the solenoid 7a is stopped, and the electromagnetic switching valve 5 is In position WIS, solenoid switching valve 7
The position becomes 11B.

As a result, the supply of lubricating oil to the 1a81 oil supply passage 8a is stopped, and the supply of imm oil to the low and reverse brake 104 is also stopped.

In this way, in this embodiment, when the low and reverse brake 104 or the band brake 108 is operated, the pressure of the hydraulic fluid acting on the pressure chamber 104e or the band servo exceeds a predetermined value for a predetermined period of time. Since the imm oil is supplied to the low and reverse brake 104 and the band brake 108, a sufficient amount of lubricating oil can be supplied even when the O-and reverse brake 104 and the band brake 108 are operated. As a result, as shown in FIG. 15, the temperature of the contact surface can be significantly lowered compared to the prior art, so the durability of the facing can be improved. Furthermore, even when the low and reverse brake 104 or the band brake 108 is repeatedly activated and released, the temperature of the contact surface remains constant depending on the number of times the activation and release are repeated, as shown in FIG. Therefore, the durability of the facing will not be significantly reduced.Furthermore, when the low and reverse brake 104' or the band brake 108 is not operating, the lubricating oil supply port stage 10 is
Since m extraction oil is not supplied, the ml! No dynamic or force loss occurs due to oil viscosity.

In this embodiment, the pressure sensor 12.13 is used as the actuation start detection means, but a pressure switch is provided instead, and the electromagnetic switching valve 5.7 is controlled by the pressure switch. -It may also be something that you control.'

In addition, an A/T control unit is provided that determines the optimum gear position according to output values from a group of sensors such as a vehicle speed sensor and a throttle sensor that detects throttle opening. In an automatic transmission in which gears are shifted in response to a gear shift instruction signal output from a shift lever unit, gear shifts from 0 to
And reverse brake 104 or band brake 108
It may also be used to detect the start of operation.

Next, a second embodiment of the present invention will be described. Note that the same components as those of the first embodiment described above are given the same reference numerals to simplify the explanation.

FIG. 7 is a schematic diagram showing the configuration of the second embodiment.

In this embodiment, a lip 16 extending in the direction of the output shaft 101 is provided on the outer periphery of the transmission case 109.
A lubricating oil supply passage 8a is provided in the lip 16.

8b is provided. Also, pressure sensor 12゜51
3 is not provided, but instead there is a temperature sensor 14 as fA nucleus detection means for detecting the temperature TR of the facing of the O-and reverse brake 104, and a temperature sensor 14 for detecting the temperature TB of the facing of the band brake 108. A weight loss sensor 15 is provided. Here, the temperature sensors 14 and 15 detect the temperatures TR and Ta by, for example, providing a thermocouple inside the facing.

The controller 11 controls the temperature Ii degree TR of the 0-and reverse brake 104 and the temperature Te of the band brake 108.
The electromagnetic switching valve 5 is controlled in accordance with the above, and in detail, the control is performed based on the flowchart shown in FIG.

In step 821, the temperature TR from the temperature sensor 14 is
Temperature TB is input from temperature sensor 15.

In step 822, it is determined whether the temperature T6 exceeds a predetermined value]゛B*.If Ta>Ta'', step 8
If not, proceed to step 826.

In step S23, the drive 11fi is output to the solenoid 5a of the electromagnetic switching valve 5, and the process proceeds to step 824.

In step 824, it is determined whether the temperature Ts has become equal to or lower than a predetermined value T611. When TB≦Ta”, the process proceeds to step S25, and otherwise, step S24 is repeatedly executed.

In step 825, the output of the drive current to the solenoid 5a is stopped.

On the other hand, in step 826, it is determined whether the temperature TR exceeds a predetermined value TR''. If TR>TR'', the process proceeds to step S27, and if not, step S21 is repeatedly executed.

In step S27, a drive current is output to the solenoid 5a of the electromagnetic switching valve 5 and the solenoid 7a of the electromagnetic switching valve 7, and the process proceeds to step S27.

In step 828, it is determined whether the temperature TR has become below a predetermined value TR''. If TR≦TR, proceed to step 829G; otherwise, step 82& is repeatedly executed.

In step 829, the output of the driving Ti flow to the solenoid 5a and the solenoid 7a is stopped.

FIG. 9 is a sectional view corresponding to FIG. 12 of the automatic transmission A used in this embodiment. Lubricating oil supply passage 8a.

8b are provided at three locations 116 above the output shaft 101, as shown in FIG. 10, which is a sectional view taken along line XX in FIG. And lubricating oil supply ports 9a, 9b, 9c
, 9d is the rAaW4A supply passage 8a.

8b and the inside of the transmission case 109 are communicated with each other.

Next, the operation of this embodiment will be explained.

■ When the low and reverse brake 10-4 and band brake 108 are at low temperatures When the facings of these brakes are at low temperatures, such as when the low and reverse brake 104 and band brake 108 are not operating,
4-7 Temperature characteristic of the acing - %L has not changed -, no drive current is output to the lower solenoid 5a of the electromagnetic switching valve 5, and the electromagnetic switching valve 5 remains in position S. Therefore, since no lubricating oil is supplied to the lubricating oil supply passages 8a and 8b, the low and reverse brake 104
Lubricating oil is not supplied to the band brake 108 or the band brake 108.

(2) Steps S21, 822, and 823 are executed at 0-ra 11 when the band brake 108 is at high temperature. Therefore, a driving current is output to the solenoid 5a of the electromagnetic switching valve 5, and the electromagnetic switching valve 5 is at position T, a! Lubricating oil is supplied to the IWII oil supply passage 8b, and! 1 Lubricating oil supply 09C, 9d to band brake 10
8 is supplied with rRm oil. Then, when it is determined in step 824 that the temperature T6 has become below the predetermined value Ta'' and that the 7 acing has been sufficiently cooled, step S25 is executed, and the output of the drive current to the solenoid 5a of the electromagnetic switching valve 5 is stopped and the electromagnetic The switching valve 5 is in position MS.Thereby, the supply of Il oil to the izm oil supply passage 8b is stopped, and the supply of rRWI oil to the band brake 108 is also stopped.

■ Low and reverse brake 104 at high temperature - Gin,
In the controller 11, step S21゜822,8
26.827 is executed. Therefore, the solenoid 5a of the electromagnetic switching valve 5 and the solenoid 7a of the electromagnetic switching valve 7 are driven 1! The flow is output, the electromagnetic switching valve 5 is in position ①, the electromagnetic switching valve 7 is in position R, and mFR oil is supplied to the lubricating oil supply passage 8a, so that the lubricating oil supply ports 9a and 9b are
Lubricating oil is supplied to the low and reverse brake 104 from. Then, when it is determined in step 828 that the temperature TR has become below the predetermined value TR" and that the facing has been sufficiently cooled, step 5239 is executed, and the output of the drive current to the solenoid 5a and the solenoid 7a is stopped. The switching valve is in position S, and the electromagnetic switching valve 7 is in position 11B.As a result, the supply of arm oil to J!l lubricating oil supply port !8a is stopped, and the supply of lubricating oil to the low and reverse brake 104 is also stopped. Ru.

In this way, in this embodiment, m? is applied to the low and reverse brake 104 or the band brake 108 as shown in FIG. It is designed to supply lll oil. The effects of this embodiment are similar to those of the first embodiment, but in addition to the effects of the first embodiment, the following effects are achieved.

That is, a rib 716 is provided on the outer periphery of the transmission case 109 parallel to the rotation axis, and a rib 716 is provided inside the rib 6.
By providing the lubricating oil supply passages 8a and 8b, the rigidity of the transmission case 109 is improved, and in order to provide the lubricating oil supply passages 8a and 8b inside the transmission case 109 as in the first embodiment, the transmission case is Since there is no need to increase the radial dimension of the transmission case 109, there is an advantage that the W- of the transmission case 109 does not need to be increased.

Furthermore, in this embodiment, the low and reverse brake 104
WJa against band brake 108! Oil is supplied according to the temperature of these vents, and the oil is supplied in an amount equal to or less than 181 in order to cool the facing temperature to a predetermined value or less.
Since the lubricating oil is supplied across Il, it is possible to improve the durability of the facing while minimizing power loss due to the viscosity of the lubricating oil.

Although this embodiment shows a configuration in which a thermocouple is provided inside the seven facings of the low and reverse brake 104 as the temperature sensor 14, a thermocouple may be provided in the driven plate 104c to indirectly measure the temperature TR of the facing. It is also good as something to do.

Further, the automatic transmission A is provided with both pressure sensors -12, 13 and temperature sensors 14, 15, and a + * oil supply means 1.
Pressure sensor 12.13 starts supplying mW4 oil from 0.
This may be performed using a signal from either one of the temperature sensor 14 and the temperature sensor 14, 15.

In this case, even if the lubricating oil supply is stopped when the temperatures TR and Ta of the temperature sensor 14. good.

Further, the automatic transmission 11 in the first and second embodiments
In A, the low and reverse brake 104 and the band brake 108 were not operated at the same time, and ImW4 oil was not supplied from the WA8I oil supply means 10 at the same time, but like these brakes. [1!
In an automatic transmission that has a plurality of engagement elements and in which the plurality of friction engagement elements may operate simultaneously, lubricating oil is supplied from the lubricating oil supply means 10 to the plurality of friction engagement elements at the same time. You can also use it as

〔Effect of the invention〕

As described above, in the invention according to claim 1,
In an automatic transmission having a frictional engagement element, a lubricating oil supply means for supplying 5 rpm of oil from the outer peripheral side of the frictional engagement element is provided at a position above the rotating shaft of the automatic transmission in a case member of the automatic transmission. As a result, lubricating oil is sufficiently supplied to the frictional engagement element, and the durability of the friction member of the frictional engagement element can be improved.

Further, in the invention according to claim 2, a rib extending in the direction of the rotating shaft is provided on the outer periphery of the case member of the automatic transmission, and the lubricating oil supplying means is provided on the rib, so that the lubricating oil supplying means is provided in the case member. There is no need to increase the radial dimension of the case member when arranging the case member, and in addition to the effect of the invention described in claim 1, there is no need to increase the ψ amount of the case member.

Further, in the invention according to claim 3, there is provided an operation start detection means for detecting the start of operation of the friction engagement element, and the lubricating oil supply means detects the start of operation of the friction engagement element by the operation start detection means. Since lubricating oil is supplied to the frictional engagement element for a predetermined period of time from the moment the WA engagement element is activated, in addition to the effects of the invention described in claim 1 or 2, there is no increase in power loss when the WA engagement element is not in operation.

Further, in the invention according to claim 4, the friction tightening 1f
! i! ! It has a temperature detection means for detecting the temperature of the element, and the lubricating oil supply means has a front &! Since lubricating oil is supplied to the frictional engagement element while the temperature detected by the temperature detection means is equal to or higher than a predetermined value, power loss is increased when the frictional engagement element is not in operation, similarly to the invention according to claim 3. In addition, since lubricating oil is supplied to the frictional engagement element according to the temperature of the frictional member of the II frictional engagement element, excessive heat is applied to cool the temperature of the frictional member to a predetermined value or less. The lubricating oil is supplied for a sufficient period of time, thereby improving the durability of the facing and minimizing power loss due to the viscosity of the lubricating oil.

[Brief explanation of the drawing]

Fig. 1 is a schematic diagram showing the configuration of the first embodiment of the present invention, Fig. 2 is a flowchart showing the operation of the controller of the first embodiment, and Fig. 3 is a cross-section of the main part of the automatic transmission mA in the first embodiment. Figure 4 is a sectional view taken along line rV-IV in Figure 3, Figures 5 and 6 are characteristic diagrams showing the effects of the first embodiment, and Figure 7 shows the configuration of the second embodiment of the present invention. Schematic figure 8 is a flowchart showing the operation of the controller 0- in the second embodiment, figure 9 is a sectional view of the main part of automatic transmission A in the second embodiment, figure 10 is i19 figure (7)X- 11 is a characteristic diagram showing the effect of the second embodiment, FIG. 12 is a sectional view of the main parts of the automatic transmission in the conventional technology, FIG. 13 is a ℃-■ sectional view of FIG. 12, FIG. 14 and FIG. 15 are characteristic diagrams showing the temperature of the contact surface. 8a, 8b-r! JW4 oil supply passage, 9a, 9b, 9c, 9d-Inn extraction oil supply port 10...
Lubricating oil supply means, 12.13... Pressure sensor (operation start detection means) 14.15-... Temperature sensor (Ii degree detection means), 1
6... Rib, 101-... Output shaft (rotating shaft), 104
...Low and reverse brake (frictional engagement element), 108...Band brake (frictional engagement element), 109
...Transmission case (case member) Patent applicant: Nissan Motor Co., Ltd. Figure 4 Figure 5 Figure 6 Figure 10 Figure 11 t+ t:zt3t4ts t6 Ginbetsu Figure 13 Figure 14

Claims (4)

[Claims] (1) In an automatic transmission having a frictional engagement element, a lubricating oil supply means for supplying lubricating oil from the outer circumferential side of the frictional engagement element is provided above the rotating shaft of the automatic transmission in a case member of the automatic transmission. A lubricating oil supply device for an automatic transmission, characterized in that it is provided at a position. (2) A lubricating oil supply device for an automatic transmission according to claim 1, characterized in that a rib extending in the rotation axis direction is provided on the outer periphery of the case member of the automatic transmission, and a lubricating oil supply means is provided on the rib. . (3) an operation start detection means for detecting the start of operation of the frictional engagement element; The lubricating oil supply device for an automatic transmission according to claim 1 or 2, characterized in that the lubricating oil is supplied to the frictional engagement element. (4) Temperature detection means for detecting the temperature of the frictional engagement element, and the lubricating oil supply means supplies lubricating oil to the frictional engagement element while the temperature detected by the temperature detection means is equal to or higher than a predetermined value. 4. A lubricating oil supply device for an automatic transmission according to claim 1, wherein the lubricating oil supply device supplies a lubricating oil supply device for an automatic transmission.