JPS60237250A - Speed change mechanism of change gear for vehicle - Google Patents

Abstract

PURPOSE:To shorten the total length of the change gear by a method wherein a mono-directional clutch, arranged in parallel to a wet type multi-disc clutch, is provided in the drum of said wet type multi-disc clutch. CONSTITUTION:The mono-directional clutch F1 is arranged between an output member or the outer periphery of inner tube of a clutch drum 62 and an input member or a turbine shaft 16. The mono-directional clutch F1 is consisting of a plurality of sprags provided annularly, an inside holder 802 as well as outside holder 803 arranged with the sprags equally on a circumference and operating all of the sprags simultaneously, and a ribbon 806 providing the sprags with a force to contact them with an outer race 804 and an inner race 805 while the outer race 804 is engaged with the inner periphery of a front side tubular section 161 through a spline and the inner race 805 is engaged with the inner peripheral tubular section 621C of a clutch drum 62 through the spline.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field] The present invention relates to an automatic transmission for a vehicle, and particularly to a transmission mechanism suitable for an automatic transmission for a vehicle using two planetary gear devices.

[Prior Art] United States Patent Publication U, S, P, 361183
No. 5 has a fluid torque converter, three clutches,
Consists of two planetary gear sets with one one-way clutch, three brakes and two one-way brakes,
A vehicle transmission is disclosed that provides four forward speeds including overdrive and one reverse speed. In this way, the engagement elements for four forward speeds and one reverse speed using two sets of conventional planetary gear systems include three clutches, three brakes, and a one-way clutch (
Since three (including one-way brakes) are required, it has been difficult to make the transmission smaller and lighter, contrary to the recent demand for smaller and lighter weights.

[Object of the Invention] The object of the present invention is to develop a transmission mechanism for a vehicle transmission that can shorten the overall length, particularly an automatic transmission with 4 forward speeds and 1 reverse speed using two sets of planetary gear devices, and an automatic transmission with 3 forward speeds and 1 reverse speed. It is an object of the present invention to provide a transmission mechanism suitable for constructing a transmission without increasing the overall length or the number of shafts.

[Structure of the Invention] A first invention of the transmission mechanism for a vehicle transmission of the present invention includes an input member, an output member, a wet type multi-plate clutch for engaging and disengaging the input member and the output member, and the wet type multi-plate clutch for engaging and disengaging the input member and the output member. In a transmission mechanism for a vehicle transmission having a multi-disc clutch and a one-way clutch connected in parallel, the one-way clutch is disposed within a drum of the wet multi-disc clutch, and the one-way clutch has an inner race. is connected to the outer peripheral side of the inner cylinder of the drum, and the outer race is connected to the inner peripheral side of the inner peripheral hub of the wet type multi-disc clutch, and the second
The invention relates the input shaft to input elements of the first and second planetary gear devices, such as first and second planetary gear devices having a sun gear, a pinion gear, a planet carrier, and a ring gear. a plurality of clutch means that engage or releasably connect the anti-fJ elements of the first and second planetary gear units to a fixed member; and an output shaft connected to the output element of the second planetary gear device, and by selectively engaging or disengaging the plurality of clutch means and the plurality of brake means, the gear is shifted to four forward speeds and one reverse speed. In the transmission mechanism of an automatic transmission for a vehicle, the plurality of clutch means include a first clutch that connects the input shaft and the sun gear of the first planetary gear unit so as to be engageable and disengageable; a second clutch that engageably and releasably connects the ring gear of the first planetary gear device; a third clutch that connects the input shaft and the sun gear of the second planetary gear device so that they can engage and release; a one-way clutch connected in parallel with the third clutch, disposed within the drum of the third clutch, having an outer race connected to the input shaft and an inner race connected to the outer periphery of the inner cylinder of the drum; The plurality of brake means include a first brake that releasably connects the sun gear of the second planetary gear set to the fixed member, and a planet carrier of the second planetary gear set that can engage and release the planet carrier of the second planetary gear set to the fixed member. a second brake connected to the
a one-way brake connected in parallel with the second brake, and the output elements of the first and second planetary gear units include a planetary carrier of the first planetary gear unit and a ring gear of the second planetary gear unit. The ring gear of the first planetary gear set and the planetary carrier of the second planetary gear set are connected.

[Effects of the Invention] The speed change mechanism of the vehicle transmission of the present invention having the above configuration has the following effects.

b) The overall length of the transmission mechanism can be shortened by arranging the one-way clutch inside the annular drum and connecting the inner race of the one-way clutch to the outer circumferential side of the inner cylinder of the annular drum.

Mouth) An automatic transmission with four forward speeds and one reverse speed is composed of two planetary gear devices, three clutches, two brakes, one one-way clutch, and one one-way brake, and the one-way clutch is arranged inside the annular drum of the clutch for an automatic transmission with three forward speeds and one reverse speed.
They can be of similar size and weight.

c) Since the number of frictional engagement elements can be reduced, the amount of drag when the reduced amount of frictional engagement elements are not engaged can be eliminated, so transmission efficiency can be improved.

2) Since the number of frictional engagement elements can be reduced, the control device for the frictional engagement elements can be made lightweight and compact.

e) Since it is possible to construct an automatic transmission with four forward speeds and one reverse speed with a small number of parts, production costs can be kept low.

[Embodiment] Next, a transmission mechanism of a vehicle transmission according to the present invention will be explained based on an embodiment shown in the drawings.

FIG. 1 is a schematic skeletal diagram of an automatic transmission for a vehicle with four forward speeds and one reverse speed equipped with the transmission mechanism of the vehicle transmission of the present invention in which the torque converter 10 is applied to the power transmission device, and FIGS. The figure shows its cross-sectional view.

This automatic transmission for a vehicle includes a torque converter 10 that is a power transmission device that transmits the rotational output of an engine, a transmission 20 that increases or decelerates the rotational output transmitted by the torque converter 10, and a transmission that increases or decreases the rotational output transmitted by the torque converter 10. It consists of a differential mechanism 30 that transmits rotational output to the drive shaft.

The torque converter 10 is a normal one that includes a pump impeller 11, a turbine impeller 12, a stator 13, and a direct coupling clutch 14, and behind it is an internal gear that has an external gear 15A, which is an oil pump, and an internal gear 15B. gear pump 1
The pump impeller 11 and the external gear 15^ of the internal gear pump 15 are driven via a power transmission case 10^ connected to the crankshaft 1 of the engine, and receive the rotation of the pump impeller 11. , the turbine impeller 12 is connected to a turbine shaft 16 that serves as an input shaft of the transmission @20,
The stator 13 is a transmission case 10 whose inner periphery is a fixed member.
It is provided on the outer periphery of the one-way latch FO connected to 0.

The transmission 20 includes a front planetary 40 consisting of a front sun gear 41, a front pinion gear 42, a front planet carrier 43, and a front ring gear 44, and a rear planetary 40 consisting of a rear sun gear 51, a rear pinion gear 52, a rear planet carrier 53, and a rear ring gear 54. The planetary 50, the multi-disc clutch C1 that engages and disengages the turbine shaft 16 and the front sun gear 41, and the multi-disc clutch C1 that engages and disengages the turbine shaft 16 and the front ring gear 44 are provided on the outer periphery of the multi-disc clutch C1. Multi-disc clutch C2, multi-disc clutch C1, multi-disc clutch C
2 and a one-way latch F1, which is an output member that covers the outer periphery of the front planetary 40, is connected to the rear sun gear 51 at one end, and has an annular end and is disposed between the turbine shaft 16 and the turbine shaft 16. A multi-disc clutch C3 is provided on the outer periphery of the one-way clutch F1 that engages and releases the clutch drum 62, and a first clutch C3 that is fixed to and released from the transmission case 100 from the outer periphery of the clutch drum 62.
A band brake B1 which is a brake, a multi-plate brake B2 which fixes the rear planet carrier 53 of the rear planetary 50 to the transmission case 100 which is a fixed member, and a one-way brake F2 which allows the rear planet carrier 53 to rotate in only one direction. , an inner peripheral countershaft 64 that connects the front ring gear 44 and the rear planet carrier 53 , and an output shaft 65 that connects the front planet carrier 43 and the rear ring gear 54 .

The differential mechanism 30 includes a differential pinion shaft 31 and a differential pinion 32.
, a differential side gear 33, and the power is transmitted from the output shaft 65 to the differential mechanism by the output gear 34 provided at the end of the output shaft 65, and the output gear 3.
The input gear 35, the counter shaft 36, the drive pinion 31, and the reduction gear 38 are arranged corresponding to the right wheel drive shaft 39R1, the left wheel drive shaft 39[
transmitted to.

The turbine shaft 16, which is the input shaft of the transmission 20, has multiple plates on the input side of the multi-disc clutch C3 in the transmission 20 spline-fitted on the outer periphery, and an outer race of the one-way latch F1 on the inner periphery. A front cylindrical part 161 spline-fits the input side of the multi-disc clutch C1, a rear inner circumferential cylindrical part 162 that splines the multi-plates on the input side of the multi-disc clutch C1 to the inner circumferential side, and It is branched into a rear outer peripheral cylindrical portion 163 into which the multiple plates are spline-fitted to the inner peripheral side.

The multi-plate clutch C3 includes a front cylindrical portion 161 that is an input member.
A plurality of input plates 701 are spline-fitted to an outer circumferential spline 161A provided on the outer circumference of the input plate 701, and a plurality of input plates 701 are disposed on the inner circumference of the outer circumferential cylindrical portion 621A of the piston cylinder portion 621 of the clutch drum 62 which is an output member disposed on the outer circumference of the input plate 701. Output plates 702 are spline-fitted to the provided inner peripheral spline 621B and are alternately arranged on the plurality of input plates 701.
an annular piston 704 disposed within a piston cylinder section 621 that engages and releases the multi-plate engaging section 703; and a multi-plate engaging section that drives the annular piston 704. Annular piston 7 that engages 703
04 and the hydraulic servo C'-3 formed between the piston cylinder part 621, the return spring 705 that presses the annular piston 704 toward the hydraulic servo C-3 side, and the return spring 105 to the piston cylinder part 621.
and a spring fitting 706 disposed on the inner periphery of the inner cylindrical portion 621C, and the supply of hydraulic oil to the hydraulic servo C-3 and the exhaust pressure are carried out through the inner cylindrical portion communicating with the hydraulic servo C-3. It is operated by a hydraulic control device (not shown) via an oil passage 621d provided in the shaped portion 621C.

The one-way clutch E1 includes a plurality of sprags 801 provided in a ring shape, and the sprags 801 are arranged equally on the circumference, and an inner retainer 802 and an outer retainer 803 serve to operate all the sprags 801 simultaneously. , is composed of a ribbon spring 806 that applies a force to bring the sprag 801 into contact with the outer race 804 and the inner race 805; The inner race 804 is connected to the inner circumferential spline 16 provided on the inner circumference of the front cylindrical portion 161.
1B, and the inner race 805 is spline-fitted to an outer circumferential spline 621e provided on the outer circumference of the inner circumferential cylindrical portion 621C of the clutch drum 62. Note that the one-way clutch described above may be configured such that the outer race or the inner race side is formed integrally with the connecting member in order to reduce the number of parts.

Next, Table 1 shows the set speeds of the transmission gears and the operating states of the clutches and brakes of the transmission device 20 having the above configuration.

Table 1 In Table 1, ○ indicates engagement of the friction engagement element, τ-) indicates engagement only during engine braking, blank indicates release, and ◎ indicates a locked state of a one-way clutch or one-way brake.

Next, the operation according to the above-mentioned set gear position will be explained.

When the transmission @20 is set to the first speed state.

As shown in Table 1, the multi-disc clutch C1 and the one-way brake F2
is in an engaged state. The engine rotation input transmitted via the torque converter 10 is transmitted via the multi-plate clutch C1, and the front planet carrier 43 attempts to rotate in the same direction as the input rotation, but the front ring gear 44 receives rotational force in the opposite direction to the input rotation. is added. For this reason, the front ring gear 44 is fixed by the action of the one-way brake gear F2 connected via the inner peripheral subshaft 64, so the rotational output transmitted to the front sun gear 41 is transmitted to the front planet carrier 43 and the output shaft 65. The reduction ratio of the input rotation is 1+1/rl (rl = front gear 41
number of teeth/number of teeth of front ring gear 44) and is output.

When the transmission 20 is set to the second speed state.

As shown in Table 1, multi-disc clutch C1, band brake B1
is engaged. Engine rotation input transmitted via the torque converter 10 is transmitted to the front sun gear 41 of the front planetary 40 via the multi-disc clutch C1. On the other hand, since the band brake B1 is engaged, the rear sun gear 51 is fixed via the clutch drum 62, so the rotational output of the front sun gear 41 drives the rear ring gear 54, and since the rear sun gear 51 is fixed, the rear planet The carrier 53 is driven at 1/1 of the input rotation of the rear ring gear 54 + r2 (r2 = number of teeth of the rear ring gear 51/number of teeth of the rear ring gear 54), and the front ring gear 44 rotates in the same way. When the input rotation transmitted to the sun gear 41 is transmitted to the output shaft 65, the reduction ratio (rl + r2 x r2
+r2)/rlX (1+r2) and output.

When the transmission 20 is set to the third speed state.

As shown in Table 1, multi-disc clutch C1, multi-disc clutch C2, and one-way latch F1 are engaged. Since the rotational input transmitted via the torque converter 10 is simultaneously engaged with the multi-disc clutch C1 and the multi-disc clutch C2, the front sun gear 41 and the front ring gear 44 rotate with the input rotation. On the other hand, when the multi-disc clutch C2 is engaged, the rear planet carrier 53 also rotates by 1fl due to the input rotation.
A. As a result, the rear sun gear 51 tries to rotate in the direction opposite to the input rotation direction, but the one-way latch F1
is locked, and the clutch drum 62 also rotates at the input rotation speed.

As described above, since the front planet carrier 43 and the rear ring gear 54 rotate at the input rotation speed, the rotation of the output shaft 65 is outputted at a reduction ratio of 1, which is the same as the input rotation.

When the transmission @20 is set to the 4th speed state.

As shown in Table 1, multi-disc clutch C2, band brake B1
is engaged. The engine rotation input transmitted via the torque converter 10 is transmitted to the front ring gear 44 and the rear planet carrier 5 by engagement of the multi-plate clutch C2.
3. At this time, since the band brake B1 is engaged, the rear sun gear 51
is fixed. As a result, the rotational output transmitted to the rear planet carrier 53 drives the ring gear 54 via the rear binion gear 52, and is output to the output shaft 65 after being increased in speed to a reduction ratio of 1/(1+r!) of the input rotation. .

When the transmission 20 is set to the reverse state.

As shown in Table 1, the multi-disc clutch C3 and the multi-disc brake B2 are engaged. The input rotation transmitted via the torque converter 10 is transmitted to the rear sun gear 51 via the clutch drum 62 by engagement of the multi-disc clutch C3. At this time, since the rear planet carrier 53 is fixed to the transmission case 100 by the engagement of the multi-disc brake B2, the rotational output transmitted to the rear sun gear 51 is transmitted to the rear binion gear 5.
2 to drive the rear ring gear 54, and output the input rotation to the output shaft 65 as a reduction ratio of -1/2 and the opposite rotation.

[Brief explanation of the drawing]

FIG. 1 is a schematic skeletal diagram of a vehicle automatic transmission equipped with the transmission mechanism of the vehicle transmission of the present invention, FIG. 2 is a sectional view of the vehicle automatic transmission shown in FIG. 1, and FIG. 3 is a sectional view of the vehicle automatic transmission shown in FIG. 3 is a partially enlarged view of the automatic transmission for a vehicle shown in FIG. 2. FIG. In the figure 16... Turbine shaft 4o... Front planetary 50... Rear planetary 62... Clutch drum 65... Output shaft C1, C2, C3... Clutch B1, B2... Brake FO, Fl...
One-way clutch F2... One-way brake agent Kenji Ishiguro

Claims (1)

[Scope of Claims] 1) An input member, an output member, a wet multi-disc clutch that engages and disengages the input member and the output member, and a one-way clutch connected in parallel with the wet multi-disc clutch. In the transmission mechanism for a vehicle transmission, the one-way clutch is disposed within a drum of the wet multi-plate clutch, an inner race of the one-way clutch is connected to an outer circumferential side of an inner cylinder of the drum, and an outer race is connected to an outer circumferential side of an inner cylinder of the drum. A transmission mechanism for a vehicle transmission, characterized in that a race is connected to an inner circumferential side of an inner circumferential hub of the wet type multi-disc clutch. 2) engaging or engaging an input shaft and first and second planetary gear units having a sun gear, a pinion gear, a planet carrier, and a ring gear; and the input shaft and input elements of the first and second planetary gear units; a plurality of clutch means releasably connected; a plurality of brake means releasably engaging or releasably connecting reaction elements of the first and second planetary gear devices to a fixed member; It has an output shaft connected to an output element of a planetary gear system, and by selectively engaging or disengaging the plurality of clutch means and the plurality of brake means, a speed change of four forward speeds and one reverse speed is performed. In the transmission mechanism of an automatic transmission for a vehicle, the plurality of clutch means include a first clutch that connects the input shaft and the sun gear of the first planetary gear unit so as to be engageable and disengageable; The second tl star gear unit is engageably and releasably connected to the ring gear of the first tl star gear device.
a third clutch that engageably and releasably connects the input shaft and the sun gear of the 212th star gear unit; a third clutch connected in parallel with the third clutch and disposed within the drum of the third clutch; , a one-way clutch in which an outer race is connected to the input shaft and an inner race is connected to the outer periphery of the inner cylinder of the drum, and the plurality of brake means engage the sun gear of the second planetary gear device with the fixed member. a first brake that is releasably connected to the planet carrier of the second planetary gear device; a second brake that connects the planet carrier of the second planetary gear device to the fixed member in a releasable manner; and a one-way brake that is connected in parallel with the second brake. The output elements of the first and second planetary gear devices are the planetary carrier of the first planetary gear device and the ring gear of the second M star gear device, and the ring gear of the first M star gear device; A transmission mechanism for an automatic transmission for a vehicle, characterized in that a planetary carrier of a second planetary gear device is connected.