JPS60175845A - Multistage gear speed change device - Google Patents

Abstract

PURPOSE:To keep axial dimensions small by obtaining a predetermined speed change stage by means of selecting and using sets of gears composed by output gears connected to an output shaft and input gears provided on intermediate shafts. CONSTITUTION:A plurality of parallel intermediate shafts 37, 38 and an output shaft 36 which is parallel with the intermediate shafts 37, 38 are provided, and sets of gears are composed by output gears 53, 54, 58, 62 connected to the output shaft 36 and input gears 43, 44, 46, 47, 55, 59, 61, 63 on intermediate shafts 37, 38 so as to provide a speed change stage by engaging the output gears with the input gears. By selecting and using the sets of gears, a predetermined speed change stage can be obtained. As the number of sets of gears equal to the number of intermediate shafts 37, 38, can be arranged in the radial direction of the gear speed change device, the axial dimensions of the gear speed change device can be shortened equivalently to that number, then even if multistage gear speed change device is employed, it can be loaded on FF vehicle.

Description

[Detailed description of the invention]

(TECHNICAL FIELD) The present invention relates to a parallel shaft type multi-stage gear transmission which is particularly useful as a gear transmission component of an automatic transmission. Therefore, the power transmission efficiency is poor, and the gear transmission section is made up of at least two planetary gear sets (7-V, so it becomes a high f curve and is a winner. With these as the main J Sendai, a torque converter is not required. Therefore, it is being considered that a parallel shaft type gear transmission device A, which has a stylish gear transmission section, can be used as an automatic transmission.
There is something like the one described in the magazine 1-Automotive Engineer J (Automotive Engineer J) published in February 1988. As shown in FIG.
1 input shaft 82 and one output shaft 5 parallel to these input shafts, the input shaft IK fixes the rickshaws 6 and 7 for the first and eighth forward speeds, and also supports the fifth forward speed. In addition to rotatably providing the manual gear 8, a reverse input gear 9 is fixed, and second and fourth forward gears 10 and 11 are fixed to the input shaft 4. Also, the output shaft 5 has an output 1 that meshes with the input gear 6.7.
tJlijjl 2 , 13 are rotatably provided, and the output gear 14 meshing with the input gear 8 is fixed, and the input gear 10 . IIK'i! I+1 matching output 1 out of 100.
5, 16 are provided on the rotating car rE, and the input float 8
is manually operated by synchronizer clutch 17.
3, the output gears J2 and 18 are output by the synchronizer clutch 18, and the output gears 15 and 16 are output by the synchronizer clutch 19. 111115 K Yui;”
JV! l'! shall be. Also, synchronizer clutch 18
A reversing output gear 20 is integrally molded in alignment with the human-powered south center 9, and a reverse idler 2 is provided so as to be freely movable in the P+1+ direction so as to mesh appropriately with the floats 9 and 20.
In such a 4tr+ configuration (in this case, 1TR+
'41 Middle class 0,12, ], 0, l 5.7,18
．． 11゜1 (by using 1, 8, 14 or 9.20.21 quickly, you can change the forward 1st gear, 2nd gear, 3AX, 4th faster, 51st and 1st or alternative gears) However, in such a +17 [configuration, the number of gears is equal to the number of gears, T, 11 Ir order, j'+1 medium shift p, 4 ji,'
7, it must be arranged in the direction of the i-axis.
Avoid C) Renat・. On the other hand, a 7th grade elementary school student who was in critical condition today died at 84 years old.
As a way to address this issue, converting automobiles to front-wheel drive (FF) is a good idea.
-Mitsuki)ru. In this case, the engine (prime mover) is
:Ql! ' + □, therefore, the float transmission 1 (1 is l
i' It is impossible to install it on F East. On the other hand, there is a tendency for transmissions to have multiple gears for the purpose of improving fuel efficiency and driving performance. If the number of stages is increased to meet the above requirements, the dimensions in the clear direction will become too large to be mounted on a front-wheel drive vehicle. It would be nice if it were possible to install it in the F.
%! The purpose is to provide a solution to the above-mentioned problems. (4) Structure of the Invention For this purpose, the multi-stage gear transmission rj' of the present invention comprises a plurality of mutually parallel intermediates 11+, to which motive power is selectively transmitted via individual clutches; C) one output shaft parallel to the intermediate '11111, and the output

[
([10f
With the input Yamanaka provided in the intermediate spider 1 so that the intermediate spider 1 provides t = 'l + i,
4, +ii +! By using reverse twisting of 14, IJ
T'1. i, muko・]! It is characterized by having 1.1 stages. (Ii)', J2h'lli I column IJ, bottom, this I3 light's actual example of the basket, and congratulations on the front page. No. 11 No. 1 is the multi-stage gear transmission device 1 of the present invention! In this figure, 80Bj drive (engine as number; 41G:L) is the crankshaft.The engine power from the crankshaft 31 is transferred to the first clutch 8.
2 and the second input terminal 33 as appropriate. +'G 2 can be transmitted to the input shaft 85, and these human forces 1111 are similar to the same axis. Coaxially facing input 1iIllI34 and output tll++
36 is provided, and a first intermediate shaft 87 and a second intermediate shaft 88 are provided parallel to this output shaft. intermediate shaft 37
is the first main gear fixed to the input +il+84
89 and meshing with this, the intermediate shaft 37 + C fixed 11', +'
The intermediate 1N1188 has a second main gear 41 fixed to the human power side 185 and a second main gear 41 fixed to the intermediate shaft 88 meshing with this. The input shaft 85 is used as driving oil through the drive gear 42 of the input shaft 85. On the first intermediate shaft 87, the first forward speed and the third continuous human power switch 1
Wheels 48 and 44 are rotatably provided, and a synchronizer clutch 45 is interposed between these manual gears. This synchronizer clutch 45 is slidably and drivingly connected to the central shaft 37, and is connected to the internal input gear 48 in the illustrated neutral position 11'j.
．． All of the 44 are intermediate. 11+87, but selectively drives and couples the input gear 48 to the intermediate shaft 37 when moving to the left in the figure, and the input gear 44 to the intermediate shaft 87 when moving to the right in the figure. shall be. A manual gear 46.4 for forward second and fourth speeds is mounted on the second intermediate shaft 88. are rotatably provided, and a synchronizer clutch 48 is interposed between these human-powered vehicles. This synchronizer clutch 48 has the same tpζ configuration as the synchronizer clutch 45, and when moving to the left from the neutral position 16 in FIG. 88. The intermediate shaft 88 is further rotatably provided with a reverse input gear 49, which can be driven and coupled to the intermediate ikl+ 88 as appropriate by a synchronizer clutch 50, and the gears 89.49
A reverse idler 51 is provided between them to constantly mesh with them. The output shaft 86 can be directly connected to the human power i1'llll 84 by means of the synchronizer clutch 52, and the output gears 58, 54 are fixed to the output shaft 86. The output gear 58 is always meshed with the input gear 48, 46, and the output gear 54 is in mesh with the input gear 4.
4,4? are always engaged. The operation of the above embodiment will be explained next. When the first clutch 82 and the second clutch 88 are turned off, engine power from the crankshaft 81 is not transmitted to both input shafts 84 and 85, and the multi-vehicle transmission is powered from the output shaft 86. It becomes a neutral state in which no output occurs. In order to obtain the first forward speed, the synchronizer clutch 45 is moved to the left in the figure, and the input gear 4i is connected to the intermediate shaft 87.
After the driving connection is made to the first crank 82, the first crank 82 is turned on. Thus, the engine power from the crankshaft 81 passes through the clutch 32, input shaft 84, main gear 89, drive gear 40, intermediate shaft 87, input gear 4B, and output gear 58, and is output from the output shaft 36 to obtain the first forward speed. be able to. When shifting from the first forward speed to the second forward speed, the synchronizer clutch 48 is moved to the left in the figure in advance, and the input gear 46
is drivingly connected to the intermediate shaft 88, and in this state, the first clutch 82 is turned off and the second clutch 8B is turned on. As a result, the engine power is transferred from the crankshaft 81 to the input shaft 85, the main gear 41, and the drive gear 4.
2. The output 1iIll 86 passes through the intermediate shaft 88, the input gear 46, and the output gear 58, and the second forward speed can be obtained. When shifting from the second forward speed to the eighth forward speed, the synchronizer ring 45 is moved to the right in the figure in advance, the input gear 44 is drivingly connected to the intermediate shaft 87, and in this state, the second clutch 88 is activated. Turn on the first clutch 3z while turning it off. From this LiC, the engine power from the crankshaft 8 is transmitted to the input shaft 34, twin gear 39, and drive gear 40.
．． The output is now output from the output shaft 8 (5) through the intermediate shaft 87, the human powered Yamanaka 44, the output gear 54, and the 8th forward speed can be achieved. When shifting to 4th speed, move the synchronizer clutch 48 to the right in the figure in advance, and drive input C plane 1 (47 to intermediate 11'+ll 88!b).
In this state, the second clutch 83 is turned on while the clutch 82 is turned off on the 11th day. As a result, engine power from the crankshaft 81 is transferred to the input shaft 84, main shaft 41. drive gear 42,
Intermediate 11111I38, human power mountain 4/7, output mountain Qj
54 is output from the output shaft 86 at 11t, and the fourth forward speed can be obtained. Previous i1'-24% 4, i, 4ji, to 5th:,
When shifting gears to i44, move the sink 11ner clutch 52 to the left in the diagram in advance, and use manual force 9.

[11 do 14/i
In this state, the first clutch 32 is turned on while the second clutch 38 is turned off. As a result, the engine power from the crankshaft 31 is outputted from the output shaft 36 via the input shaft 84 and the synchronizer clutch 5z without being changed, making it possible to obtain the front first position and fifth gear. . Finally, in order to select reverse, the synchronizer clutches 4, 8, 50 are moved to the left in the figure in the neutral state, and the input gears 46, 49 are drivingly connected to the intermediate Il+1138. After that, when the first clutch 32 is turned on, the engine power from the crankshaft 31 is input to the engine 34.
, main gear 39, reverse idler 51, input gear 49, intermediate shaft 88, human power 1ψ] cars 4 and 6, output float 53
A & output 11nn 8 A lowers reverse rotation It is possible to obtain each of the gears, but as described above, the gears are changed by turning off one of the first and second clutches 82 and 83 and turning on the other. Because of this, the gear shift can be carried out while constantly transmitting power, and the float transmission part of the automatic transmission (~ [ is also a practical oil. Note that the clutch for each gear stage: U2, 83
, 45 , 48 , 50 , 52 cooperative crops 1. The following table shows I) and A). Table 1 and Figure 2 show the present invention's multi-stage 1ψ (another example of a vehicle transmission;
t'++ The same parts as in Figure 1 are not indicated by the same reference numerals. In this example, instead of the reverse input gear 49, synchronizer clutch 50, and reverse eye 51 in FIG.
6 and a reverse idler 57 are provided. The gear 55 is rotatable on the intermediate shaft 87-H (as well as the synchronizer clutch 56 1゛〕1〕1 middle shaft 3).
7 has a driving connection b' function. Then, the output gear 58 is fixed on the output shaft 86, and the reverse idler 57 is always engaged with the output gear, the reverse manpower, and the first wheel 55.In this example, the intermediate shaft On 88, human power t4:'+ car 59 for forward 0 speed is freely provided and added at times 1jj7,
This gear 59 can be driven and coupled to the intermediate +11+ a B as appropriate by a synchronizer clutch 600 on the right side of the figure. In the borrowing of this example, the 5th speed of the first forward train can be obtained in the same way as the example shown in the figure, but njl), 1
．． 6 To change from the 5th gear to the 6th gear added in this example In this state, the first clutch 32 is engaged and the second clutch 83 is turned on.The engine movement and power from the crankshaft 31 is transferred from the IC to the human driver 85.
Main gear 41, drive gear 42, intermediate i1+111
88, by using the human power f' noise wheel 59 and the output gear 58, the output power becomes smaller than 6, and the 6th gear can be shifted by 1 day.Also, in order to select reverse , the synchronizer clutch 56 is moved to the right in the figure.
After drive-coupling the clutch 3 to the intermediate shaft 37, the clutch 3 of 11
Turn on 2. As a result, the engine power from the crankshaft 81 is transferred to the input power 84, the main gear 89, and the drive gear 40. Intermediate+ia+8? , human gear 55
By using the reverse idler 57 and the output IM/1 vehicle 58, the output is now output from the output shaft 86 in an offensive direction.
Reverse movement can be done by i. In this example, the combination operation of clutches 82° 88.45, 48, 52, 50, 600 for each gear is shown. The result is as shown in the following table. FIG. 3 shows still another example of the multi-j sand mountain 11 variable speed changing device of the present invention, in which the same parts as in the 11th engine (K) are designated by the same symbols VC-'C. In this example, the forward 5th gear In order to obtain the synchronization, the input and output (34, 36) are not required, therefore, the synchronizer clutch 52 in the first L gear 1 is omitted and the synchronizer clutch 52 is omitted.
An output fk eetun 62 is provided to output ``i'iil:ifl+,'' and the fifth floor is outputted by these floats. At the time of IT1J, it meshes with the 11J power wheel 62 and provides the front hole 6th speed: 4; Ertun connection device ft and Buez'. Human power tooth 1j 6] is adjacent to human power Yamanaka 4.4 and intermediate tl.
These input floats 61.degree. 41 can be selectively and drive coupled to the intermediate Ill 37 by means of a synchronized synchronizer clutch 64. In A/r, the human gear 43 is driven by a synchronizer clutch 65 to the intermediate shaft 37 (nJ/+i, 7). Hard 98 L, human power Yamanaka 63
1 input H wheel 47 and 1 solenoid are combined to form an intermediate shaft 8s-1:
68147 in these input diagrams is the same width synchronizer clutch 66.
Optionally, the drive coupling 11 is attached to the intermediate shaft 8.8.
h and i). Because of this, the human power Yamanaka 46 is lk to the input float 49! il, these input gears can be selectively driven to the intermediate shaft 88 by a synchronizer clutch 67, both of which are 111i. In the configuration of this example, 1 (8.
For speed and reverse, the synchronizer clutch 05 is set to the right, the synchronizer clutch 67 is set to the right, the synchronizer clutch 64 is set to the left, the synchronizer clutch 66 is set to the left, and the synchronizer clutch Ofl and 67 are set to the left.
By switching the first and second clutches 82.38 on and off in the same manner as described in 1-111 in FIG. You can do it. By the way, the previous J! IU was trying to shift from 4th gear to 5th gear 1)
In this case, the synchronizer clutch 64 is moved to the right in advance, and the input gear 61 is connected to the intermediate 'H1+s7 for 1 drive. In this state, the second clutch 8B is not engaged, and the first clutch 32 is turned on. As a result, the engine power from the reflux shaft 31 is input to 1 liter + 34
・, Main gear 39, Intermediate 411187, Manual toothing (
I], output mountain 11j6';! , then output flQhaa
More output than 116 yen (Buri 1. 5th forward gear
a). Next, when shifting from 14.5 speed to 6th speed, the synchronizer clutch 66 is moved to the right in advance, and the human power tooth Ili, 68 is drive-coupled to the intermediate shaft 88. While doing this alone, turn off clutch 32 of r4i and l, then turn on clutch 88 of r4i and l). As a result, the engine power from the crane 1, the engine power 31 is transferred to the human power spider 135, and the main gear 41. drive gear 42,
Intermediate shaft 38, manual tooth jJ, j Q 3, output m rl
It is possible to change the number 62 to 1c so that the output is output from 11 + 8 o, and change the n15 6th gear to 1:). (With two clutches 82, .8 B for each gear stage. If the combined operation of fl 5, 67, 64, and 66 is a flame, the result will be as shown in the following table. Table 8 Thus, the multi-stage gear transmission of the present invention For example, 1゛■ is -1-
J/T, the power of the original 11Φ80 is selectively transmitted to multiple (two in the illustrated example) peaks through individual clutches 82 and 83. , intermediate shaft 8
7.88, and an output shaft 8 (1) parallel to these intermediate axes, and an output shaft 53° 54.
58, 62 and mesh with these to provide a gear stage 4/
Intermediate: 1iIi + a 7, a to a; input gear 43, 44, 4 (1, 47, 55, 59, 6
By selectively using a gear set that forms ff7 with 1°68 and Align the gear set according to the gear transmission mechanism (3r2 ff
1l+, and its fraction j'(I change, i・(l
The dimensions of the device 1'1 in the X and IH directions are shortened and borrowed. Therefore, the main gear transmission device itself is multi-staged and one side of the engine is installed.
Even when used on white type 1'i'F cars, it is sufficient to use R5-mounted r'J' f.
fhito/Xru. The simple f1'1 picture on page 1/IX1 is an abbreviated +IN diagram of the multi-stage float transmission system of the present invention, 24s.
2 and 8 respectively show two other examples of the device I'''1' of the present invention, and FIG. la, i + k) in the diagram. :40...Engine (drive 1) 8]...Crankshaft 32...First clutch 8B...Second clutch 84...First input side 1:85... ...Second human-powered cicada 1 86...Output ζ1
11.37...First intermediate shaft 38...Second intermediate shaft 89, 4.1...Main gear 40, 42...
・Dry mite 1゛ya 4.8...1st speed manual gear 4
4... 2nd speed river human powered float 45. 4.8, 50... Synchronizer clutch 46... 8th speed human powered float 4.
7... 4th speed river input meat car 4.9... Human power m for reversing
A! ', 51... Reverse idler 52... 5th
Speed selection synchronizer clutch 5f3, 54.・・・
・Output gear 55...manpower for reverse (+, +wheel 56,
60... Synchronizer clutch 57... Reverse idler 58... Output tooth off. 59... father-in-law) 6th speed river human powered float 61... 5th speed river human powered float (52... Output gear 63... 6th continuous human powered float +
If, East 64-67... Synchronizer clutch. Figure 4

Claims (1)

[Claims] 1. A plurality of mutually parallel intermediate +1Ilbs to which power from the prime mover is selectively transmitted via individual clutches;
an output shaft parallel to these intermediate shafts, and an output gear connected to the output shaft and an input gear provided on the intermediate shaft so as to mesh with the output gear to provide a gear stage. Tode↑
1. A multi-stage transmission device characterized by being configured to obtain a predetermined gear stage by selectively using the Φ-Φ set formed in 1.