DE1801249A1 - Multi-speed transmissions for vehicles, especially for motor vehicles - Google Patents

Description

Patent attorney
Dipl.- h ν · - "· ' ^Λ / ·> 339Ι 8 Munich 13, O 4th October 1968

Hohenstaufenstrasse ΤτβΙ. 558111 FK-2310 1801249

FORD-Werke, public limited company

5 Cologne-Deutz 1
Ottoplatz 2

"Multi-speed transmissions for vehicles, especially for

Motor vehicles "

For this registration, the priority of registration Ser.-No. 680 239 of November 2, 196? in the United States claimed by North America.

Brief description

The invention relates to a multi-speed transmission for vehicles, especially for motor vehicles. This transmission includes one toothed torque path with two slow gears between the torque shaft and the output shaft, a direct gear and an overdrive. The input link for the transmission is with the turbine part of a hydrokinetic torque converter connected, the pump part is connected to the torque source. The torque travel for the direct gear is divided. A friction clutch for the overdrive gear is arranged between the transmission and the output member. The drive

909832/0801

■ .- ■■■ - 2 -

shaft extends through the gearbox % n this clutch »

Haujgtbes more O ₁ IbUiIg -

The invention includes a planetary gear with the possibility of four forward gears and one reverse gear, one of the four forward gears 1st © in Senne 11 gear. The W @ © Sasel can be seen between the individual courses by optionally tightening
and loose iron two Healctiomsbreasen and of three optionally indentable! Beibkupplei & ^ en be eraiolt. -

To use the clutch to be the Scfemallgang and an interim> eoh®nc, ^ tens zn switching © »« BiiSise clutch within the Pia · netengetriofeoo on. ο & ηοτ * position arranged ₉ welch® of the
both of them are far from the couplings and from the hydrokinatic waac ler.

When ν orb © known Plaae-feengetrieben this type find locking = couplings to produce Yentenduags a Draiiraoroeiataaweg which lor the hydroklsaetisehen torque transmission wall dee umgehte Selene blocking clutches Video- usually within the Puiapengehäiaees _s arranged as another suitable
not siar Yerzufimg provides «Such a ßm.QV <ünumg ars © fagf
oino tanojrwünsehte Hensaattg der I £ öppl! jag _e because this ⁰ ©! ®
^{Link 1 to} the flow adrEsek d © Clipart Wandlers a.ö0gtonss@f

• 90S832 / 0801

18Q124S

is therefore extremely difficult to achieve a precisely coordinated successive engagement and disengagement of the Clutch. To remedy this disadvantage, a suitable servo device is arranged in the pump housing for such a coupling, then only a limited space is available for it. It also creates the lead the required fluid pressure to such servo devices construction problems, what in particular to the remote arrangement of the clutch in relation to the transmission and other devices of the transmission to generate a frictional torque.

According to the invention, the aforementioned disadvantages are now in one Gear avoided, which in the usual way and ¥ ice has a hydrokinetic torque converter and a Allows shifting into four gears, under which there is a tendon gear, without the need for a clutch to be arranged in the pump housing. So the invention is the The task is based on creating a multi-speed transmission that requires neither clutches nor brakes.

The solution to this problem emerges from the following description which, together with the claims, defines the scope of the disclosed and claimed inventive concept sets out.

909832/08 01

. _h _ 180124S

The invention is described with reference to an embodiment shown in the drawing. It shows!

Figures IA, 1 B and 1 C, longitudinal sections through a multi-speed transmission according to the invention,

Figure 2 shows the individual components in a schematic representation of the multi-speed transmission according to Figures 1 A, 1 B and 1 C in their mutual assignment to the explanatory * tion of the course of the torque path, and

FIG. 3 shows a table to explain the individual clutches and brakes that are engaged or disengaged Gears of the multi-speed transmission according to the invention.

In FIG. 1A, 10 denotes one end of the crankshaft of an internal combustion engine; this crankshaft is connected to an engine plate 12, the edge of which is connected to the pump housing Ik of a hydrokinetic torque converter 16 by means of bolts, which are not shown in detail. The converter 16 comprises a bladed turbine 18 with a hub grooved on a hollow shaft 20, the hollow shaft 20 extends axially through a stationary hollow shaft 22 of the stator. The hollow shaft 22 is connected to a wall Zk of the pump housing. This wall Zk is connected by means of bolts 26 to a wall 28, which is connected to a projection 30 of the transmission housing wall 32 with bolts (not designated in more detail). The walls 28 and Zk delimit a pump chamber in which the individual pump elements and a displacement

90 9 832/080Ί

pump 3k are arranged. This creates a pressure source for an automatic control valve system, not shown, which also optionally supplies a control pressure for the clutches and brakes of the multi-speed transmission.

The pump housing Ik comprises a front housing part 36 which is directly connected to a guide sleeve 38, which in turn is grooved on a central shaft k2 at kO , this shaft k2 extends through the hollow shaft 20 of the turbine.

The hollow shaft 22 of the stator has a grooved inner ring kk of an overrunning brake k6. This brake k6 comprises an outer track k8 _t which is provided with cams that create a cam effect with rollers 50. A dredged stator has a hub which is directly connected to the outer track k8 . The pump part, shown partially at 52, is firmly connected to a hollow shaft 5k which is mounted at 56 in a bore in the wall 28. The wall 2k carries a bearing sleeve 58 for a brake drum 60 with hub 62. The brake band 6k of a servo-operated brake for the intermediate gear rests on this drum 60; solve again.

The reference arrow 66 denotes a planetary gear in its entirety in FIG. 1B. This planetary gear

909832/0801

holds a front sun gear 68, a rear solenoid gear 70 and a ring gear 72 ". A first set of planet gears 7" meshes with the sun gear 70. Another set of planet gears J6 meshes with the sun gear 68 and the planet gears 7h » Di © Planet gears 76 are also in engagement with the ring gear 72. The planet gears 7% and 7 * 5 are on a common planet gear carrier 78 via shafts 82 and 80, respectively stored. The sun gear 70 is wedged at Bh with "? © r coupling sleeve 86, 'which is mounted on the We 11a% 2 ^ sadi on the coupling member 88", Bas coupling member 88 as inclined at its outer end coupling disks 92, which disks with lung 9 ^ - aussisrassa who have been betrayed by a Kapplut 96. 31 «Socket 86 is connected to umta Eoipplurags member α- · 'cider forms part of the same © ia · Bae;' _:: 1Λ "." SS is sä elssis "Z-jtlnaov 98 ausforaatj iniieriiaib chem ei; ·; Kctb & zs. ISO aagöordmet is. The cylinder f8 and the piston 130 form ssusaenaen" a pressure chamber ₉ which, however, is connected to an inflow of 10% with an inflow is "A return spring for the Xtapplimg is designated with 106, it is anchored on a spring arm 10 © and pushes piston 100 into the loose pitch of the clutch." veracliiebenda piston 100 engagement of the clutch by frictional connection between two disks 92 and! 9% «The axial toraiis for liquid pressure is intercepted by buckets of Bßvtvs" l®navimg- 110

909832/0801

180124S

the coupling carried by the coupling member 88. This coupling member 88 also carries further coupling disks 112 (FIG. 1 A), which interact with one or more clutch disks 114 carried by the brake drum 60.

Inside the cylinder formed by the brake drum 60 116 a piston 118 is arranged, which together with the cylinder 116 forms a pressure chamber. This pressure chamber stands In connection via an opening 120 with an inflow pressure channel 122 which is formed in the bearing sleeve 58.

The sun gear 68 is connected to the drum 60 via a member 124 for the possible transfer of torque. This link also serves as a bearing for the carrier 78. The carrier 78 is drivingly connected to the extension 126 of a brake drum 128. This brake drum 128 is surrounded by a brake band 130 which, for the optional anchoring of the drum, can be tightened and released by means of a servo device (not shown). The outer track of an overtaking brake carried by the drum 128 is designated by 131. This outer track is provided with cam surfaces and cooperates with rollers 132. An inner track is denoted by 13 ^, this inner track is fixed by means of bolts I36 against an end wall I38 of the gear housing 32. As shown, the inner track 13 ^ creates the bearing for a hub ikO of the drum 128.

9Ü9832 / 08Ü1

The ring gear 72 is connected to a torque transmitting drum 1 ^ 2, the other end of which is connected to a radially extending disk Ikk , which is carried by the output shaft ΛΗ6 . The shaft Ik6 extends through a bearing sleeve 1 ^ 3 which is carried by the end wall I38. A housing extension lk8 surrounding the shaft 1 * 12 is also fastened to the end wall 138 by means of bolts 15I. A brake wheel I50 for parking the vehicle is keyed on the output shaft 1k6. The teeth of this brake wheel I50 work together with a pawl, not shown, which anchors the wheel I50 with respect to the housing Ik8 . A regulator valve 152 for the fluid pressure is also drivingly connected to the output shaft 146. This regulator valve, to which fluid pressure is fed through a sleeve 15 * 1 provided with openings, modulates the pressure and generates a speed signal in a line 156 which is fed to an automatic control valve system for controlling the engagement and disengagement of the various clutches and brakes. A clutch for the overdrive gear and for the direct gear is arranged between the planetary gear 66 and the aforementioned overrunning brake. This coupling comprises a coupling member 158 which is directly connected to the carrier 78 by means of rivets or the like. This coupling member carries friction disks I60 which cooperate with friction disks I62 carried by a drum I6h. The drum I6 * l · is over a hub

2/0801 - 9 -

keyed on the shaft kZ. The drum "\ 6k" forms a cylinder 168, within which a piston 170 is arranged to form a pressure chamber, which fluid pressure is supplied via an inflow opening 172. A return spring for the piston 170 is designated by 17 * 1. This spring sits on one anchoring member 176 carried by the hub 166. When fluid pressure is introduced into the cylinder 168, the friction disks are frictionally engaged, thereby connecting the coupling member 158 to the drum 164. The reaction force is absorbed by a reaction ring 178 which is connected to the interior of the drum T6k is.

The various torque paths in the individual gears will now be described in more detail below with reference to FIG. For the purpose of a simplified description and illustration, the coupling members 112 and 114 according to FIG. 1 A are shown with C 3, the coupling members 92 and <? U according to FIG 1, the overtaking brake 132 in accordance with FIG. 1 B is denoted by C k and the brake band 6k in accordance with FIG. 1A is denoted by B 2. The table according to FIG. 3 shows the respective mode of operation of the individual clutches and brakes for the individual gears.

In order to bring about a slow gear, the brake band B 2 must be tightened. As a result, the planetary gear carrier of the planetary

909832/080 I.

transmission »anchored. The torque of torque converter 16 developed by the turbine is then output directly to sun gear 70 via shaft 86 and clutch C 2. The clutch C 2 is engaged in each of the forward gears with the exception of the overdrive. The ring gear is driven with a transmission ratio of 2 * ^ 0, while the reaction torque is absorbed by the brake B 2 and the overtaking brake C h. If an automatic upshift from the slow gear to the intermediate gear is desired, then the brake band B 2 can be released so that the entire reaction torque is absorbed by the overrunning brake C h Brake B 1, in order to anchor the front Somienradl 68. This causes an increase in the speed of the ring gear 72 compared to the turbine speed. >

The direct gear · is switched by simultaneously the clutches C 2 and C 1 are engaged while the brake B 1 is released. This creates a split torque path, part of which is hydrokinetic via the clutch C 2 and the other part via the engaged clutch C 1 is delivered to the carrier. The ring gear takes the torque each of these torque paths. Is such a divided one Path not desired, then clutch C 3 can be icy-steep

909832 / 080Ί - n -

180124S

to lock the planetary gear and between the input shaft and the output shaft a direct mechanical Establish drive connection.

Applying the brake B 1 shifts to overdrive. No further device is required for this circuit, which would have to be engaged or disengaged. A typical value for this overdrive is the value 0.667 · If the overdrive is switched to, the sun gear acts as a reaction member, and the torque is the planet carrier supplied by the machine.

By applying the brake B 2, the carrier is anchored and thereby switched to reverse gear. The brake B 2 allows an inverse torque delivery, the torque is output from the turbine to the sun gear 68 via the engaged clutch C 3.

The arrangement according to the invention of the overdrive clutch C 1 enables oil to be distributed via the regulator system, which is arranged at the right end of the shaft k2 . This regulator system comprises the sleeve 1 ^ 3 and a radial connecting channel 180, which is arranged in the area of the left end of the shaft.

909832 / OÖÜl

Claims (3)

Claim· 1. Multi-speed gearbox for vehicles, especially for motor vehicles, consisting of a hydrokinetic torque converter with the pump part as the input element and a downstream planetary gear consisting of a first and a wide sun gear and which are in engagement with this and are supported by a common planetary gear carrier · Planetary gears, of which the »wide planetary gears are in mesh with a ring gear as an output member, and a first clutch, which can be optionally engaged for three forward gears, between the turbine of the converter and the« wide sun gear and a ■ wide clutch for reverse gear «between the two sun gears , a first brake for the planetary gear carrier al · reaction member in slow gear and a «wide, optionally pullable brake for the first sun gear al · reaction member in an intermediate gear, characterized in that a third, optionally engageable clutch (O 1 - 160» 162) provided let * which in a Schn ell gear drivingly connects the drive shaft (10, k2) with the planetary gear carrier (78) of the planetary gearbox * * (66), and that the also la Zwlsohengang is operated, 909832/0801 2. Multi-speed transmission according to claim 1, characterized in that the third clutch (C 1) comprises a drum (164) directly connected to the drive shaft (1O, hz) and is arranged on one side with respect to the planetary gear carrier (78), while all further clutches are arranged on the other side of the carrier, and that within the clutch drum (164) there is arranged a piston (170) which cooperates with this and which, when pressure is applied, the friction disks (162) carried by the drum with the carrier (78, I58) brings worn friction disks (160) into frictional engagement. 3. Multi-speed transmission according to claim 2, characterized in that the clutch drum (164) is surrounded by a drum (i42) transmitting the torque, one end of which with the ring gear (72) is the planetary gear (66) and the other end with the output shaft ( 146) is connected, and that the brake (B 2) for the planet carrier (78) has a third clutch (C 1 - I60 / 162) and this drum (1 * 12) comprehensive brake drum (128), via which an im Langsangang sucked in brake band (130) is placed k, multi-speed gearbox naoh one of claims 1 to 3, characterized in that the outer track (131) of a safety brake (C k - 132) is connected to the planet carrier (78), the inner spar (13 * 0) of which is fixed and that the*· ORIGINAL INSPECTED 909832/0801 -ifc « . μ _ 180124S Overrunning brake (C 4 - 132) is arranged on one side of the third clutch (C 1 - 160/162) and the planetary gear (66) on the other side. 5 «Multi-speed gearbox according to one of claims 1 to k, characterized in that the clutch drum (164) is connected to the drive shaft (10) via a shaft (42) concentrically penetrating the planetary gear (66) and the converter (16). 909832/0801 Blank page