GB2153023A - Hydromechanical change-speed gearing - Google Patents

Hydromechanical change-speed gearing Download PDF

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Publication number
GB2153023A
GB2153023A GB08432282A GB8432282A GB2153023A GB 2153023 A GB2153023 A GB 2153023A GB 08432282 A GB08432282 A GB 08432282A GB 8432282 A GB8432282 A GB 8432282A GB 2153023 A GB2153023 A GB 2153023A
Authority
GB
United Kingdom
Prior art keywords
clutch
planetary gearing
gear
central gear
gear box
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
GB08432282A
Other versions
GB2153023B (en
GB8432282D0 (en
Inventor
Olgert Ivanovic Giruckji
Jurij Konst Jesenovskij-Laskov
Viktor Jefimovic Raskin
Jevgenij Michajlovic Skokov
Viktor Vladimirovic Belikov
Antonin Hau
Jiri Srubar
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ustav Pro Vyzkum Motorovych Vozidel
Original Assignee
Ustav Pro Vyzkum Motorovych Vozidel
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ustav Pro Vyzkum Motorovych Vozidel filed Critical Ustav Pro Vyzkum Motorovych Vozidel
Publication of GB8432282D0 publication Critical patent/GB8432282D0/en
Publication of GB2153023A publication Critical patent/GB2153023A/en
Application granted granted Critical
Publication of GB2153023B publication Critical patent/GB2153023B/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
    • F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion
    • F16H47/085—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion with at least two mechanical connections between the hydraulic device and the mechanical transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F16H2041/246—Details relating to one way clutch of the stator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H2045/005—Combinations of fluid gearings for conveying rotary motion with couplings or clutches comprising a clutch between fluid gearing and the mechanical gearing unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/48—Control of exclusively fluid gearing hydrodynamic
    • F16H61/50—Control of exclusively fluid gearing hydrodynamic controlled by changing the flow, force, or reaction of the liquid in the working circuit, while maintaining a completely filled working circuit
    • F16H61/58—Control of exclusively fluid gearing hydrodynamic controlled by changing the flow, force, or reaction of the liquid in the working circuit, while maintaining a completely filled working circuit by change of the mechanical connection of, or between, the runners
    • F16H61/60—Control of exclusively fluid gearing hydrodynamic controlled by changing the flow, force, or reaction of the liquid in the working circuit, while maintaining a completely filled working circuit by change of the mechanical connection of, or between, the runners exclusively by the use of freewheel clutches

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Thermally Insulated Containers For Foods (AREA)
  • Containers And Packaging Bodies Having A Special Means To Remove Contents (AREA)
  • Telephone Function (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

The first central gear 8 of reduction planetary gearing 10,11,8,9 is connectable in both senses of rotation by means of a first clutch 24 to the second central gear 17 of collecting planetary gearing 20,21,16,17,19 and by means of a second, lock-up clutch 30 to the inlet shaft of the gearing and then it is connected in one sense of rotation to a turbine wheel 3 of a torque converter by means of a free wheel 26; the second central gear 17 of the collecting planetary gearing is connectable in both senses of rotation to the inlet shaft 2 of the gearing by means of the first clutch 24 and the second clutch 30 arranged in series, thus allowing engine braking in all ratios. The reduction planetary gearing comprises suns 10,11 and double planets 8 mounted on a carrier braked at 9. Collecting planetary gearing comprises suns 20,21, intermediary planets 16,17 and a ring gear 18 braked at 19. In a second embodiment the torque converter is replaced by a fluid coupling. Figure 2 (not shown) shows detail of friction clutches 24,30. <IMAGE>

Description

SPECIFICATION Hydromechanical gear box The invention relates to a hydromechanical gear box for a transmission mechanism of a transport vehicle, especially of a passenger car.
With respect to a decrease of energetic losses, there are more advantageous hydromechanical gear boxes, in which a part of energy is transmitted by means of a hydrodynamic transmission, e.g. by a hydraulic torque converter or by a hydrodynamic clutch and a part in a mechanical way.
There is known a hydromechanical gear box, comprising a hydrodynamictransmission represented by a hydraulic torque converter, a reduction planetary transmission, consisting of a crown wheel, carriers, a central gear, locking coupling, reduction planetary gearing and a brake of the central gear, and a collecting planetary gearing, consisting of a carrier with two mutually meshing satellites, of the first central gear, of the second central gear connected to the carrier of the reduction planetary gearing, of a crown gear connected to the driven shaft and of brakes for connecting to the body ofthe first central gear and carrier.Then the gear box includes friction clutches for connecting driving shaft to the crown gear of the reduction planetary gearing and to the carrier of the collecting planetary gearing, and a free wheel for connecting the turbine wheel of the hydraulic torque converter to the crown gear of the reduction planetary gearing. This gear box secures a transmission of the output at the first and second gear stage by means of the hydraulic torque and at other stages in a mechanical wayt A drawback of this gear box resides in the fact that it makes not possible to brake by means of the engine at low gear stages - the first and the second - when it is mostly needed because of the free wheel under the turbine wheel of the hydraulic torque converter.
There is also known a hydromechanical gear box, comprising a hydraulic torque converter, the pump wheel of which is connected to the inlet shaft of the gear box, a turbine wheel, a reduction planetary gearing to the carrier which is double satellite, a brake connecting the carrier to the box of the gear box and two central gears and a collecting planetary gearing connected to the outlet shaft of the gear box by means of a carrier with two mutually meshing satellites, two central gears, one of which is connected to the second central gear of a reduction planetary gearing, a coupling for locking a collecting planetary gearing and a crown gear with a brake for connecting the crown gear to the box of the gear box.Besides that the gear box includes a friction clutch for connecting the turbine wheel of the hydraulic torque converter and the second central gear of the collecting planetary gearing to the driving shaft of the gear box. The turbine wheel is then connected by means of a friction clutch and the free wheel to the said second central gear of the collecting planetary gearing.
The advantage of this four-stage gear box' with respect to the previous one' resides in a possibility to enlarge the range of gearing at keeping four velocity stages at the same planetary gearing, to increase an efficiency and to decrease fuel consumption because of locking the hydraulic torque converter at two last gearing stages' and then in a possibility of a free wheel finish run of the vehicle at the first, third and fourth velocity stage.
But its drawback resides in the fact that it is impossible to lock the hydraulic torque converter at a shifted second gearing stage, and if the hydraulic torque converter is not locked, a free-wheel finish run of the vehicle cannot be utilized at the second gearing stage.
The above mentioned drawbacks may be obviated by the hydromechanical gear box according to the invention, the principle of which resides in the fact that it comprises friction clutches for connecting the first central gear of the reduction planetary gearing to the second central gear of the collecting planetary gearing and to the driving shaft of the gear box and a free wheel, connecting the turbine wheel of the hydraulic torque converter to the first central gear of the reduction planetary gearing.It is also advantageous to create the first friction clutch so that friction disks and a piston of the clutch for connecting the first central gear of the reduction planetary gearing to the second central gear of the collecting planetary gearing are situated between the body and the piston of the friction clutch, connecting the first central gear of the reduction planetary gearing to the driving shaft of the gear box.
It is also advantageous to create the gearbox in the way that the first central gear of the reduction planetary gearing is connectable in both senses of rotation, by means of the first clutch, to the second central gear of the collecting planetary gearing and, by means of the second clutch to the inlet shaft of the gear box, and then it is connected in one sense of rotation, by means of the free wheel, to the turbine wheel, the second central gear of the collecting planetary gearing is connectable in both senses of rotation, by means of the first clutch and the second one, arranged in series one behind the other, to the inlet shaft of the gear box, or in the way that the external ring of the free wheel is connected to the turbine wheel and the internal ring of the free wheel is fixly interconnected with the first central gear of the reduction planetary gearing, and with one common half of the first clutch and the second one; the second separate half of the first clutch is fixly interconnected to the central gear of the collecting planetary gearing and the second separate half of the second clutch is fixly interconnected with the inlet shaft of the gear box.
The advantage of the gear box according to the invention resides in the fact that the free wheel of the transmitting branch from the engine makes possible to increase the efficiency of the gearing and simultaneously it secures an effective braking by an engine at all velocity stages; always, if it is needed, it enables an idling run of the engine when transmitting the output through the hydraulic torque converter. The clutch for locking the hydraulic torque converter provides effects said as the first advantage of this embodiment.
The arrangement of the disks of the friction clutch makes possible on the first, third and fourth forward state to put in function both friction clutches, situated in the front part of the hydromechanical gear box by means of a single channel, through which a pressure operational liquid comes; both two remaining channels are connected to the discharge, and packing rings of these channels do not work under pressure, so that no wearing comes in question. The possibilities of the assembly are improved, dimensions are getting smaller, as well as the weight and moment of inertia of parts, loading the friction clutches and braking at changing a velocity gear.
In order that the invention may be clearly understood and readily carried into effect, a preferred embodiment thereof is, by way of example, hereinafter more fully described and illustrated in the accompanying drawings, in which: Figure 1 shows a schematic sketch of the hydromechanical gear box with a hydraulic torque converter; Figure 2 shows a design of friction clutches before the hydraulic torque converter, and Figure 3 shows a schematic sketch of the hydromechanical gear box and the hydrodynamic clutch.
As it is shown in Figure 1,the hydromechanical gear box consists of a hydraulic torque converter with a pump wheel 1, connected to the driving shaft 2 of the gearbox, of a turbine wheel 3 and of a reactor 4, connected by means of a free wheel 6 to the box 5 of the gear box. A reduction planetary gearing consists of a carrier 7 with a double-rim satellite 8, of a brake 9 for connecting the carrier to the body 5 of the gear box and of the first and second central gear 10 and 1 lithe first of which is located on the shaft 12 and the second is seated on the shaft 13.A collecting planetary gearing consists of a carrier 15 with two mutually meshing satellites 16 and 17; the carrier 15 connected to the outlet shaft 14 of the gear box, then of a crown gear 18 and of a brake 19 arranged on the said crown gear 18; the brake serves for its connecting to the box 5 of the gear box, further on it consists of a first central gear 20 and the second central gear 21, of a clutch 22 for locking this planetary gearing, connecting the carrier 15 to the first central gear 20 of the collecting planetary gearing. The first central gear 20 of the collecting planetary gearing is connected through the shaft 13 to the second central gear 11 of the reduction planetary gearing.The gear box is provided with a second clutch 23 for connecting the first central gear 10 of the reduction planetary gearing by means of the shaft 12 to the driving shaft 2 of the gear box, and with the first clutch 24 for connecting the central gear 10 by means of the shaft 12 and the shaft 25 to the second central gear 21 of the collecting planetary gearing. The turbine gear 3 is connected to the free wheel 26 to the shaft 12 of the first central gear 10 of the reduction planetary gearing.
The second clutch 23 consists of a body 27, connected to the inner ring 28 of the free wheel 26, of the piston 29, of a friction clutch plate 30 connected to the driving shaft 2, and of friction disks 31 and 32 connected to the body 27 of the friction clutch 23.
The first clutch 24 consists of a piston 33, seated in the body 27 of the second clutch 23, which is of a smaller diameter than diameter of the piston 29, of friction disks 34 connected to the body 27 of the second clutch 23 and friction clutch plates 35, connected to a hub 36, which is non-revolvingly seated on the shaft 25.
The friction disks 34 and 35 and the piston 33 are situated in a cavity 37 between the body 27 and the piston 29 of the second clutch 23. Through channels 38 the pressure liquid may come in the cavity 37, and through holes 39 from the channel 40 into a cavity 41, formed by the piston 33 and body 27. A channel 42 connects a cavity 43 and the hydraulic torque converter to a source of the pressure operational liquid.
The brakes 9 and 19 includes pistons 44,45 and 46, which form, between them and the body of the gear box, operational cavities 47,48 and 49, needed for their putting in function. The friction clutch 22 includes a piston 50, forming together with the body of the clutch an operational cavity 51.
The hydromechanical gear box works as follows: In the following table there is shown a sequence of switching of friction clutches and brakes and deliveries of the pressure operational liquid into operational cavities of the friction clutches and brakes, when shifting individual gearing stages.
shifted clutch or operation cavity n '::', "c,,,, 5 shifted a) velocity 8 > > , > , 5 X > > sz > Im > = Co Co Co Co a) stage 0 A, 0Co X 0Co w 0Co ~ o H - - + + + - - - - - + + + B + ~ H H - - + - - + + + - + - - + B + + ~ H H - - + + + - - + - + - - + B B + + H - - + + + + + - - - - - + B + + N - - + - - - - - - - - H H - - + - - - - + + - + + + B + + ~
where H means a utilization of the hydraulic torque converter or clutch B means blocking of the hydraulic torque converter or clutch + means that the clutch or brake are switched off or the operational cavity is connected to the outlet 1, 2, 3,4 means velocity stages N means neutral Z means back stage At the first velocity stage there is put in function the first clutch 24 and the brake 19. The working liquid is supplied, under pressure, into the cavity 41 and it shifts the piston 33 to the left, which presses friction disks 34 and 35, and in this way the closing of the clutch is ensured. As the cavity 37 is connected to the outlet, piston 29 is affected by pressure of the operational liquid in the cavity 41 and it presses it to the right.
The closing of the clutch 19 is achieved by supplying pressure liquid into the cavity 49. The output is transmitted from the inlet shaft 2 to the pump wheel 1 of the hydromechanical clutch and then from the turbine 3 through the free wheeel 26 and the closed second clutch 24 to the shaft 25, then to the second central gear 21 of the collecting planetary gearing and through the satellite 17, rolling on the crown gear 18, braked by means of the brake 19, to the carrier 15 and the outlet shaft 14. At releasing the gas pedal, the free wheel 21 makes possible an idle run of the vehicle and the engine runs at idle revolutions consumpting minimum of fuel. When increasing the fuel supply, the free wheel closes and the transmission of the pulling force is performed in the above mentioned way.The locking of the hydraulic torque converter at the first velocity stage is ensured by connecting the cavity 43 through the channel 42 to the waste, the piston 33 shifts, through closed friction disks 34 and 35, the piston 29 to the left and presses disks 30,31 and 32 to a friction connection. The output of the driving shaft 2 is transmitted onto the body 27 and through the closed first clutch 24 to the shaft 25 to the collecting planetary gearing. At the locked hydraulic torque converter there is possible to brake by means of the engine at the first gearing stage.
At the second gearing stage there is closed the brake 9 and the friction clutch 22. The pressure operational liquid is supplied to the cavity 48 and 51 and through pistons 44 and 45 it puts in function the brake 9 and puts in function the friction clutch 22 by means of the piston 50. The torque moment is transmitted from the driving shaft 2 to the pump wheel 1 of the hydraulic torque converter and from the turbine wheel 3 through the free wheel and shaft 12 to the first central gear 10 of the reduction planetary gearing. As the carrier 7 is braked by the brake 9, the planetary mechanism works as a simple reduction gearing, and the output is transmitted through a double-rim satellite 8 to the second central gear ii and through the closed clutch 22, locking the collecting planetary gearing, to the outlet shaft 14 of the gear box.The free wheel 26 makes possible an idle finish run of the vehicle even at a shifted second velocity stage. The locking of the hydraulic torque converter at the second velocity stage is performed by interconnecting the cavity 43 through the channel 42 to the outlet and supply of the pressure operational liquid into the cavity 37 through channels 38.
The piston 29 is going moved to the left and it closes the second clutch 23, connecting the inlet shaft 2 through the body 27 and inner ring 28 to the shaft 12.
If the hydraulic torque converter is locked, one may brake by means of the engine at the shifted second velocity stage.
At the third velocity stage there is closed the first clutch 24 and the brake 9. The operational pressure liquid is supplied into the cavity 41 and 48, the piston 33 puts into operation the first clutch and pistons 44 and 45 put into operation the brake 9. The torque is transmitted from the driving shaft to the pump wheel 1 of the hydraulic torque converter and from the turbine wheel 3 through the free wheel 26 through both branches, viz, to the first central gear 20 of the collecting planetary gearing through the reduction planetary gearing and to the second central gear 21 of the collecting planetary gearing through the first clutch and the shaft 25.
In the collecting planetary gearing both branches of the flow of the torque are connected and by means of the carrier 15 are transmitted to the outlet shaft 14 of the gear box. The locking of the hydraulic torque converter at the third velocity stage is achieved by closing the second clutch 23; the cavity 43 is now connected to the outlet and the piston 29 is shifted to the left by an action of the piston 33 - as at the first velocity stage. The free wheel 26 secures even at the third velocity stage an idle finish run of the vehicle; if the hydraulic torque converter is locked, one may brake by means of the engine.
At the fourth velocity stage there is closed the first clutch 24 and the friction clutch 22 by supplying the operational pressure liquid into the cavities 41 and 42 under the pistons 33 and 50. The torque is transmitted from the driving shaft 2 to the pump wheel 1 of the hydraulic torque converter and from the turbine wheel 3 through the free wheel 26, first clutch 24 and the hub 36 to the shaft 25. The friction clutch 22 locks the collecting planetary gearing and the output is transmitted from the shaft 25 to the outlet shaft 14 of the gear box. The locking of the hydraulic torque converter is carried out by closing the second clutch 23 as at the first and third velocity stage. Even at the fourth velocity stage an idle finish run is made possible and, if the hydraulic torque converter is locked, the braking by means of the engine as well.
At the neutral stage all clutches and brakes are disconnected, all operational cavities are connected to the outlet and the operational pressure liquid takes place only in the hydraulic torque converter and in the cavity 43.
If there is shifted a return velocity stage, both brakes 9 and 19 are in function. As the brake 19 transmits an increased torque at this velocity stage, the pushing force is provided by two pistons 46 and 45, on which the operational pressure liquid presses in the cavities 49 and 47, and the brake 9 is put in function by means of the piston 44.
At the return velocity stage the output from the inlet shaft 2 is transmitted to the pump wheel 1 of the hydraulic torque converter and from the turbine wheel 3 through the free wheel 26 and the inner ring 28 to the shaft 12 and then through the reduction planetary gearing, the carrier 7 of which is stopped by the brake 9, through the shaft 13 and collecting planetary gearing, the crown gear of which is stopped by the brake 19, to the carrier 15 and outlet shaft 14 of the gear box.
In case of need, the hydraulic torque converter may be locked at the return velocity stage by the second clutch 23, closed by the piston 29, which the operational pressure liquid affects in the cavity 37 and the cavity 43 of the hydraulic torque converter is connected to the outlet.
According to the second alternative, shown in Figure 3, a hydrodynamic clutch is applied in the hydromechanical gear box instead of the hydraulic torque converter. The function of the gearbox remains absolutely the same.
By means of the hydromechanical gear box according to the invention one gets four forwards velocity stages and one return velocity stage with a possibility of locking of the hydraulic torque converter and with a possibility of an idle finish run of the vehicle in all velocity stages.
The locking of the hydraulic torque converter increases the efficiency of the gearing and decreases fuel consumption. Besides that, the idle finish run of the vehicle at supplying less gas enables that the engine may work in idle running revolutions, what also improves the economy of the drive.
A design of the first clutch and the second one in the front part of the hydromechanical transmission enables in the first, third and fourth velocity stage to close the first and the second clutch 24 and 23 by means of one channel 40, connected to the source of the operational pressure liquid. This fact enables to decrease the wearing of packing rings in the channels, connecting the cavities 47 and 43 either to the outlet orto the source of the operational pressure liquid.
Although the invention is illustrated and described with reference to preferred embodiments thereof, it is to be expressly understood that it is in no way limited to the disclosure of such embodiments, but it is capable of numerous modifications within the scope of the appended claims.

Claims (5)

1. A hydromechanical gear box, including a hydrodynamic transmission, consisting of a pump wheel connected to a driving shaft, and of a turbine wheel, a reduction planetary gearing with a carrier and double satellite, with a brake for connecting a carrier to a box of the gear box and with the first and second central gear, and a collecting planetary gearing, connected to the outlet shaft of the gearbox by means of a carrier with two mutually meshing satellites, and with the first and second central gear, the first of which being connected to the second central gear of the reduction planetary gearing, to a friction clutch for locking the said planetary gearing and to a crown gear and brake for its connecting to the gear box body, comprising a first and second clutch for connecting the first central gear of a reduction planetary gearing to the second central gear of the collecting planetary gearing and to the driving shaft of the gear box, and a turbine wheel of the hydrodynamic transmission is connected by means of a free wheel to the first central gear of the reduction planetary gearing.
2. A hydrodynamical gear box as in claim 1, wherein friction disks and a piston of the clutch for connecting the first central gear of the reduction planetary gearing to the second central wheel of the collecting planetary gearing are situated between the body and piston of the friction clutch, connecting the first central gear of the reduction planetary gearing to the driving shaft of the gear box.
3. A hydromechanical gear box as in claim 1, wherein the first central gear of the reduction planetary gearing is connectable in both senses of rotation by means of the first clutch to the second central gear of the second clutch it is connectable to the inlet shaft of the gear box and then it is connected in one sense of rotation by means of a free wheel to the turbine wheel, the second central gear of the collecting planetary gearing is connectable in both senses of rotation by means of the first clutch and the second one, which are arranged in series 'one behind the other' to the inlet shaft of the gear box.
4. A hydromechanical gear box as in claim 1, wherein the outer ring of the free wheel is connected to the turbine wheel and the inner ring of the free wheel is fixly interconnected to the first central gear of the reduction planetary gearing and to one common half of the first clutch and the second clutch, the second separate half of the first clutch is fixly interconnected to the second central gear of the collecting planetary gearing, and the second separate half of the second clutch is fixly interconnected to the inlet shaft of the gear box.
5. A hydromechanical gear box substantially as herein described with reference to the accompanying drawings.
GB08432282A 1983-12-29 1984-12-20 Hydromechanical change-speed gearing Expired GB2153023B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CS8310166A CS238524B1 (en) 1983-12-29 1983-12-29 Hydromechanical gearbox

Publications (3)

Publication Number Publication Date
GB8432282D0 GB8432282D0 (en) 1985-01-30
GB2153023A true GB2153023A (en) 1985-08-14
GB2153023B GB2153023B (en) 1987-12-02

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ID=5448202

Family Applications (1)

Application Number Title Priority Date Filing Date
GB08432282A Expired GB2153023B (en) 1983-12-29 1984-12-20 Hydromechanical change-speed gearing

Country Status (6)

Country Link
JP (1) JPS60211163A (en)
CS (1) CS238524B1 (en)
DE (1) DE3446616A1 (en)
FR (1) FR2557658B1 (en)
GB (1) GB2153023B (en)
IT (1) IT1180250B (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2167818A (en) * 1984-10-17 1986-06-04 Fletcher Sutcliffe Wild Ltd Torque transmission arrangement and control system for same
US7703590B2 (en) 2006-05-01 2010-04-27 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Torque converter with turbine one-way clutch

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CS271027B1 (en) * 1988-05-18 1990-08-14 Antonin Ing Csc Hau Controllable epicyclic gear
JPH0932910A (en) * 1995-07-24 1997-02-07 Jatco Corp Structure for cooling automatic transmission
DE102006019782A1 (en) * 2006-04-28 2007-10-31 Daimlerchrysler Ag Hydrodynamically starting element for motor vehicle, has freewheel coupled with turbine wheel of transmission housing such that only one direction of rotation of turbine wheel is possible in relation to transmission housing
DE112007002624A5 (en) * 2006-11-29 2009-08-06 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Power transmission device
DE102008007017A1 (en) * 2007-02-27 2008-08-28 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Power transmission device for use in drive train of vehicle, has support arranged in axial direction at both sides of clutch device and carries out support elements supplied with pressure under formation of chamber

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2037383A (en) * 1978-12-06 1980-07-09 Ford Motor Co Automatic transmission mechanism
EP0037059A2 (en) * 1980-03-27 1981-10-07 Ford-Werke Aktiengesellschaft Three speed automatic transmission with split torque delivery paths in the two high speed ratios
GB2108220A (en) * 1981-09-15 1983-05-11 Ustav Pro Vyzkum Motorovych Vo Automatic planetary transmission gear

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2037383A (en) * 1978-12-06 1980-07-09 Ford Motor Co Automatic transmission mechanism
EP0037059A2 (en) * 1980-03-27 1981-10-07 Ford-Werke Aktiengesellschaft Three speed automatic transmission with split torque delivery paths in the two high speed ratios
GB2108220A (en) * 1981-09-15 1983-05-11 Ustav Pro Vyzkum Motorovych Vo Automatic planetary transmission gear

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2167818A (en) * 1984-10-17 1986-06-04 Fletcher Sutcliffe Wild Ltd Torque transmission arrangement and control system for same
US7703590B2 (en) 2006-05-01 2010-04-27 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Torque converter with turbine one-way clutch

Also Published As

Publication number Publication date
GB2153023B (en) 1987-12-02
IT1180250B (en) 1987-09-23
FR2557658A1 (en) 1985-07-05
DE3446616A1 (en) 1985-07-11
JPS60211163A (en) 1985-10-23
CS238524B1 (en) 1985-11-13
IT8424290A0 (en) 1984-12-28
FR2557658B1 (en) 1988-12-30
GB8432282D0 (en) 1985-01-30

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