DE1750536C - Automatic switching device for a hydrodynamic-mechanical compound transmission - Google Patents

Description

the circulating flow within the rotary drive and represents the output shaft of the torque converter by means of the dynamic pressure method represents the torque converter according to the invention to determine and the oil pressure, which is proportional to a motor vehicle, this shaft 3 with the Karzum Dynamic pressure is set, od to actuate the danwelle. The like. Connected and drives over the Diffejeweiligen Use clutches and brakes. 5 rential the road wheels, so that the shaft 3 for It should be noted that as the description of this embodiment increases as the gelrie torque ratio of the converter the flow plane wave 3 is designated.

speed increases accordingly, so that it The input shaft 2 is possible with a rotatable is provided, the gear shift point in the automatic housing 4, to the torque converter oil see gear changes by comparing the obtained io within it, and revolve To determine the dynamic pressure, or it is the oil pressure located within the rotatable housing 4 proportional to the back pressure, the speed of the to pump impeller 5. A number of guide vanes of The driving shaft or the driven shaft are suitable for use radially on the pump wheel 5 represents or proportional to the opening angle of the provided so that the torque converter oil the Throttle valve or for servo pressure. 15 Pump effect due to the centrifugal force of the rotating

In the figures, exemplary embodiments of the earth can produce the paddle wheel. The Middle finding explained in more detail. It shows this pump wheel is designed as a shaft and

Fig. 1 is a sectional view of an embodiment by means of a bearing through the outer housing 1 geIaeines hydrodynamic rotary device according to the invention, so that the stability of the rotation Aufrecnimomentwandlers, 20 is obtained, but this is at one end

F i g. 2 on an enlarged scale a sectional shaft with a gear oil pressure pump 6 directly view of the main part of Fig. 1, connected to the shaft. The oil pressure pump 6

3, 4 and 5 are schematic representations showing which oil pressure is generated as described below the oil pressure circuit of the configuration shown in FIG. 1 is set in a suitable manner and the respective guide form show * 5 league parts supplied and further in the Dren-

Fig. 6A, 6B, 6C, 6D and 6E are schematic representation torque converter from the shaft of the impeller G positions which introduced the main part of in Fig. Λ DAR. Furthermore, the returned oil will also show the set oil pressure circuit, used for the lubrication of the respective parts. Over

7 is a sectional view of a further embodiment of further oil ^{conduit paths, oil is used as the connecting oil guide of the invention, 30 pressure for the respective clutches and ß remscn}

F i g. 8 is a schematic representation of part of the gearbox supplied. When the speed of the oil pressure circuit of the embodiment according to FIG. 7 of the driven shaft is to be determined, oil and also assigned to the controller value on the same shaft

F i g. 9 is a schematic diagram that guides one. As far as the mentioned oil pressure paths are concerned, so These become part of the oil circuit of another embodiment 35 in connection with indicates. F i g. 3, 4 and 5 described in more detail.

The sectional view given in FIG. 1 shows the turbine wheel 7 with its blading

Overall arrangement of hydro- invention faces the impeller S and with the turbine dynamic torque converter for a Kraflfahr- gear shaft la connected. And the rotation of the turzeug. 40 binenrades7 is transmitted through the shaft la ,

The torque converter according to the method shown in FIG. 1 and a dynamic pressure receiving tube 8 in the form of a The provided Ausfühningsform is with an interchangeable Staudüsc is at one point between the blades Gearbox equipped with the three forward gearboxes of the turbine wheel, with the pressure stages and a reverse gear is shifted receiving opening to the impeller 5 so that the can. This is an example of a suitable angle of attack in the direction of the Slroweise Embodiment of the invention in order to obtain the rate of stimulation. The watering of the invention to facilitate, and it can reduce Di uckaufnahmerohr 8 is namely within of course, many other conventional designs in the flow path between the blades 7 of the Connection with the torque converter provided turbine wheel, and the oil will be at FuIJ, as follows from the following. 50 part of the dynamic pressure receiving tube 8 from the outside

In the following, the blades shown in FIG. derived and explained the wave la in presented embodiment. From the left of the center along the outer wall of the blade 7 by means of the right end of FIG. 1, an extension of the line pipe Sa extends. In the axial direction shafts in the same center line, which shaft direction of the turbine wheel shaft 7 "is a bore 8 through bearings at the respective points for rotation 55, the end of which has a transverse bore, within the housing 1 surrounding the shafts and with the oil pressure control device 14 connected, are stored. as indicated schematically, for what purpose a

The shaft 2 Leilungsweg8c shown in Fig. 1 at the left end serves the inside of the housing 1 is connected to the motor shaft, through which it and in the bearing attached to the housing Rotation is driven and which the proportion 60 is provided.

Drive shaft of the torque according to the invention The control system and the oil path to horderiing

converter forms. It is hereinafter referred to as the input of the pressure oil in the torque converter or to wave 2 designated. '' other parts, as described below,

The shaft 3 shown in Fig. 1 at the right end are within the oil pressure control device as well is almost the same speed as the inlet and 65 as the pressure setting valve for the intake and input shaft 2 driven, but the speed setting of the oil pumped by the pressure oil pump 6 the shaft 3 can be reduced and this last-provided, called shaft for rotation in any direction aage- between the impeller 5 of the torque-

I 750 536

converter and the turbine wheel 7 is a The shaft 3 of the third sun bevel gear 25 is the

Idler 12. The outer housing is a fixed shaft, the end shaft of this torque converter and the inside the shaft of the stator 12 is extended and drive or output shaft, with which a parking through a one-way clutch 12 a with the fixed shaft gear 31 is firmly connected, its arrangement and connected, so that the stator 12 can only be of a type known per se in the 5 mode of operation, can turn one direction. Via the bearing part so that when a vehicle is at a standstill, The same oil located in the torque converter is d. i.e. when it is parked by the hand lever returned to the outer oil container. The invention-actuatable connection with the gear 31 of the proper torque converter is the simplest side of the housing 1 is made from, so that of all known systems that cannot turn to the three-factor unity. level type belong. Of course, when idling or forward

A first pressure oil multi-plate clutch 15, downward travel or reverse travel is switched, the which by oil pressure engaged or disengaged connection canceled, so that the rotation of the disengagement can, is on the shaft 7 α of the turbine drive shaft3 is not regulated. Provided on the output gear 7, and a rotary drive is a 15 shaft 3, a regulator valve 32 is provided, which first bevel gear 17 from a shaft 16 is operated by the centrifugal force generated by the the pressure oil multi-plate clutch is communicated, or rotation of the output shaft 3 is generated. This it can be the sun bevel gear through the latter free- Regulator valve is designed so that the speed of the are given. A second pressure oil multi-disc shaft 3 is absorbed by the oil pressure, and The coupling 18 is also on the shaft 7 α of the door ao has the same structure as the conventional one Binenrades 7 is provided and can also provide the means, so that here is a more detailed explanation of the rotary drive on a second bevel gear 22 over left. Due to the achieved oil pressure, the switchgear Wave 21 transmitted or can release this, point indicated at which the automatic Gangje after it is engaged or changed by the oil pressure, which oil pressure for the disengaged wild. »5 mechanism of downshifting or upward

The outer circumference of the multi-plate clutch 18 shift commands are used. The foregoing is designed as a brake drum 19, the explanations relate to the structure of the execution shaft 21 is firmly connected or an extension form according to FIG. 1, the rest of the structure of which is a number the same represents. A first brake band 20 may have conventional features that emerge from the outside of the brake drum 19 easily give the overall structure by means of pressurized oil 30, tightened or loosened so that it is possible, the following is an explanation of the effect

the rotation of the second bevel gear 22 as the main part of the off-standstill shown in FIG to bring or this given free form of rotation for rotation.

give when the multi-plate clutch 18 is disconnected The torque converter from the three main parts,

is moving. With the first bevel gear 17 and 35 d. H. from the impeller 5, which by the Eindem second sun bevel gear 22 are first planetary gear shaft 2 is driven, your turbine wheel 8,

bevel gears 23, 23 'in engagement, the inclined arrangement of which faces the pump wheel, and from the guide

Nete transverse axes 26 and 26 'with a carrier housing wheel 12 is of the simplest design of the three-part

27 are connected. gate type, the mode of operation of which is

Second planetary bevel gears 24, 24 'have the transverse 40 can! is, so only a brief explanation is given

axes 26, 26 'as axes and are at the same time with will. The speed of the impeller 5 and the rotation Bevel gears 23, 23 'firmly connected so that the moment, i.e. the power, is on the side of the

Bevel gears 23 and 24 as well as the bevel gears 23 'and turbine wheel 7 continuously according to the load

24 'rotate together. moment changed on the starting page. If namely-

The second planetary bevel gears 24, 24 'are borrowed at 45, the load increases, the speed of the tur-

a third sun bevel gear 25 in engagement. The binenrades from and instead the torque to.

Carrier housing 27, which the axes 26, 26 'inclined so that the rotation when balanced with the load

holds and surrounds the bevel gears, torque is transmitted at the left end. The alternating gear "

through the shaft 21 of the second bevel gear and serves, as mentioned, the need for a higher « through the shaft 3 of the third sun bevel gear 25 to meet 50 torque. In the case of the i

stored The housing 27 therefore enables the planetary gear to be formed in the form of:

the first planetary bevel gears 23, 23 'and the second of a group of bevel gears, such as the first sun

Planetary bevel gears 24, 24 'around the oblique axes 26 bevel gear 17, the second Sonrenkegelrad 22, the first!

and 26 'can rotate and at the same time jointly planetary bevel gears 23, 23', the second planets

rotate with the housing 27. The outside of the 55 bevel gears 24, 24 ', the third sun bevel gear 25 around The carrier housing 27 is designed as a brake drum 28, the carrier housing 21 containing these bevel gears

det, held by a second brake band 29, the change gear, and the four links, d. H. di

or can be released, which de by pressure first clutch 15 for connecting or disconnecting

oil can be operated from the side of the housing 1, shaft 16 of the first bevel gear 17 and de

so that it is possible to rotate the carrier 60 shaft 7 α of the turbine wheel 7 by the oil pressure, di

housing 27 and the first and second planetary gears second clutch 18 for connecting or disconnecting

23, 23 ', 24 and 24' to allow or to a standstill to the shaft 21 of the second sun bevel gear 22 uo

bring. Since between the carrier housing 27 and that of the shaft 7 α by the oil pressure, the first brake

Housing 1 at the left end a one-way clutch 30 band 20 for connecting or disconnecting the mil di

is provided, the 'revolving of the carrier 65 shaft 21 united first brake drum 19 2

housing only take place in one direction, a single body from the outside through the öldrui

which is the same direction in which the one and the second brake band 29 for connecting od

Output shaft 2 rotates releasing the second brake drum 28 on the outside

¹ I 750 536

circumference of the carrier housing 27 from the outside by the oil pressure, mainly lead the mooring or release to shift the three forward gears and one reverse gear, their relationship to one another being as follows:

Scheme

Forward gears First stage ... Second step .. Third step ,,,

Reverse gear

First coupling

fixed fixed fixed loose

Second clutch

loose loose tight tight

First brake

loose tight loose loose

Second brake

tight loose loose tight

Because of the gear ratios, no further explanation is given here, but this has Planetary gears have the property of selecting the transmission ratio within a wide range determine when the various bevel gears are given a corresponding number of teeth, with It should be mentioned that the range of choice is further expanded if inclined transverse axes are provided for the planetary bevel gears.

With the structure described above, the oil pressure should automatically be set to the most suitable state for actuating the first clutch 15, the second clutch 18, the first brake band 20 and the second brake band 29 can be adjusted according to requirements. In other words, it are, as mentioned, if the operating oil pressure working on them is not suitable, the clutches and Brake bands actuated immediately without accompanying suitable slip if the oil pressure is too high, so that the shock becomes strong and driving becomes not only uncomfortable but also severe wear and tear and damage to the various Elements is the result. If the oil pressure is insufficient, the slip time will be too long and it will work not only is the purpose of the operation lost, but other disturbances arise, for example early wear of the clutch discs or brake bands.

In order to achieve smooth actuation in this case, only a suitable throttle valve is not required sufficient. The best way to achieve this goal is to use an appropriate oil pressure and throttle valve together.

FIG. 2 shows, on an enlarged scale, the torque converter which comprises the main part of the circuit shown in FIG forms illustrated embodiment, and the pressure receiving part g of the nozzle type is on one part of the turbine wheel 7 is provided, the flow rate of the circulating flow in the Direction shown by the arrow is determined by the value of the back pressure, however, is natural the direction of the flow velocity not within the surface including the WeQe, i.e. the direction of the arrow m in Fig.2. The relative Speed corresponds to the difference between the speeds of the two wheels, and the Guide vane forms an angle, and it is preferable to make the pressure receiving area 8 so much To give angle of attack. However, the relative speed is not constant, so that its angle of attack is difficult to determine. However, the circulating current tends to move longitudinally of the stator so that it is easy to achieve a nearly satisfactory angle of attack aim, and the oil pressure determined by the nozzle sets the oil pressure generated by the gear pump 6 to a constant pressure by constant pressure valve, so that pressurized oil is pumped into the torque converter, which pressure

ίο is the sum of three pressures, namely the internal pressure, the pressure which is generated by the centrifugal force as a result of the rotation of the turbine wheel, and the aforementioned dynamic pressure. Since the centrifugal force is switched off when the pressure oil closes the hole after 3

reaches the shaft Ta via the pipe 8a, the oil pressure is the sum of the dynamic pressure and the internal pressure. Of course, it is the same oil pressure as in the oil line 8 c, which is provided in the housing part.

ao Following the oil line path 8 c, the oil pressure acts on the main setting valve for the supply of Pressurized oil to the first clutch, the second clutch, the first brake band and the second brake band, which has the consequence that the oil pressure is proportional to

As this can be done, however, the explanations about the following operations in connection with Figs. 3, 4 and 5 which show in sequence the pressure oil paths in this embodiment.

First of all, the part shown in FIG. 3 will be explained. The oil pressure pump 6, which is driven at the same speed as the input shaft 2, sucks oil on the oil container 50 and conveys this to the main adjusting valve 35 via an oil line 41. Im

Main adjusting valve 35 reaches the pressure that is through. the sum of the internal pressure and the dynamic pressure which is formed by the nozzle on the turbine wheel? is determined within the torque converter, into the chamber 35 c with a slide Piston 3Sa of large diameter in the upper part of the main setting valve 35 via the oil line path 8 a, the bore 86 within the shaft 7 a and the öHeiiungsweg Sc and Bd. The aforementioned pressure and preload

a spring 35 / act on the slide piston 35 c of large diameter, so that the slide piston 35 b connected to this fesi is moved downwards from a small diameter. On the other hand, the oil pressure from the oil pump 6 in the chamber 35 d which faces the spool 35 b of a small diameter, so that the two pressures act against each other. The chamber 35 d is provided with an outlet opening 34, so that when the absorbed by the large slide piston 35 force becomes larger, the spool 35 b of small diameter in the Schließsirm the opening 34 functions, st that the internal pressure of the chamber 3SD are so far Incr karm that it comprises a pressure compensation leads induce When acting on the larger piston "

Force becomes weaker, the little piston puts it down Pressure of the chamber 35 rf by releasing de Auslaßöffmmg 34 down, whereby the pressure equalization brought about by wind. The pressure, which equals the Pressure is created by the constant pressure emstefl valve 40 is generated, is in the torque converter passed and a chamber 3Sr between the large piston 35a and the small piston 351 via the Ölicrhmgswcg 42, which pressure

209647/245

"*" ίο

acts on the other side of the large piston 35a, therefore occurs through the oil line 42 and through the so that the force with which the piston 35a presses down from the space between the shaft of the large diameter pump, almost nides 5 of the torque converter and the shaft des has no internal pressure and from the back pressure of the stator 12 through and is promoted in the torque circulating flow within the torque converter 5 converter. The purpose of the transmission of the and the spring pressure is compound. In special oil is a cavitation is verderen characterized, when the internal pressure prevent within the Chamber, that the internal pressure within the Drehmer 35 e and the internal pressure of the conversion of torque is the torque converter is increased and these are compared in a coupler, the internal pressure of the rotary cooler 49 is derived to prevent in a known torque converter always lower, but almost sta- io way an increase in the temperature of the internal oil bilized oil pressure, and if the diameter of the; However, in this embodiment, the connecting shaft of the two slide pistons is a further purpose of the invention, so that the entry of oil into the stagnation nozzle can be determined with little consideration of this fact. The oil should, it is possible to completely cancel the effect of the internal pressure entering the radiator 49 through the space of the torque converter. 15 between the stator shaft and the shaft of the tur-es can therefore be used as the pressure of the chamber 35 d of the bine wheel via the oil line path 40 c, and the main adjusting valve a high pressure from the pre-heat dissipating oil is tensioned by the oil line path of the spring 35 / and the dynamic pressure, which 49 c is diverted into the oil container 50 after it has lubricated the piston 35 a, which is proportionate to the cross-sectional ratio between the various parts of the gearbox 51, and the small piston 35 b.

increased back pressure achieved. Regarding the pressure oil pumped into the oil line path 42 from the adjusting valve 40 Hch of the preload of the spring 35 / it has the on for constant pressure it appears that the additional pressure is theoretically branched out oil line path 42 α and is applied to the regulator, however It is in fact, when the flow valve 32 via the main adjustment valve 35, the oil flow rate of the circulating flow is zero or conveyed by the line 42 b and the throttle point 42 c, is almost zero, it is preferable that the pressure be reduced is of conventional design is sufficient to provide the actuation for reasons of and on the output shaft 3 and to maintain the safety for which purpose the oil pressure so that a pressure proportional to the rotary spring 35 / serves. The oil pressure set on this number of the output shaft 3 by means of the centrifugal force generated by the latter for the respective clutches and brake bands 30 is obtained. Such a pressure is supplied through the oil line path 41b as shown in FIG. 5 can namely be obtained in that the shown, but takes its way via the in FIG. 4 Amount of oil is regulated, which switching device represented by the parts. It is to be brought into the chamber 32 a, 32 b and 32 c of the piston to exit gemer 40 c of the setting valve for constant pressure, the latter being introduced accordingly via the other oil line path 41a. The centrifugal force shifts the balance between the spring force and the oil that has emerged through the outlet opening 34.

is returned to the oil tank 50 via the lines 34 a der in the manner described above and 34 d . keep the speed of the output shaft 3 propor-The purpose of the adjusting valve 40 for constant tional oil pressure is in the switching part 14 of the after-pressure is to keep the oil pressure in the oil line 40 following described automatic change gear 41a always constant, although it is more or bes passed through the oil line 42 d. The less lower than the minimum oil pressure, which oil is passed to the oil container 50 via the oil passage through the main adjustment valve 35 can be achieved. processing paths 34 c, 34 d returned. After the above-In other words, the slider piston which continuous description of the pressure oil circuit by a piston 40a of large diameter and 43 FIG. 3 is below the portion shown in Fig. 4 b a piston part 40 described of small diameter up, of the in Fig. 3 shows which parts are connected to each other is as follows.

provided within. Against the back of the KoI- F i g. 4 essentially shows the part of the shift part 40a of large diameter, a device for shifting the gears of the interchangeable spring 40d acts, which is always geared against this piston part 50 by hand and automatically. If you support. Hand lever 55 is brought into the positions, which on the other hand, the pressure in the chamber 40 c is designated in succession with D, L, N, R, P , in the middle between the two spool pistons, the pressure parts supplied by the main setting valve 35 are opposite the piston part 40a, and oil via the oil line path 41b, which changes from the latter in the manner described below when the oil pressure overcomes the force of the spring 40d, the slide piston is pushed upwards, so branches or subdivides In order to selectively supply oil to the respective oil pressure is reduced by the fact that the oil-type clutches and brakes or the return piston part 40 b closes the oil line path 41 α, because of.

while in the opposite case the piston part The switching device 14 has a slide

40b is moved so that the oil line path 41a is free 60 piston 56, which is coupled to the hand lever, s <

is given to increase the oil pressure. On this, that he moves together with this, onei

Way, the oil pressure within the chamber 40 c automatically shifts slide piston 71 to itself

constant and balanced by the force of the spring switching the oil line paths through the sub

4Od regardless of the consumption of the oil in the differentiated between that through the nozzle 8

Direction of the outlet and the dynamic pressure taken by the change 65 and the pressure of the regulator

of the main valve held at the inlet. It is therefore ventils32 and a spool 66 for an attachment

Oil of constant pressure to the oil line path 42 in th of the oil line path from the automatic switch

the direction of the outlet promoted. The pressure oil the piston 71, only when the hand lever 55 i

ife

11 I 12

the position D is and to switch off the oil as springs 73 a, 73'α balls 73, 73 'in grooves 71 b conduction path when the hand lever 55 in and 71 c lock, and the shift is in other positions. happens quickly.

In the respective positions D, L, N, R and P with regard to the gradual shift or

of the lever 55 switched pressure oil circuits are like 5 movement will when the pressure in the chamber 70 follows; the back pressure to the right is much higher,

the piston 71 moves rapidly to the left while,

(1) When the lever 55 is in the position D when the pressure of the vehicle

"(automatic gear shift) is (Fig. 6A) wheel speed to the left strongly predominantly

ίο, the piston quickly · back to the right-

In the embodiment shown, the is guided. The position shown in the drawing second and the third forward gear automatically of the piston 71 is the position when the "pressure switches to. As shown in FIG. Lever is in position D , which increases with it in order to move it to the left. The following oil line 15 is coupled into the slide piston 56. This position, when the piston 71 is on the left, is the way The oil pressure of the oil line path 62 c is connected to the oil line switching device 14 via the oil line path 41 b supply path 61 d , since the part 71 f is guided by a large amount, which is divided into three paths 41 c, 41 d and 41 e diameter of the piston branches in the Freigabestelluüg 71st in the above-mentioned position is just the oil and is at the same time Ölleitungsweg 61c is locked at the part with conductive path 41 e with the Ölleitungsweg 62 through 20 to the large diameter, so that there is no piston 56, Währe nd the oil pipeline routes leakage can take place. The oil pressure from the oil 41 c and 41 d interrupted by the piston 56 line path 61 d therefore comes at 61 α over the oil. The pressure-receiving oil path 62 is also line path 61 on. He is then split for the first Bremsin three paths 62a, 62b and 62c. The oil band 20 passed on, as shown in Fig. 5, in the line path 62 b is actuated by the piston 56 at 25 of this, so that the brake drum 19 is prevented from exiting the return path 34c, during the wave of the second shown in Fig. 1 Sun the oil in the conduit 62 α, as shown in FIG. 5 bevel gear is held, whereby the condition shown in FIG. 1 and 5 shown first is created for shifting the second gear. Clutch 15 is promoted in order to operate this. On the other hand, through the part 71 e of large The oil passes through the conduit 62 c to the 30 diameter of the piston 71 of the oil conduit 65 b slide piston 66, which is closed by a spring 68 and 65 c opened, so that the pressure oil is held in the right position is, since a chamber 67 can escape and therefore the oil pressure within the in the right end position of the piston 66, the oil oil line paths 65, 65 a is reduced to zero, paths 63 c and 63 b with the oil exit path 34 c second clutch 18 is derived, binds. The piston 66 connects in this position 35 as will be described below, so that the condition required for not only the oil path 62 with 62 c, but also connects second gear is created. also the oil path 61 with 61 c and 61 d and the oil pressure is not moved along the oil line path 63 65 with 65 b and 65 c, so that the oil pressure in the divides and is diverted via 63 c, so that the oil pressure of the line path 62 r is reduced to zero on the middle part of the automatic oil line path 63 α. How switching piston 71 (Fig. 4) is transmitted. Shown in 40 in Fig. 5, the oil line path 63c is connected to the chamber 70 at the right end of the piston 71 second brake band 29, so that its effects, however, the pressure, which is composed of activity is released and therefore the circulation of the dynamic pressure the circulating flow of the rotary brake drum 28 around the carrier housing take place torque converter and from the internal pressure. can, whereby the required for second gear

On the other hand, acts in the chamber 70 a on the left 45 borrowed condition is created.

End of an oil pressure that corresponds to the flow rate If then the oil pressure in the chamber 70 is right;

is proportional, which is generated by the regulator valve 32 er of the piston 71, namely the back pressure of the nozzle. Furthermore, a spring is lowered in this chamber and the oil pressure of the vehicle wheel 72 is provided. The spring 72 exerts a compressive force on the left-hand side as a result of its pre-rotation speed in the chamber 72, which is greater than 50; the Ölleitungsweg 61 d to it exerts essentially a force of which the portion 71 / of the large diameter of the Schieberkol difference closed the pressure from the Fahrzeuggeschwin- bens7i and simultaneously 61c geöffne speed and the back pressure of the torque converter, so that the oil pressure within 61 α derivative corresponds to 55 being. This will make the oil pressure the first brake

When a vehicle is in normal driving, band 20 is reduced to zero and diverted, the pressure inside chamber 72 is higher. On the other hand, part 71 e is of large diameter so that slide piston 71 is displaced to the right and piston 71 is the outlet of oil from the oil, while if a sudden acceleration line path 65 c is closed, and at the same time we are made or if the vehicle is going uphill, the oil pressure from the oil line path 62 c over the ö! driving upwards or when the back pressure is added within the line path 65 c, whereby the second torque converter increases significantly, the clutch is actuated.

Pressure within the chamber 70 is overcome, so the oil pressure of the oil line path 62 a actuate

that the slide piston 71 is displaced to the left. regardless of the foregoing the first Kupj on the other hand, the piston when the back pressure 65 ment 15 from the start. At the same time, the ö is reduced to its normal value, the piston line path 61 α branched off from the oil line path 61 b returned to the right. This movement so that the first brake band 20 is released. However, the flow to the right and left occurs gradually as the oil emerges from the oil conduction path 63 a takes place

13 14

if, independently of the preceding, from Anband 20 and the second brake band 29 are tightened begin instead, so that the second brake band 29 are flat or loosened.

if it is released, whereby the third gear is in this position by means of the ice skating in FIG. 6C

Gearbox 51 is obtained. As mentioned, it is shown in which the oil line 62a for the first clutch, when the hand lever 55 is in the position D 5 position 15 and the oil line 64a for the second clutch, the second gear and the third gear is automatic Piston slide 56 are switched off, switched automatically. - While the oil line 62 a with the outlet line 34 e

is connected and the oil line 64 b with the outlet

(2) When the hand lever 55 is connected in the L line 34d position, so that the first clutch (first forward gear [see FIG. 6B]) and the second clutch 18 are not under oil pressure

stand and are therefore disengaged. The oil pressure off

The first clutch 15 and the second brake band of the oil line 41 c is, however, assigned to the second brake 29 are assigned to the gearbox 51, while band 29 is connected so that it is tightened.
the second clutch 18 and the first brake band 20 On the other hand, the first brake band 20 does not stand

need to be resolved. As a result of this condition, 15 is under oil pressure and is released, since the automatically scarf through the piston 56, as shown in Fig. 6B, the tend piston valve 71 from the piston valve 66 is also connected to the oil line path 41 b from the main adjustment valve 35 and the oil line 61 b with the outlet of the oil line paths 41 c and 41 β connected, selection line 34 / is connected, whereby the oil line path 41 d is switched off for the empty end. The oil run required condition is obtained
pressure from the oil line 41 c is therefore to the second 20

Brake band 29 via the oil lines 63, 64 a (4) when the hand lever 55 is in the reverse direction, which pulls it, and at the same time the gear position R (see FIG. 6D) is located

into chamber 67 on the right side of the piston

66 promoted so that it counteracts the force of the second clutch 18 and the second brake

Spring 68 is moved to the left and the oil lines a.5 band 29 of the gearbox 51 are actuated, and the first clutch 15 and the first brake band 20 are completely separated from the automatically switching piston 71, so that no connection to the are released. In the 01-sem shown in Fig. 6D, there is. The discharge from the oil line 63 b is circular, the oil line 41 d is also switched off for the oil pressure, so that the pressure oil cannot leak or leak out of the oil line 64 via the piston valve 56. 3 ° den, and the oil line 41 c is with the oil line 43

On the other hand, the pressure oil from the oil line is connected, and at the same time the oil line 64 b of 41 e, which is connected to the oil line 62, from which the outlet line 34 d is switched off and the oil line oil line 62 a to the first clutch 15 is promoted, where 63 & shut off from the outlet line 34 c, so that it is actuated by this. The oil pressure of the oil line and the oil pressure of the oil line 64 with the second coupling 62 is therefore connected in this case by the piston 66 through the line 64 a and the oil is switched off so that it does not flow to the piston 71 of the oil line 63 to the second brake band 29 is changed. On the other hand, the derivation from the oil via the line 63 α is promoted, so that both line 62 b to the oil line 34 e by the piston 56 are actuated.

switched off so that there is no leakage or leakage. In this case, the oil pressure of the oil line is

he follows. 40 63 c communicated, the piston slide 66 to the left

The oil pressure from the piston valve 71 is moved through the and are switched off with the automatically switching piston valve 66, so that the oil pressure piston valve 71 connected oil lines from the piston valve 71 does not switch into the oil line 61 α.

and with the outlet oil line 34 / from the oil- There is therefore no oil pressure to the oil line 61 α,

Line 61 b is connected and therefore the oil pressure is reduced to 45, which is connected to the first brake band 20, so that the second clutch is, however, the oil line 61 b with the outlet line 18 is in the disengaged state. 34 / connected so that no oil pressure is effective

The oil pressure from the oil line 41 d is released by the and the first brake band 20.
The piston valve 56 is switched off, and the oil lines. The oil line 41 e is through the piston valve 56

64, 64 a do not take up any oil pressure. At the same time 50 switched off, so that no oil pressure in the oil line 62 is, since the oil line is effective with the outlet oil line 34 d, which leads to the first clutch 15, the oil pressure is reduced to zero, so and at the same time the oil line 62 b is with the outlet that the first brake band 20 is connected in the released state line 34 e , whereby the oil pressure is located. first clutch reduced to zero and their

Therefore, if the hand lever is switched off in the position 55 connection.
lung L is the one required for first gear

Condition, namely the condition in which the (5) When the hand lever 55 is in the position P the first clutch and the second brake are actuated, (parking) (see Fig. 6E)

while the second clutch and the first brake

are resolved. 60 As for the torque converter, there is

already many systems through which the connection

(3) When the hand lever 55 is in position N between the input shaft and the output shaft in (l-cerlauf) (see Fig. 6C), this position can be separated, and the same

in good time when setting the hand lever to the

This condition can be established if 65 ment P with respect to the parking gear on the Abuie first clutch 15 and the second clutch 18 drive shaft takes place a mechanical clutch or disengaged against actuation. On this locking, and a notch or a Paßkör-Wetsc, it does not matter whether the first brake is effective, whereby the parking gear is locked.

15 16

is tensioned. In this embodiment, if such a requirement exists only if an operator Part of it is affected, the same system is applied and the sooner it is released det, however, as in connection with FIG. 1 get closer the better. The bypass oil line has the explains the parking gear 31 from the outside by means of a task that the oil pressure quickly also from the notch or a fitting body clamped. The 5 step can be derived from the fact that the in this case existing pressure oil circuit is in ball 77 a of the check valve from the branch-Fig. 6E shown. .The oil pressure from main setting line 77 is removed.

valve 35 ago is completely switched off by the piston valve 56. The same applies in the case of the second brake band and does not gain access to it. 29, and it must, for example, when the hand lever on the other hand, the inner oil lines 62, 64, 61, io 55 are quickly returned from position D to position L -63, which is brought with the first clutch 15, the second, the force of the actuation process and clutch 18, the first brake band 20 or with the actuation time, which is why a second brake band 29 are connected, with the throttle valve 80 between the oil lines 63 a and corresponding outlet lines 34 e, 34 d, 34 / and 63c whose structure is connected to that of the throttle 34 c, so that its oil pressure is completely equal to zero »5 valves 75, so that one is reduced here. The individual couplings and a detailed description are not required.
Brake bands are therefore completely switched off) or it is now the oil circuit for the first clutch release, whereby the conditions for parking ment 15 are described. The first clutch 15 is taken into account. all forward gear positions, ie both in the

The above explanations relate to position L as well as actuated in position D , except for

on the parts shown in Fig. 4 of the present recorded during the time of startup or when on

Execution form, and then the is switched to the N position, in which cases the

F i g. 5 shown part of the mentioned embodiment actuation or release is not carried out, so that

explained in more detail. the requirement regarding the actuation time does not

F i g. 5 primarily concerns the various as is strict, which is why a certain throttle 62'c

Clutches and brake bands and shows the oil circuit between the oil line 62 c and the first clutch

run with the control devices for the loading 15 is provided. As for the internal structure of the first

activity or releasing the clutches and clutch 15 and their mode of operation are concerned

Brake bands. the details of which are exactly the same as in the case

The 30 of the conventional multi-plate oil pressure clutch, which is supplied from the oil line 61 α in FIG.

Pressurized oil passes through a throttle valve 75 and conditions, so that no further explanation is given

takes its way to the cylinder chamber 20c for the will.

first brake band 20 from the oil line 61c, and when the actuation of the second clutch 18 is komdas Oil is supplied to the cylinder chamber 20 c, so plicated than that of the first clutch, so that it looks up this if the shifting of the second gear 35 is intended following a detailed explanation and further, when the hand lever 55. will give.

from position D of the automatic gearshift When the second clutch 18 is actuated, so

is switched downwards. there can be two cases, depending on the

In other cases, which are explained below hand lever 55 in position R or in position, the same applies, and if there is oil for actuation 40 position D for shifting third gear,
the brake or the clutch with respect to its When from the position N to the position R switched partner is fed, the connecting part is switched and the speed of the motor is low, so a fairly high torque or a fairly low one Torque is effective, strong counteraction can be done simultaneously with the actuation, the actuation easily, however, there is one advised so that the means for the actuation are very important 45 case in which the reversing quickly out of the. As mentioned, when the actuation position N is initiated so that the oil pressure coming from the oil is carried out under a high pressure, the oil pressure line 64a is throttled by the throttle, a strong shock during the establishment of the connection 64'a is throttled to counter this, and it is preferable that the operating oil level oppose and the second clutch 18 pressure when the actuation is performed so 50 is supplied.

is greatly reduced that it can then be adapted to the torque when the hand lever 55 is actuated for the third time. Therefore, gear is shifted from second gear to position D even in this case, which is shifted from the oil line 61 α represents, and when the actuation is carried out, 55 clutch 18 are made so that the Besoll are provided for a suitable period of time, that is, actuation takes place and, as mentioned, the return a suitable slip time. If the torque of the oil pressure is high with respect to the release of the first, the slip should take place quickly over the bypass line for a long time brake band 29, while if the torque is carried out low with the oil supply to the second, the slip should only take place during a short time, clutch 18 is set so that a sufficient time is to be found in order to obtain a satisfactory result.

Therefore, in the present embodiment, the actuating force of the remaining torque of the pressure oil supplied to the first clutch IS is diverted into the portion of the first clutch 15 of the total torque transmitted via the oil line 62 e via the throttle valve 75 65, the splitting is diverted and introduced into the chamber 75 a. This is not always divided equally into two parts. The needle valves 76, 76a are then actuated in order to oppose the distribution ratio through the transmission oil line 61 o a resistance. the ratio of the planetary gears is determined. For example

π ^f is

the distribution ratio can be less than two five- The nozzle 8 is opposite to the pump

tel, and as far as the coupling area, the wäh- wheel 5 for recording the flow velocity

rend the time the position R is required, imme- diately from the mentioned direction in the same way as

is utilized, it is preferable that that in the above-described embodiment

the second clutch 18 supplied oil pressure low 5 directed. The flow velocity from the

is made riger than the direction opposite to the first clutch IS can namely be determined here

supplied oil pressure. Be from this point of view. The circulating flow in such a direction

is a pressure reducing valve 85 between the branch line is generated when the speed of the turbine

tung62d of the oil line 62 a and the oil line 65 6, rades7 higher than the speed of the pump wheel 5

which leads to the second clutch 18 is provided, io is what occurs during braking by the engine,

in order to reduce the oil pressure so that this is the case when a vehicle moves through its inertia

imagined apportionment ratio can be obtained. moves that is the case. This can be done during normal

The throttle valve 86 to set the slip time drive happen, however, if a sudden

Braking is carried out in the pressure reducing valve or the vehicle in the aforementioned manner

85 provided. 15 goes downhill. Because the torque from behind

When driving forward, the oil line 62 c, which can always be determined by the fact that the flow

is supplied both in the L position and in speed in such special cases.

the position D, branched off after 62 d , and the oil is caught, the determined torque is applied to the

pressure is applied from the chamber 85 6 to adjust the main adjustment valve, and it

Oil pressure recorded as well as from the chamber 85 a ao is not only possible to reduce the connecting force in

for the throttle valve this mechanism. Another way of maintaining it, but i & i too

on the other hand, if the oil pressure is possible via the oil line 65 a, the downshift according to the

When upshifting is supplied, the oil in taking the torque from the rear in the event of a

Intermediate chamber of piston valve 88, 886 on, sudden braking when driving at high speed

and since the oil pressure of the oil line 89 with the Kam- as swhidigkdt to be carried out automatically, so that the

mer88c on the back of the part can be used preferentially by larger engine braking.

Diameter of the slide valve 88 is connected, in the present embodiment this is also

This oil pressure acts against the oil pressure of the chamber if combined.

85 b on the back of the part of smaller diameter. An explanation will be given below of the in diameter of the piston valve 88. The oil pressure of the oil 30 F i g. 8 given the scheme shown, which the line 89 must in opposite proportion of the area α main part of the pressure oil circuit of the embodiment on the right and left of the piston valve 88 shows in comparison. In the embodiment according to FIG. 8, the pressure from the stagnation nozzle 8 on the side of the turbine can be reduced to the oil pressure in the oil line 62 d , since the line 65 a is regulated by opening or rades7 on the outer oil line 8 c via the Boh closing the same so that the Aus 35 tion 8 b of the shaft and the conduit pipe 8 a can be achieved with this cross-sectional ratio, while the pressure from the pitot tube 9 can be applied to the. the side of the pump wheel 5 on the oil line 9 b over

Therefore, if the aspect ratio on the right of the conduit pipe 9 can be obtained, λ becomes which

and to the left of the piston valve set in advance two pressures on the chambers 10 a and 10 & right

is, the setting is transferred to the actuating oil pressure upstream and downstream of the switching valve 10,

taken, which is required for the second clutch 18 inside the switching valve 10 is a slide piston

is borrowed. When supplying the oil pressure of the oil line 81 10 c provided either to the right or after

to the second clutch 18 regulate the throttle valves 86, left by the difference in the pressures in the chamber

86 a the resistance, and since the details here 10 a, 10 b are shifted.

of exactly the same as in the case of the throttle valve 45 when the vehicle is in normal driving

75, no explanation is required. the side of the impeller 5, the driving side and

The foregoing is the crux of the we- the side of the turbine wheel the driven side, so The manner of the pressure oil circuit and the structure of the embodiment that no back pressure is absorbed by the nozzle 9 according to Fig. 1, which pressure oil circuits will men. In and of itself, on the inside, there are no flies Another for fluid torque converter 50 force and internal pressure is available, but the With change gears of other systems applied pressure caused by the centrifugal force can be almost increased be able. lifted when it reaches the outside, so that the

With the basic structural concept of the execution internal pressure alone in the left chamber 10 ft of the approximate shape according to FIG. 1, the switching valve 10 shown in FIG. 7 can be present. On the other hand, the process to which the 55 of the right chamber 10 a the stagnation nozzle 8 is directed for the following explanation takes place. At the Ausbinenrad 7 the dynamic pressure on, wherein the opposite guide form according to FIG. 7, the pressure set pressure is overcome to such an extent that the orifice 9 of the back-up nozzle type on the pump wheel 5 is moved in front of the slide piston 10c to the left. In this case, and the pressure determined is the shaft of this case, the oil pressure on the side of the back pressure pump wheel by means of a pipe 9 a pulls 60 with the oil lines 8 "c and Sd leads through the opening, and the oil pressure that passes through the Oil line 96 is connected to the branch 8'c, and is supplied in the same way within the housing, is sr loading manner as in the above-described measuring that the guide shape received by the nozzle 9, the oil pressure is removed from the main set pressure from the torque converter are fed to valve 35. The oil lines and their Aufgakann. The pressure receiving opening 9 of the stagnation nozzle is 63 ben are exactly the same as in the preceding directly directed to the turbine wheel 7, and the embodiment described, so that here the flow velocity of the circulating flow from one to single detailed explanation is superfluous.
Turbine wheel is recorded as the back pressure. If, on the other hand, the engine brake is activated,

19 20

The turbine wheel 7 is the driving side and the control valve 35, which is set to a suitable pressure in the pump wheel, the driven side so that the back pressure is set to the back pressure, ie to the pressure of the circulating flow through the back pressure nozzle 9 oil pressure via the oil line 41c, which is taken in FIG. It is therefore drawn by the chamber and 4 with dashed lines, effective 10 b of the piston valve 10 added. What 5 sam. On the other hand, on the other hand, the oil pressure in the chamber 10a acts on the left chamber 70α on which the cam element 74c, which corresponds to the right side, so the oil pressure of the flow opening of the throttle valve or the acceleration nozzle 8 is low and there is no pressure is actuated by centrifugal organ, ie generated by the connecting force, so that only the internal pressure is the only active rod 74 b to the accelerator pedal 74 a for regulating the sam, the oil pressure of which is lower than the oil pressure of the xo speed of the engine, via the spring 72 which is to left ventricle 106. The slide piston 10c will have the effect that the slide piston 71 is shifted to the right, therefore to the right, and the pressure of the jam can be moved. Therefore, when there is "a nozzle 9 is from the branch line 9 c of the oil line vehicle is in normal driving, the pressure of the 8" c is supplied. The ge in the manner described. Spring 72 is set in such a way that the automatically switching oil pressure is also moved to the right on the main adjustment valve spool 71, whereby it acts on valve 35, whereupon the same work precedes in parallel to overcoming the moving pressure as in the case of the above-described output right ventricle increases and decreases. In this guide, the setting of the oil pressure at the trap acts on the oil pressure of the oil line 62c, ie the main setting valve 35, so that the oil circuit of this part is as follows. The oil pressure, the correct oil pressure, which is required for the respective clutches ao oil line 62c takes its way via the oil lines and Bremsbä'ider, generated and pulls 65 b, 65, 65 a to the second clutch 18, which can be a leads. is moved, and then when the nozzle

It can therefore be shown in FIG. 4 and 5 increases, as a result of the add-on forms directly for this embodiment, the flow velocity within the would be used satisfactorily. The mode of operation of the torque converter, for example in a mountain of the second embodiment, differs in that, when driving up or under sudden acceleration, as mentioned, the engine brake works well when the pressure in the right chamber 70 of the sudden braking increases when driving at high Ge - Slide valve 71 abnormally, and if the pressure speed is made by the fact that the pressure is brought into position D with the lever 55 in the position D and the spring 72 coupled to the acceleration element, the circulating flow is in the opposite direction the spring 73 a displaces the loaded ball 73, increases and that the flow nozzle 9 absorbs the increased flow through which the slide piston moves rapidly to the left and also the flow in FIG. 4 becomes.

showed, automatically shifting spool 71 according to this is the so-called determination of the downward left is shifted to the downshift through- 35 switching point at which the oil line 6Sb, to feed. the second clutch leads, on part 71 e of great

The following is the one shown in FIG. 9, the third diameter of the slide piston 71 is switched off Embodiment described. is and at the same time the oil line 65 c for discharge

In the case of the in FIG. 4 shown embodiment of the oil pressure is released and therefore the switching point in the switching part of the automatic 40 binding of the second clutch 18 is released. On the change gear from the dynamic pressure of the rotating part, the flow is switched off at the other part 71 / of the slide piston or the oil line 61c, which is connected to the outlet oil line to carry out the oil pressure and the wheel speed, from the proportional 71, and at the same time the oil line is switched off automatic gear change can be obtained, while oil pressure from the oil line 62 c from the oil line 61 d rend in the third embodiment 45 shown in FIG is supplied, whereby dynamic pressure of the circulating flow or from which this is actuated, with the result that the first oil pressure proportional to this and from the öff- brake drum 19 can be retained, whereby the accelerator's voltage level can be obtained, the second gear obtained will. However, if the Beum is to carry out the automatic gear change. 50 acceleration of a vehicle is significantly reduced The oil circuit within the switching device 14 'or when the torque is reduced in the vicinity of the hand lever 55 is in position D at the end of a road gradient, the same as in the previously described dynamic pressure of the nozzle is also reduced Reduced, so embodiments for position D, and the second that the oil pressure of the right chamber 70 of the piston gear as well as the third gear are automatically reduced by the slide 71 so that the pressure of the switches. right spring 72 becomes larger again and the slide

■ The oil pressure from the Haupteinstellventil is moved to the right over berkolben 71, whereby the supplied oil passage 41b, however, the oil line oil circuit to the condition of the third speed to-41 e to the oil line 62, and the oil pressure is fed back. The vehicle therefore moves when the first clutch 15 is in third gear via the oil line 62a 60.

supplied, whereby the first clutch is actuated. These work processes take place at the same

The oil pressure in oil line 62c takes its way hold-up instead when at high speed to the middle part of the automatically switching slide 71 is suddenly braked and the spring pressure on the on the piston side of the accelerator member located in the open position and reduced slide 66. Ö5 at the same time the back pressure of the nozzle 9 in the direction

Therefore, in the right chamber 70 of the automatic device of the engine brake is increased. The reverse switching piston valve 71 of the back pressure is going on in the same way, so that this the nozzle or the oil pressure from the main inlet no explanation is given.

21 22

In the following, the fourth embodiment is carried out or accelerated

purifies. Vehicle moving on an incline, the speed of the

In this embodiment, the slightly from the in engine to, while the back pressure within the Fi g. 4 and 10 (not shown schematically) receive the torque converter increases more, and if the th can be, the determination of the downward pressure in the right chamber 70 of the piston valve downward shift point and the upward shift point 71 is higher than in the left chamber 70 a The slide piston 71 is shifted to the left, as well as the switching of the same with an automatic - shifting the gear shifting when the manual- a downshift, ie the second gear, can be raised to 55 in the position D in relation to the traffic jam, and when the vehicle pressure of the circulating flow moves normally again within the rotary io, the slide piston 71 torque converter or to the torque converter proportional to it is returned to the right, in order to increase the pressure and the speed of the engine to third gear. For example, switch. If instead of the speed of the engine, the right chamber 70 of the in FIG. 4 dargestell- a servo pressure or a this proportional pressure th automatically switching slide 71 as shown on the left chamber 70 a of the piston valve 71 is maintained, but the speed of the engine 15 is effective through a suitable method, oil pressure can be proportional to the gate left chamber 70s the transmission and the gear change of the shift provided in order to take up the oil pressure in this. point to be carried out, which arrangement The method for generating an oil pressure, which is proportional to the speed of the engine and its mode of operation, which is not described in detail here, can be easy.

be obtained in that the regulator valve on ao The points at which the nozzle pressure-wave part is used, the same speed measurement openings on the impeller and on the turbine as the engine has, as shown in FIG. Therefore, the wheel of the torque converter will be provided a vehicle on a slippery road is near the front ends, however away, the third gear is given, so that the through the Druckaufnahmeöffnvingen do not have to dei The oil pressure caused by the speed of the engine must be greater than one of the »5 points indicated above is placed as the back pressure within the rotary The mentioned places can even between the dei torque converter, however, increases if sudden vanes of the stator are provided.

For this purpose 3 sheets of drawings

Claims (3)

1 2 It is already known to measure the flow claims: speed in a hydrodynamic torque converter the dynamic pressure by means of 1. Automatic switching device for a hy- Htotrohren to measure that in the stator in certain Drodynamic-mechanical compound transmission, arranged at 5 distances from each other and their a hydrodynamic torque converter opening angle can be selected in a certain way, and a multi-stage gear change transmission so that the differential pressure has a linear hunlction of the whose gears are by means of one of a servo oil output torque of the converter. The pump generated servo pressure by the actuating order of the pitot tubes at a point where gen or by loosening the couplings and io the angle of inflow in the working fluid Brakes are switchable, whereby the servo pressure changes, is unfavorable. · by means of a sensor element in the transducer. The invention achieves that the betäligten proportional regulating valve pirn drives gears connected soft and shock-en ^released. Converter output torque is controllable because the oil pressure can also be used to determine the characterized in that a pitot 15 downshift point and the upshift point pipe (8) for the purpose of receiving the dynamic of the automatic transmission .
According to an advantageous development of the invention, the pressure circulates in the torque converter The working fluid wedge between the blades of the is used for actuation by the controlled servo oil pressure Pump wheel (5) or the turbine wheel (7) of a gear change valve, which the gear change torque converter is arranged. ao time determined so that the one for the clutches 2. Switching device according to claim 1, characterized and brakes specific oil pressure supplied or marked, that the controlled servo oil pressure can be locked in order to shift into automatic gear To effect actuation of a gear change valve (71) change. For this characteristic only serves, which determines the gear change time in connection with the main claim Schulz true, so that he desires for the clutches or »5 Braking certain oil pressure supplied or reduced can be locked to the automatic gear measurement of the dynamic pressure in both stream changes to effect. directions in the converter fluid in opposite directions 3. Switching device according to claim 1 or 2, in the direction of the first pitot tube, a second pitot tube characterized in that it is provided for the purpose of measuring the 30. The advantages mentioned can therefore be dynamic Pressure in both directions of flow for forward travel as well as for backward movement the converter fluid can travel downwards in the opposite direction. a second pitot tube (9) in addition to the first pitot tube (8) is. lay the previously described design. The medium for transferring work performance of the pump wheel on the turbine wheel of the hydrodynamic torque converter is carried out by The invention relates to an automatic formed by the liquid enclosed in the transducer. Switching device for a hydrodynamic compound If a large torque is transmitted, a transmission with a hydrodynamic torque 40 has a strong circulating flow. The rotary converter and a multi-stage gear alternating torque ratio of the converter increases with the increasing gear, the gears of which increase by means of a servo pressure generated by a servo the speed difference between the two gears Brakes can be switched by the flow speed of the circulating flow, the servo pressure being proportional to the regulator actuated on the converter output by a sensor element in the converter by means of a 45. torque transmitted to the shaft can be viewed proportional to the torque converter output speed,
moment is controllable. It is therefore possible that the converter output As a result, such a switching device is closed with the torque transmitted to the French output shaft see patent specification 1502 459 known. The sensor 50 determine that the flow rate of the member in the converter consists of the Haltecinrich- circulation flow is determined. A possibility tion of the stator, whose reaction force is recorded to determine the flow velocity of the is used and to control the hydraulic pressure circulating flow is to use a dam is, pressure filler, e.g. a nozzle or pitot tube in the The invention is based on the object of arranging a run of the converter output shaft. In this case, switching device of the type specified at the beginning is so that the liquid in the pitot tube is influenced by the fact that despite the lowest possible centrifugal force, which in turn counteracts the circulating flow wall, the servo pressure counteracts the theoretically best value. A correct measurement is approximated in advance, that is, that with as many rotating as possible, the measuring fluid and working fluid have an exact proportion of the same centrifugal force under numerical ratios of the transducer,
tionality between converter output torque and it is also generally a certain one Servo pressure should be present. External pressure to the torque converter The posed problem is solved by dividing a in order to increase the internal pressure 711, and this Pitol tube for the purpose of recording the dynamic pressure is of course determined in the same way in the kcs of the Ar- 65 measuring tube circulating in the torque converter. However, since it is a solid liquid The pressure applied between the blades of the pump can easily be kompenracles or the turbine wheel of the torque. It is therefore a very functional and Converter is arranged. simple method, the flow rate