DE3016381A1 - Active gyroscope converter for vehicles - uses gyroscope mounting in compact housing for use as torque converter in vehicle systems - Google Patents

Abstract

The active gyroscope for the steering of vehicles and ships is designed to provide torque conversion and inertial braking. The gyroscope body is mounted on bearings on one axis and has gears that couple with a transverse axis. The main axis of rotation (AA) provides a support for the gyroscope units and a bevel gear coupling connecting with a disc. The disc is supported on bearings from the main shaft. The complete transverse assembly is supported at one end on bearings. The volume and the mass of the gyroscope is made as large as possible in relation to the converter volume.

Description

Active media-free rudder

Additional patent application for P 29 01 612 .4.

Inventor and applicant: Christian Strobel The one described below The invention relates to an addition to the main application of the same name, namely a active media-free rudder, based on the inertial travel principle, whereby the in the Main registration defined gyro torque rectifier forms the starting point, The additional invention aims in part, also known from the previous notifications Way on the gyroscopic torque converter based on such rudders for Drives of all types with falling speed characteristics, especially for vehicle drives, e.g. Road vehicles, rail vehicles and propellers.

The gyro-torque inertial braking also occurs in a manner that is also known in some cases benefit as a spontaneous effect of the application.

In particular and in contrast to the gyro torque converters shown earlier, In which the rotor impeller is built into an epicyclic drive for the torque conversion and inertial braking delivers and reversing still remained problematic here the new @ re design of the rudder is substituted for the circulatory drive, in which without reversing the input direction of rotation, only the direction of rotation for reversing the effective torque direction of rotation is reversed, and this effect by alternately rolling the bevel gears (8) on non-rotatable axially guided tapered friction flanges (6) or (12) with a only a very small alternating stroke (sj) of the flanges (24) and (25) can be arranged and e.g. in the state of Fig. 1, where a gap is open at both (32) and (33), idling at gyro speed = zero is feasible even with simple controls, without the input shaft being brought to a standstill.

In application to drives of all types, according to Fig.1. The invention that in a known manner the useful decoupling axis of the rectified gyroscopic torque ML as N-N is at the same time the input and output axis of the converter, namely the longitudinal axis of the To N-N rotating output housing (18,27) and at the same time the same directional axis E-E is that also centered rudder housing foot (17) on the housing cover firmly screwed or made in one piece with it, e.g. cast and together with (18,28) output shaft is that also acting on the spider shaft input gear (21) the cup wheel (30s30a, 30b) with bearing (29) on the for centering (17) centered antipodal rudder housing foot (17a) and thereby (18,27,28,30a) on N-N are aligned because the pot wheel (30,30a) with bearing (31) is also rotatable about N-N is, the wheel (22) on the spider shaft (4) with bearing (23) rotatable in the opposite direction to (21) is supported around A-A and idler gear, that also bevel gears in a known manner (8), whose rotation around E-E frictionally depends on their rolling on the friction flanges (6,12) of the thrust cylinder (13) is derived, firmly coupled disks (10) with cup-shaped Friction linings (11) operate around E-E and this with a high gear ratio via friction wheels (1a) drive the gyroscope (1) to B-3 rotating, that also to reverse the Useful torque and to produce one at zero gyro speed under continuous Input shaft occurring idle state of the thrust cylinder under axial Guide in pin (14,15) with forces P1 and P2 with the thrust pin (26,34) of the Schubflansohen (24,25) is moved coaxially to the rudder housing in the case of relatively small ones Strokes (si) so that the switching pin (34,26) with the ball housing (18) in its holes they are guided to rotate around N-N, and that aids are arranged based on them it from a fixed base (35) by strokes (s +) in directions P1 and P2 for positioning the direction of rotation or idling can also be moved by rotating (18) by N-N are, the secondary gyroscopic moments of the system Mnl and Mn2 spontaneously in full are used as frictive couplers and do not act as a free moment on the system, namely by the rotation of the components (1,2,3,10,11,8) around E-E in connection with rotation around A-A occurring inner gyroscopic moment Mn1, which around perpendicular to A-A and the axis lying to N-N acts, the gyro drive wheels (81) act on the friction surfaces (6) or (12) presses, and that from the rotation of the gyroscope (1) around B-B in connection with rotation around E-E occurring gyro torque Mn2 as to the To N-N and to B-B perpendicular Aohse rotating the gyro drive wheels (1a) to the cup-shaped friction wheel body (11 press @ with these secondary moments Mn1 and Mn2 $ the same The origin and technology, like that, have the roller printing on the grist and the grinding table supplying pan mill moment of a pan mill.

In the figures of the drawing, this inartial rudder converter is in Not to scale structure and its function shown in schemes Fig. 1 shows a partial longitudinal section of the transducer.

Fig.2. Shows the reversing adjustment mechanism, acting on one Adjusting pin (34). Pin (26) is disengaged.

Fig. 3 shows it under instantaneous action on pin (26).

Pin (34) is disengaged.

Fig. 4 shows the adjustable pot with roller bearings instead of sliding.

FIG. 5 shows how one can also use the input side instead of the output side can sohieben forth the adjusting sleeve over the converter if the provision of a fixed base (35) that requires, e.g. in Fig. 6.

Fig. 6 shows the disintegrated application of 2 transducers as components of two wheel rims of a rear or front axle on the motor vehicle, for forward and reverse rotation and inertial braking without reverse gear hold.

Fig. 7. shows its integrated application, using it as a duplex unit take the place of the differential gear since then, which you can see in Fig. 6. as in Fig. 7. superfluous.

Fig. 8 shows the diagram of the converter circuit for degressive useful torque according to Fig. 10.

Fig. 9 shows it for progressive useful torque according to Fig. 11 * Fig. 10 shows Converter characteristics of the degressive type from Fig. 8.

Fig.11. shows converter characteristics of the progressive type according to Fig. 9.

In detail, the construction and modes of operation are as follows: Fig.1.

Three of the well-known design with an offset of 120 degrees around the shaft (4) The gyro base gears (3) that have been plugged in and have been thrown around A-A are carried in forks One for each B-B to be driven from a fixed drive cone roller (1a), a loose wheel cone roller (2) and the gyro body (1). The bases are given for the purpose of torque rectification when rotating around A-A by rolling your teeth on the fixed gear rim of shield (19) @Rotation around rectifier axis E-E. It has the same speed as (4). The teeth of (3) are denoted by (3a). The drive of (1,1a) is provided by radia Conical friction wheels 8, welohe in the rotary cage (5) rotatable around E-E with bearings 9 supported disks (10) and their friction pots from Jurid (11) drive around E-E, and on their conical friction surface roll under centrifugal pressure around A-A and the secondary torque pressure of the gyroscope from Mn2 rubbing the wheels (1a) including (1) around B-B. The translation is very large what is desired.

This MachSrt allows that with a wave moving in the same direction (4) and (30a) the direction of rotation around B-B and thus also the direction of rotation of the useful torque becomes selectable from ML to N-N.

The rotary cage bearing shield (5a) is on the rudder shield with bearing (7) (19) supported rotatably around A-A. The hub of the cage (5) is keyed to the shaft (4) and is driven to A-A.

With; Bearing (16) is (4) in the rudder housing (17) and with bearing (20) in the Gelläusearlagerschild (19) rotatably supported around A-A, the shaft (4) is fixed at the front wedges the toothed or friction bevel gear (21) and at the back the one with bearing (23) around A-A in the opposite direction to (4) rotatably supported idler wheel (22). Acts on both wheels at (21) driving and at (22) supporting the tooth or friction cup bevel gear (30b, 30) below high gear ratio and at a relatively low speed around N-N. Its shaft (30a) is Input shaft and supported with bearing (31) rotatable around N-N in the output housing (18). At the same time (30) is centered with bearing (29) and rotatable around N-N on the rudder housing base (17a) based. Antipodal to this centering of the housing (17) on Aohse N-N the rudder housing (17) is centered with a centering attachment on the output housing base (27), which is screwed up with (18). So that the decoupling axis N-N of the rudder (17) is bilateral to the drive shaft (28) or to the input shaft (30a) is fluted, with frequent (28) is omitted and the housing (18, 27) becomes the output shaft, as is known.

With pin (14), which is fixed in the Sohubflansoh (24) and in the Sohubylinder (13) seated, this cylinder is guided aohsially in the rudder blade (19). With tenons (15), which sit firmly in the other thrust flange (25), is drum (13) on the other Side also guided axially in the rudder housing (17).

With thrust pins (26,34), which run guided in the converter housing (1s), the flanges (25,24) can be used with forces Pl or P2 and with them via pins (15,14) the drum (13i axially back or forth and its friction linings (6) or (12) won cone sail.

ment-like design alternatively apply pressure to the bevel gears (8) so that they are driven, in one or the other sense of rotation around E-E.

If - as in Fig. 1. is shown at the moment, -both at (32) just as there is a gap in (33), then the gyro prevails at zero speed E-E idle, whereby (30,30a, 30b, 4) can continue to run in the same direction of rotation. if if you keep moving from one direction of rotation to the other, then you step inside Braking torque at (18,27,28) as "inertial braking", the hub (ski) of the flansohen (24,25) or the drum (13) only needs to be 10-15 mm, as does that of the pin (26.34). This makes the control easy, The structure of the transducer is shown inappropriately. In practice this is the volume and mass of the top (1) selected as large as possible relative to the transducer volume and weight. Because on large rotor diameter, rotor mass and rotor speed are important here.

Fig 2.

The picture shows the converter of Fig. 1 reduced. From the output side (28) an adjusting pot (36) made of sheet metal with a front bead is pushed over, whereby the bead has the task of each one of the adjusting pins (34) or (26) of Fig and slide it to N-N when the output shaft housing (18) rotates leave on the inner circumference of the Sioke. Here is currently the one from Fig. 1. known force Pa while holding down the pin (34) and thus in Fig. 1 with the flange (24) or Pin (14) the thrust cylinder in direction P2 with its Jurid ring (6) against the Press the bevel gear (8).

Behind the bead is the other pin (26) in the extended state visible, which means that the gap (33) in Fig. 1 has a width zero and the gap (32) has its maximum width.

The actuating force F2 is supported against a solid base, which is symbolic and is denoted by (35). It could e.g.

be the holder of a compressed air cylinder or hydraulic cylinder similar to e.g. the overall sketch Fig. 6. a vehicle rear axle. On the rifle (36) there is a small torque resulting from the friction of the tip of (34) on the bead around N-N in the sense of rotation from (18,28).

Fig. 3.

The same picture as in Fig.2. shows here the sleeve (36) with pulling force F @, which is supported by the base (35), shifted to the right by one stroke (s2) so that pin (34) is disengaged and pin (26) is pressed in by the bead, and with the force P1 of Fig. 1. This means that in Fig.1.

at gap (32) width zero and the gap (33) its maximum width has, i.e. cattle (8) roll on the friction ring (12), which, compared to Fig. 2. the Direction of rotation of gyroscopes (1) and that the useful torque was reversed to N-N. (S2) can be about 50 mm, compared to (s1) of Fig.1. that is only 10-15 mm.

Fig44.

To the sliding friction of the pin (26,34) on the bead of (36) and on (36) transmitted moments to reduce N-N, the Sioken profile is here on the Inside of a roller bearing race (37) laid, which with Büohse (36), in which the outer bearing ring (38) is stuck and is taken along in directions F1 or F2 so that on - (36) hardly a moment around N-N acts.

Fig.b.

While in Fig.2. to 4. the thrust pot (36) from the output side (28) is pushed over the converter (18), it can be here from the input (30a) be postponed if that is the provision of a solid base (35) for support of the forces F1 or F2, as e.g. in Fig. 6, where none on the outside of the rim solid basis would be expected.

Fig. 6.

The integrated one is driven by two such converters and view braked vehicle rear axle system in top view; disintegrated, because in contrast to the integrated of Fig.7. each of the two rims separately one Converter (18) is flanged on the inside so that without an output shaft (28) the Revolving housing (18,27) wheel drive is, the cardan shaft (42) drives in the bevel gear (41) a single crown wheel around N-N, which runs in the same direction via shafts (30a / 1 and 3oa / r) as converter drive shafts drives the two units by N-N. From the inside as with Fig. 5. the pins (26,34) will run forward with 2 push sleeves (36/1 and 36 / r) the rims or controlled to reverse, the latter without using a gear reverse gear and only by means of two valves or push buttons or a pedal reverse switch brings from the forward run at the same time the - even if only with the direction of rotation of the cardan - Inertial braking known from previous registrations, with a reversal of the cardan shaft rotation here not applicable. The switching forces are supplied by a pneumatic or hydraulic double cylinder (39/1 or 39 / r) as F1, F2 and supports them as a solid base in its middle armature (35), which is screwed to a carrier or bracket of the vehicle.

Fig. 7.

Here is the back or Front axle shown integrated: the two Converters (1J / l, 18 / r are rotatably supported around N-N in a housing (43) and from the bevel gear (41) takes place in the same direction with waves (30a / 1.30a / r) the input to both converters. The same positions (28 / l, 98 / r) provide the output sensible but independently of each other on the rims, which then also have an additional Can contain friction brake; although they also here as in Fig. 6. inertial can be braked. The integrated unit is mounted in the middle where previously deer The same drive as the two disintegrated in Fig. 6. will be superfluous.

Fig. 8.

The transducer housing outline (18) is shown and includes in phantom a gyro axis B-B when the state is currently parallel to A-A, when ML = o, furthermore a rectifier axis E-E and the epicyclic drive shaft (4) with bevel gear (21), which in this converter not only revolves around A-A but also around N-N with (18). Furthermore is the switch pin (34) that is currently disengaged and the one that is currently pressed in Sohaltzapfen (26) indicated. Forces P1, F1 act on the latter on a solid basis at. Input (30) experiences input torque Me and angular velocity + # @ on the known Sketched pot bevel gear above translation. The gyro base rotates around the shaft (4) with + ## including (5, 19) gyro (1) and drive wheel (8) from Fig. 1. To E-E as a rectifier axis rotates with + # 3 the gyro base (3) including components (l, la, 2) and instantaneously rotates around E.E as with Rig.1.

also bevel gear (8) including cup wheel ((lo, ll) with + +. Also rotates Gyro (1,1a,) around own axis B-B. The converter housing (18,27) rotates with the shaft (28) as output with + # 6 6 around N-N.

The + signs of the scalars Ml and angular velocities # 1 to E @ indicate the direction of rotation compared to the switching state vsn Fig. 9. It is considered from the converter types of degressive characteristics in this switching state as known, that and why with increasing output rotation + # @ the rotations + # 2 to + # 4 decrease, like Fig.10. shows. It is related to the fact that wave (4) is increasingly related and -mim the same angular velocity + # 6 with housing (18) rotates around N-N; because this If the rotation is in the same direction as that of (30), the speed of (21) decreases.

This switching state is therefore addressed as a degressive; because with increasing + # 1 the abtrie @@@ omentumsum (+ ML + Me) decreases, similar to that with converters, di. not yet on this simple: rt were reversible, out Advance registrations became known. The condition Fig.8. defined when the pin is pressed in (28) and Ausger @ cktem (34) that bevel gear (8) with force P1 and secondary torque + Mn1 the conical friction flange (12) of (13) is pressed on. By definition, this arises at (8) + # 4, at (1) + # 5 at + # 1 + # 2 + # 3 and consequently + ML as a synonym for + Me Moment.

Fig. 9.

In the same way of representation as in Fig. 8, but with extended Pin (26) and indented (34), is defined here and readable that from positive Values + # 1, + # 2, + # 3 by pressing (8) with force P2 and secondary torque -Mn1 Also insert the friction flange (6) from (13) by turning the direction of rotation from (8) to - # 4 - # 5 arises and with parameters remaining positive + # @, + # 2, + # 3 and + Me negative Result -Ml and - # 6 occur at the output. This is because of the constant + # 3 and + # 2 and turned - # 5 the output torque converts to -ML and additionally in addition because of the occurring together with (18) and counter-rotating to the rotation of (30b) Rotation of (4) by N-N the amount + # 2 increasing with the sign remaining the same There is a tendency so that -with unchanged direction of rotation of +21 and torque + Me am Input-at output the negative difference (-ML + Me) is present as a moment, whereby the scalar of Me becomes smaller and smaller than that of ML. # 6 only becomes whole when it starts up short positive Fig. 10.

This link @ page of the moment diagram shows the switching status of the Fig. 8. assigned by the aggressive type. With three different + # 1 stationaries # 11 <# 12 <# 13 and an assigned curve of + Me at the input are then the three torque characteristics (+ Me + ML) as Kru @@ e between three fixed points of the Me lines and the ordnate stretched, namely in the positive range of + # 1 and of + (Me + ML), namely right. As with systems of advance registration, the output torques take place with increasing output speed.

ln fig. 8. and 10. the scalar + ML is never smaller than rapid drive moment scalar No, which is assigned to the # 1 in question.

i "i.11.

This right-hand side of the characteristic curve is the state of the Fig. 9. assigned and has progressive moment curve, which is based on Sejienbehavior tends to change the output direction of rotation when the characteristic curves pass through the ordinate wondens.

To the left of it is a small positive area of + # b based on the fact that at startup + Me gets a larger scalar than -ML for a short time. Only from one certain initial gyro speed - # 5 becomes -ML + Me = 0 and that is what the three interpret passes marked as dots through the negative ordinate line, where assigned at to three different input rotations like, # 12, # 13 @ie passage points at # 6 = 0 show the balance.

On the right the square characteristic curve is characteristic and leaves high Output torques to; this circuit of Fig.9. is not only suitable for the known Inertial braking from the full range without reversing the input direction of rotation, but also for forward drive; especially when the torque ratio is below spontaneous adaptation of the output torques to the load is expected. If you have the system Fig. 9. e.g. drives with a three-phase asynchronous motor with or without slip rings, so with (18,28) [-Ml + M @] and - # 6 fits down to very low output speed values and at very high moments of the load without the motor tilting or burning out because the speed gives way beforehand. This flexibility occurs at almost constant Drive speed, which in increasing phase their energy up to the performance limit of the motor by increasing the current consumed.

In this respect, a squirrel cage drive can also be used on all networks with such a converter work at higher levels than those permitted since then.

In the case of vehicle drives, the accelerator pedal can also be slid under Choosing +1 to widen the control range, with more throttle a higher torque and higher Driving speed there, and the engine does not stall if you drive less often switches on inclines.

ßoi apply to vehicle drive according to Fig. 6. and 7. makes sense, that taking into account that in the circuit according to Fig. 9 and 11.

The mean value of the scalar of - is only about 50% of that of + # 1, to achieve high torques and high speeds -ML or -6 either behind the drive motor or behind the gearbox a translation stage is built to Increase the speed of the cardan shaft (42). Alternatively, there is the possibility , in Fig. 6. and 7. the number of teeth on the input bevel gear (41) is much larger than that of the wheel (43). The control range of the moment at the wheels (49 / l, 49 / r) or. the rims (40 / 1.40 / r) and also the control range of the vehicle speed can be made even wider with the accelerator without having to hold the gangso, so that gears can sometimes be dispensed with; even more so than with this propulsion circuit then without gear shift by: fluidic switching according to Fig. 8 and 10, backward travel is adjustable without turning the direction of rotation of the cardan shaft.

Literature (5. Strobel P 29 ol 612.4 "Active media-free Trägruder" Main application, gyro torque rectifier.

P P 29 o5 952.7 Ditto. Additional registration re.

Gyro rudder torque converter, degressive type.

"p P 29 46 239.3 Ditto. Additional registration re.

Rudder with a new type of reversing by switching the frictional one Gyro drive without reversing the input shaft.

"P 30 13 543.4 Ditto. Another innovation on the rudder hit pneumatic circuit Blank page

Claims (2)

Additional patent claims to P 29 ol 612.4 1. Active media-free support rudder, according to the claims of the identical main application, where SP 3%! I 'newer Type without reversing the input direction of rotation and with a continuous input shaft that Reversing the rudder torque ML by N-N by reversing W5 of the gyroscope (1) around B-B and the torque conversion by installing this reversible Rudder is arranged in a known manner in an orbital drive, naoh the Figures of the additional drawing characterized in that d a ß according to Figure 1. the drawing in a known manner the useful torque decoupling axis N-N of the rectified gyroscopic torque ML is at the same time the input and output axis of the converter, namely the longitudinal axis of the N-N rotating output housing (18,27) and at the same time aush at a gyro The rectifier axis E-E is centered on the rudder housing foot of (17) Housing cover (27) firmly screwed or manufactured in one piece with it, e.g. 13. Poured is and together with (18,28) output shaft that further on the spider shaft input gear (21) the cup wheel (30,30a, 30b) with bearing (29) acts on the centering centered by (17) antipodal rudder housing foot (17a) and thereby (18,27,28,3oa) Because the pot wheel (30,30a) with bearing (31) can also be rotated around N-N, aligned to N-N is aligned to N-N, the wheel (22) on the spider shaft (4) with bearing (23) in opposite directions to (21) is supported rotatably around A-A and idler gear is that also known in Wise bevel gears (8), the rotation of which around E-E frictionally depends on their rolling on the friction flange (6,12) of the Sohubzylinders (13) is derived, firmly coupled disks (io) with pot-shaped friction linings (11) operate around E-E and this over at high gear Friction wheels (1a) drive the gyroscope (1) to B-B rotating, that also for reversing of the useful torque ML and for producing one at zero gyro speed under continuous Input'-wave occurring idling state of the So-stroke cylinder (13) Yet Claim 1. under axial guidance in pins (14,15) with forces P1 or P2 and with the thrust pins (26,34) of the thrust flanges (24,25) coaxial to the rudder housing is moved with relatively small strokes (s1), so that the switching pins (34,26) together with the output shaft housing (18) guided in its holes rotate around N-N, and that Aids are arranged, by means of which they can be set in directions P1 and P2 direction of rotation or idling despite rotation of (18) by N-N in direction F1 or F2 can be effectively moved, with the secondary gyroscopic moments Mn1 or Mn2 can be used to the full as a frictional coupler and on the system as an internal one do not act as free moments, namely that from the rotation of the cohponents (1,2,3,8,10,11) around E-E with simultaneous rotation around A-A occurring moment Mn1, which by a Axis perpendicular to A-A and N-N acts, the gyro drive wheels (8) on the friction surfaces from (6) or from (12) presses, and this from rotating the top (1) by B-B in Connection with their simultaneous rotation around E-E occurring moment Mn2 as around the Aohse perpendicular to B-D and N-N rotating the circles 1 driving wheels (1a) to the cup-shaped friction body surfaces of (11) pressed, these moments Mnl and Mn2 the have the same origin and technology as the well-known gyroscopic torque which the Presses pan mill rollers on their grinding surface. Claim 2. Trägruder according to claim 1. according to Figures 2. and 3. characterized by a supporting base (35) from which forces F2 resp. F1 for switching the pins (26,34) in directions P1 bz *. P2 act , namely on a push sleeve (36) which e.g. pushed or pushed over the converter (18) from the output side (28). is withdrawn that this sleeve is also an annular to N-N coaxial Siokung has with which the switching pin (26,34) alternatively in the direction of Pl or P2 can be pressed in with forces Fl or F2, so that in the overrun condition Fig.2. e.g. pin (34) pressed in and bevel gear (8) on conical flange (6) is pressed, and with a stroke (s2) push out with force F1 according to i'ig.3 pin (34) can and pin (26) is pressed quickly so that the bevel gear (8) is pressed against the conical flange (12) is while in Fig. 2. Pin (26) was disengaged, and that so alternately with a downward stroke (s2) the wheel (8) to the left direction of rotation around E-E and with an oppositely directed Stroke (s2) Still claim 2. it is switched to clockwise rotation around E-E, which is analogous to the Gyroscope (1, 1a) working through this on the left or. Clockwise direction of rotation around B ~ B switches, whereby the output torque accordingly ML and the output rotation #b at (18,28,27) goes to left or right rotation, without the input shaft; (30a) needing to be shut down or reversed. Claim 3. Trägruder according to claim 1. @ and 2. and Fig.5. characterized, that instead of from the output side, the switching sleeve (36) from the input side (30a) is pushed over the converter for switching. Claim 4e carrier rudder according to claims 1. to 3. and Fig.4., Characterized characterized in that to reduce the sliding friction of (26,34) on the inner surface the beading of (36) and to reduce the resulting damaging torque (36) the corrugation is shifted to N-N on the inner race (37) of a rolling bearing, whose outer ring (38) is firmly connected to (36) the shift F1 and F2 on (37) transmits with little torque and controls the two levers. Claim 5. Trägruder according to claims 1 to 4 and Fig. 6., Characterized in, that e.g. in application to a motor vehicle rear or front axle or call both at the same time, a converter (18/1 or 18 / r) flanged into each rim (40/1 or 4o) is, d§ from the cardan shaft (42) via a simple bevel angle drive (41) with the same direction drive shafts (30a / 1 or 3oa / r) rotating around N-N, with push bushings (36/1 or (36 / r) of the type in Fig. 5 on pins (26,34) for forward and reverse rotation, @ Also including the well-known Inertialbremsunglgesteuert, for which the known actuating forces P1 and P2 from a hydraulic or pneumatic double working cylinder (38/1 resp. 39 / r) with thrust forces F1 or F2 soft against each other support the solid base (35) of the cylinder ari its central valve plate. Claim 6. Trägruder according to claims 1 to 5 according to Fig.7. as an integrated motor vehicle axle type characterized in that two transducers of the type of Fig.1. to 5th in the axis are arranged in the middle, their input shafts (30a / 1 or 5oa / r) driven in the same direction from the ring gear (43) of the bevel angle drive (42) lead the output shafts (28/1 or 28 / r) to the rims (40 / l or 4o / r) and propel them in the same direction while replacing the compensating engine and by reversing according to Fig. 7. and 8. with the adjusting bushes (36 / l or 36 / r) and Pin (26, or 34) also inertial braking or reverse travel without reversing the Direction of rotation of the cardan shaft (42) deliver, the actuation of the bushes (36) with Double cylinder (39 / r or 39/1) is made from a solid base (35) with strokes (s2), by pushing open the bushings from the input side (30a), and furthermore the system with bearings (47, 48) in the central part and with bearings (46) in the outer shields (45) of a housing (44) is supported rotatably about N-N, in which with bearings (50) the cardan shaft and its bevel gear are also mounted, and the housing (44) Housing cover detachable in the middle at the top and bottom for the assembly and maintenance of (42,41,43,46,47,30a / r, 30a / 1,35,39 / r, 39/1) Has. Claim 7. Trägruder according to claims 1 to 6 in the circuit with degressive Course of the output torque +} E according to Fig. 8. and 10. characterized in that with pin pushed in (down) and pin disengaged (34) at + #, $ # 2, + # 3, + # 4, + # 5, + # 6 the output torque (+ ML + Me) is in the same direction as the input torque M2 In Fig. 10, via the abscissa + # 6 with a falling tendency, torque characteristics (+ ML + Me) occur because for a known reason the gyro rotation + # 5 with increasing + # 6 with constant input rotation + # 1 shows a decreasing tendency, with characteristics unequal input rotations # @, # 12, # 13 between fixed points on the ordinate and fixed points of the straight line Me of the input torque are stretched as Ro @@@ de. Claim 8. Trägruder according to Fig. 1. to 7. and in circuit with pressed-in pin (34) and disengaged pin (26) according to FIG. 9. as a progressive type circuit, characterized in that at the input side + Me shortly after running without turning the input direction of rotation into -ML and - Q 6 416 progressive tendency occurs because the rotation of the spider shaft (4) occurring with (18) without reversing the direction of rotation sGJt and + # 3, by N-N an increase in the rotation + Z on the wheel (21), and in this respect by reversing + # 5 to - fl) 3 the moment at the output on - ML is turned and also -Co 6 is increased according to its amount, whereby the difference - (+ ML -M @) occurs as a counteracting to Me as the moment at the output, but very shortly after the start-up according to Fig. 11. as long as a + (Me-ML) and a + # 6 occurs when the scalar of + Me is even larger than that of -ML @ what with the hochkle @ ternden spinning top - # 5 is eliminated and used in industry and Vehicle drives is hardly noticeable, so that this circuit according to Fig. 9. and 11. with progressive reversed torque characteristic also as an industrial and vehicle forward drive circuit It is used where the output speed is "in series" at a constant or variable input speed flexibly adapt to the load and also with strong Falling output speed should deliver increasing output torques quadratically, what the curvature of the characteristics of Fig.11. indicates. Claim 9. Trägruder as a converter according to claims 1 to 8 and Figures 9 and 11. In progressive switching mode, in particular on motorized drives of FIG. 6. and 7. using a forward gearshift Fig undl1 and a reverse gearshift or, inertial braking circuit Fig. 8. and 10. thereby gekennzeiohnet that bevel gear (41) larger number of teeth than wheel (43) and the drive thereby higher speeds and Torque width, in particular also in the direction of greater travel speeds, 9 a reverse gear is omitted and sometimes more forward gears are saved, m @ tunter also the entire shift gear on the engine can be dispensed with. Claim 10. Trägruder as a converter according to claims 1 to 9 and in forward switching according to Fig. 9. or 11 or, reverse ~ and brake circuit according to Fig. 8. and 10. as Built-in coupling or pulley on motors and other drives, in particular on motors with a bypass characteristic or on asynchronous squirrel cage rotor types marked that shaft (30a) Motere shaft or centered with the motor shaft and is coupled, housing (18, 27) but pulley or (28) output shaft stub will.