DE102008013462A1 - Driving forces moving device for coaxial driving wheels of motor vehicle, has transmission elements that are arranged such that ratio of continuously variable transmission amounts to specific value during adjusted operation mode of gear - Google Patents

Abstract

The device has a distributor and/or differential gear with an input point and two starting points, where the starting points stay torque-moderately in result to internal design of the gear as a planetary gear with planetary ratio of 1.0. A mechanical transmission device i.e. continuously variable transmission (CVT), is rotatably and steplessly adjusted parallel to a transmission path between the input and starting points. Transmission elements provided in the transmission path are arranged such that a ratio of the CVT amounts to 1:1 during adjusted operation mode of the gear.

Description

Of the Subject of the invention relates to a device for automotive differential (Differentials) with those in the preamble of the main and secondary claim described embodiment features for controlled displacement the driving forces between side different achsgleichen Driving wheels of the vehicle chassis. He serves the improvement traction, steering power and stability behavior of the motor vehicle when cornering.

State of the art, disadvantages, task, Solution.

In The car technology and industry is the most in sporty driving style relevant, adversely affecting effect known that with conventional differentials when cornering is negative adjust impacting effects on traction and steering. This problem is already in various references described and dealt with extensively; this is especially on the references [1, 2, 3, 4, 5] referenced.

• a) Parallele Anordnung einer stufenlos verstellbaren mechanischen Übertragungseinrichtung zwischen der Eingangsbasis und einer Ausgangswelle des Differential mit einem Planetenverhältnis von i_Pl = 1,0. In ihrer Neutralstellung läuft sie im Leerlauf mit. Eine Übersetzungsverstimmung in diesen Nebenschluß-Übertragungspfad bedingt in ihr einen Leistungsfluß. Je nach Richtung der Übersetzungsänderung wird der Leistungsanteil des betroffenen Differentialpfades und somit der seitenzugeordneten Fahrwerks-Antriebswelle vermindert oder erhöht

The patent literature already describes various types of such devices. Their type-typical design features are briefly explained below under a) to d). On the basis of representative patents / applications cited there are disadvantages of such devices of these generic types mentioned disadvantages and the motives for the task of the present inventive concept expressed:

• a) Parallel arrangement of a continuously variable mechanical transmission device between the input base and an output shaft of the differential with a planetary ratio of i _Pl = 1.0. In its neutral position, it idles with. A translation detuning in this shunt transmission path causes a power flow in it. Depending on the direction of the ratio change of the power component of the differential path concerned and thus the side-associated chassis drive shaft is reduced or increased

Such a solution lies [6] DE 102 41 918 A1 based, wherein, parallel to a transmission path, the differential arranged continuously variable transmission means consist of a continuously variable rolling body gear.

One Shortcoming of this type of transmission is that they - as in circles the drive technology known - sensitive to overloads react and then break in already low roll or Reibpartieschäden transmission and have increased running noise.

Further is coaxial with a multiple arrangement of its rolling bodies around the output shaft - due to the requirement of absolute synchronous and inclination equal pivoting their axes of rotation to the central output shaft - their storage and adjustment very expensive. In addition, there is a required reversing direction, the axial also depending on the concept also supporting tasks has to accomplish.

Also can (if necessary) increased contact pressure on Rolling body gearbox on the other side on the (axial floating) planet carrier bevel gear acts on the input side bevel gear meshing part (eg, 2-11) detrimental loss-increasing or even wear-promoting impact.

in the second-mentioned embodiment come as disadvantages yet elaborate countershaft gear and Anpresseinrichtungen added.

task and object of the present invention is a device on differential gears to propose the generic type without the aforementioned disadvantages, the both also adjustment and control technical favorable Prerequisites and properties.

• b) Serielle Anordnung einer stufenlos verstellbaren mechanischen Übertragungseinrichtung zwischen einen abtriebseitigen Leistungspfad des Differentials mit i_Pl =|= 1,0.

The solution is achieved according to the invention with the characterizing features of claim 1 and the related dependent claims, based on the use of a proven in automotive transmission system. Other structural and functional advantages will be apparent from the description of the embodiment of the 1 out.

• b) Serial arrangement of a continuously variable mechanical transmission between an output side power path of the differential with i _Pl = | = 1.0.

In [7] DE 14 25 779 U the infinitely adjustable mechanical transmission device also consists of a rolling element transmission as in [6].

To Disadvantages, task and solution largely applies the same as stated in [6].

In addition, a continuously adjustable transmission element in such applications in the steadily required presence safe translation constancy with fine controllability harbors certain operational uncertainties and dangers. This, because z. B. after failure of his line or control systems or the adjustable transmission device itself, the function of the differential because of the then lack of balance in planetary gears with i _Pl = | = 1: 1 is no longer given.

• c) Anordnung von hydraulischen Maschinen an einem Differential-Abtriebspfad zur Beeinflussung des Leistungsgleichgewichtes des Differenzials.

To solve the task also applies here to [6] listed.

• c) Arrangement of hydraulic machines on a differential output path for influencing the power balance of the differential.

at several such concepts with differential variants with one Planetary ratio of i = | = 1.0 becomes hydraulic machines for effecting a load balance in the differential itself used. Here determines the translation position of stepless transmission device in whole or in part Size and force flow direction in this transmission path and thus acts alone as an equilibrium-holding organ of the differential.

In [8] DE 10 2006 018 661 A1 causes the function of a continuously variable transmission device operable as a pump or hydraulic motor hydraulic machine. This claim is used in several ways. The power control in the path of the hydraulic machine takes over an adjustable flow valve. A striking feature of this patent application is inter alia a rotatable training and storage of the hydraulic pump. The main drawback of such concepts - even for any other related versions with throttled hydraulic circuits - is generally that the energy content of the pressure moderately reduced by throttling flow rate component in such pump inserts as pure, the entire vehicle anti-loss design derives detrimental power loss.

Of Further, superimpositions included in such concepts require and countershaft gear extensive design effort, in the present Trap by the rotatable design and Storage of the pump is particularly high.

task and aim of the present invention is to provide devices of the generic type To propose type (use of hydraulic machines), the aforementioned Do not have disadvantages.

The object is achieved according to the invention with the characterizing features of the independent claim as set out claim 2 and their associated subclaims. The design and functional advantages of the solution are based on the descriptions of the 2 and 7 out.

[9] DE 32 39 223 A1 has on a path of a running as a double planetary gear differential on a rotationally connected hydraulic motor which is fed to a driven by a different path of the double planetary gear, controlled pump.

There not just the driving or possibly braking Activity of the hydraulic motor, the load distribution of the output shafts determined, but also for the ever-needed inner Balance in the differential gear inside with unequal planetary ratio must apply, here too apply to [7] listed Security concerns.

Furthermore is the design effort for used in any way Double planetary gear up, also the rotational Connection of hydraulic machines.

Especially Here are the hydraulic throttle losses at this Basis working regulatory organs very detrimental.

• d) Bekannt sind auch Einrichtungen bei denen zum vorbestimmten dosierten Verlagern der Ausgangsleistungen von Differenzialen Elektromaschinen eingesetzt werden

The task, goal and solution also apply here to [6].

• d) Also known are devices in which for the predetermined metered displacement of the output powers of differentials electric machines are used

In [8] DE 10 1004 024 086 A1 are proposed and claimed in connection with transfer cases (automotive differentials) various embodiments of overlay and countershaft transmission, in which electric machines are used as speed-regulating element. A striking embodiment of this patent is that with the interposition of one or more superposition gear electric machine (s) on the differential output shaft (s) act, wherein a base of the formed as a planetary gear superposition gear is in rotational connection with the planet carrier of the differential.

at Other known variants cause one or more electric machines the balance on one of a double planetary gear set Differential the desired effect.

Also Conceptions are known in which by means of countershaft gears Electric machines are connected to the differential output shafts.

adversely is the high design effort of as connecting elements between superposition gears and the electric machines serving countershaft transmission, in particular in conjunction with differential concepts with double planetary gearsets.

With the use of double planets in the actual differential, where i _ges = | = 1.0 and therefore the electric machines are required for steady equilibrium, here too the related safety concerns mentioned in [6] apply. Also are regenerative and motor-acting, as Transmission elements used electric machines not favorable in terms of their Gesamttwirkungsgrates. In particular, when they have to be in continuous operation as an active element of the differential, especially if they have to transfer part of the net power of a differential path.

• e) Weiterhin sind vielfältige Vorschläge solcher Einrichtungen an Differenzialen bekannt die mit unterschiedlich ausgeführten Differentialen und verschiedenen Überlagerungs- und Vorgelege-Getriebevariationen als Geschwindigkeits- und Drehmomenten regulierende Komponente eine Schlupfkupplung aufweisen. Solche Ausführungen beinhalten z. B. [9] DE 39 00 638 C2 und [10] DE 10 2004 013 542 A1 .

Therefore, the present inventive concept for improving such devices saves such variants.

• e) Furthermore, various proposals such devices to differentials are known to have a slip clutch with differently designed differentials and different overlay and counter gearbox variations as a speed and torque regulating component. Such designs include z. B. [9] DE 39 00 638 C2 and [10] DE 10 2004 013 542 A1 ,

main disadvantage Such concepts is that of the entire vehicle drive concept detrimental power loss resulting from the factors Slip torque × differential speed results. This has a special effect in concepts crass, where slip couplings directly in the output path sit the differential, so the full drive torque of the vehicle drive wheel are exposed.

There Slip clutches are subject to wear and tear their limited life a certain operational uncertainty and require a special maintenance dedication, what is the risk of a Lubricant contamination by their inevitable Abrasion added.

Furthermore they require special design precautions for one safe dissipation of the results of their slipping performance, in a relatively narrow range occurring heat development.

The present invention concept is therefore fixed only on the creation of low-loss facilities. (It should be noted that the in 1 used and claimed couplings ( 12 / 13 ) ( 21 / 22 ) is pure disconnect couplings without the use of a slip effect)

embodiments

The Invention is described in embodiments by the following illustrates drawings described. These schematic representations show in:

1 a parallel frictional engagement of a belt pulley transmission (CVT) to a force path of a conventional conventional automotive differential, with speed reducing step gears to adjust the overall ratio of this parallel path to the path of the affected differential path and the essential components serving the CVT control.

2 an arrangement of two hydraulic displacement machines on both output shafts of the differential with a schematic representation of hydraulic control elements for controlling the pressure medium flow between the hydraulic displacement machines for the purpose of energy transfer between the two differential output shafts.

3 the embodiment of a positive displacement machine as a multi-stage gear pump.

4 and 5 Modified variants of the multi-stage gear pump after 3 , wherein in the sectional views associated with a common centerline of the 4 and 5 the arrangement of a planetary gear in the interior of the driven central impeller is shown as a speed-transmitting transmission element between the differential output shaft and the driven impeller,

5 in addition to 4 one of the pump planetary gear combination superior separation clutch.

6 a sectional view of 4 -gemäßen gear pump in a plane perpendicular to the differential shaft axis cutting plane.

7 a modification of the 2 with the arrangement of multi-stage hydraulic displacement machines in the form of two-stage gear pumps 3 on both output shafts of the differential with associated hydraulic controls.

descriptions

To 1

In the case of the conventional automotive type differential, the torque introduction takes place by means of a cardan shaft 1 over bevel gear 2 to a bevel gear 3 , which in the interior as a planet carrier 4 is formed on which the bevel gears designed as planetary gears 5 are stored, which in turn with on the output shafts 7 and 9 rotationally fixed bevel gears 6 and 8th are engaged. Of course, the drive train with the invention modified differential also be different: z. B. in a front-wheel drive, where the differential is constructively connected to a transmission with horizontal transmission shafts, the torque is then over a Spur gear drive to the planetary bridge 4 directed.

A rotary connection from the planetary gear 2 starting from the differential over one on an axis 10 stored bevel gear 11 , an associated coupling base 12 a clutch 13 , to a conical friction disc set 14 that with a transfer belt or chain 15 and a frictionally engaged further pulley set 16 a known in the art
and proven continuously variable CVT forms. On details of this known hydraulically pressed and controlled mechanical transmission is therefore not discussed in more detail, the same applies to the couplings used. Last named conical friction disc set 16 is rotatable on the output shaft 9 stored and stands with the inner sun gear 17 a coaxial on this output shaft 9 seated planetary gear in rotary connection. This consists further on the housing-fixed planet carrier 18 sitting planet wheels 19 and the outer sun wheel 20 by an internal toothing of an external coupling base 21 is formed, their associated inner clutch base 22 with the output shaft 9 is in a fixed rotational connection.

The clutches 12 / 13 and 21 / 22 Although not important for the principal function of the energy transfer between the differential shafts, but (Idling loss minimization can be useful, as they allow a decoupling of the CVT from the differential path and thus drag moments do not arise up-to-the-minute routes, or to be up-to-date and useful in a desired economic

The hydraulic supply of the CVT takes over to the drive base ( 2 ) of the differential connected hydraulic pump 23 , Your pressure line 25 leads to a four-way valve 25 formed as a four-way control spool with somewhat intersecting control edges. About the control lines 27 and 28 become the impression cylinders of the conical friction disc pairs 24 and 15 supplied with adjusting or Abstützdruck after a predetermined mode, or for their relaxation or drainage with the drain line 29 connected. In a known manner is to limit the pump pressure and thus the maximum Anprssung the conical friction discs of the CVT's a pressure relief valve 30 , As well as to ensure a minimum contact pressure of the CVT rubbing a (preferably adjustable) preload valve 31 in the drainage line 29 arranged. The ratio control of the CVT - hydraulically controlled via four-way valve 26 , whereby the power flow in the direction and size of this shunt power path is determined, as well as the coupling functions controls the electronic / electrical control device 32 after a predetermined mode. To accommodate various required parameters, sensors are assigned to them that capture at least the following quantities: CVT translation 33 , Pump pressure 34 , the pressure ratio of both pressure cylinders to each other 35 ; Speeds of the differential output bases 36 . 37 ,

The translation system of the CVT ( 14 . 15 . 16 ), And thus the regulation of the load distribution on the Differentialabriebswellen or on the associated achsgleichen drive wheels of the vehicle by the electronic / electrical control and regulating device 32 after knowledge and requirements known in the automotive industry. Reference should be made to the references [1, 2, 3, 4, 5]. The integration and utilization of industry-known CVT-specific characteristics such. B. Form and control pressure dependencies on the load, facilitate and simplify the realization of control strategies and control operations, as well as the minimization of idling and power loss of the CVT. Also load limitations can be arranged by placing a simple pressure relief valve 30 , which is advantageously carried out to adapt to different operating conditions adjustable, easily realize.

A effective, with relatively small manipulated variables enabling load regulation on the CVT in this power path a highly dynamic management of the intended benefit transfer of one differential output shaft to the other.

Of the relatively small required control range allows a specific high utilization of the CVT proven in the motor vehicle. It also favors or allows the output side arrangement of the Drehzahlreduzierstufe, matched to usual gear ratios conventional differentials, at (relatively) high speed running CVT an eco-friendly and space-saving Design of this converter. A significant advantage of his invention Its use is that, in contrast to other solutions, where combinations of power and work machines the desired Effect effect, or even a speed control effect on the sacrifice of Slip performance based, that here only the pure between the Car sides demanded to be shifted differential suspension drive power becomes. Especially since he still has a low efficiency are, the losses of this conception very small.

to 2 :

The differential consists essentially of those in a known manner executed in the description 1 mentioned striking elements 1 to 9. Its output shafts 7 and 9 are with two, both pump and as motor operable displacement machines 40 . 41 and 42 . 43 connected, preferably they are coaxially arranged on the output shafts of the differential. They can also be combined to form a unit. Your connection cables 44 to 51 depending on the symbolically represented switching system by multi-channel reusable controls 52 . 53 with the suction or return line 56 or with the pressure line 57 connected. These switching elements 52 and 53 be from the actuator 54 operated, in turn, to one of an electronic / electrical control and regulating device 55 is driven according to a predetermined algorithm. In the present example, these switching elements 52 . 53 preferably mechanically coupled multi-edge control slide. You can also be designed as a different kind of hydraulic switching elements, such. B. consist of several individually controllable valves.

The switching strategy of the multi-channel reusable switching elements 52 . 53 essentially consists of the connecting cables 44 - 51 the displacer machines 40 - 43 in an alternative way, as needed:
over their control channels 52 _{α, β, γ, δ} . 53 _{ε, ζ, η, θ} , and 52 _al . 53 _mx with each other, with a suction or return line 56 or a pressure line 57 with accumulator 66 get connected. The suction and return channel located in the immediate area of these control channels 56 and pressure channel 57 are advantageously in the control housing 52 . 53 integrated.

• I.) Inaktiver Betrieb der Einrichtung, bei längerer Geradeausfahrt oder einem ökonomischen Betriebsprogramm (mit geringen Anforderungen oder Bedarf an Antriebskräfteverlagerungen). Mittlere bzw. Ruhe- Betriebsstellung der Schaltelemente 52, 53: beide Anschlussleitungen 44–45, 46–47, 48–49 und 50–51 aller Verdrängermaschinen sind über die Steuerkanäle 52_α-a,e-β , 52_γ-h,k-δ , 53_ε-n,q-ζ und 53_η-t,w-θ mit einander verbunden. Sie fördern weitgehend drucklos und verlustleistungsarm im Kreise. Alle anderen Steuerkanäle 52_{a,c,d,f,g,i,j,l} , 53_{m,o,p,r,s,u,v,x} zu den Kanälen 56 und 57 sind gesperrt.
• II.) Aktivität der Einrichtung bei Lenkereinschlag 50 in Fahrtrichtung links, angestrebt und bewirkt wird die Antriebsverstärkung auf des Treibrad rechts und eine Verminderung links: auf der linken KFZ-Seite wirken die Verdrängermaschinen 40, 41 als Pumpen.

In the illustration, the respective active control paths for three different operating and switching stages I, II and III are shown. In the operations described below are the displacement machines 40 and 41 the differential output shaft 7 the left side of a car and the displacement machines 42 . 43 on the output shaft 9 assigned to the right side of the car.

• I.) Inactive operation of the device, during longer straight-ahead or an economic operating program (with low requirements or demand for driving force shifts). Mean or idle operating position of the switching elements 52 . 53 : both connection lines 44 - 45 . 46 - 47 . 48 - 49 and 50 - 51 All positive displacement machines are via the control channels 52 _{α-a, e-β} . 52 _{γ-h, k-δ} . 53 _{ε-n, q-ζ} and 53 _{η-t, w-θ} connected with each other. They promote largely depressurized and loss of power in circles. All other control channels 52 _{a, c, d, f, g, i, j, l} . 53 _{m, o, p, r, s, u, v, x} to the channels 56 and 57 are locked.
• II.) Activity of the device when steering 50 in the direction of travel on the left, the drive gain on the right-hand drive wheel and a reduction on the left: the displacement machines act on the left-hand side of the vehicle 40 . 41 as pumps.

They are on the suction side with their connecting cables 45 and 47 over the spreader channels 52 _β-d and 52 _δ-j with the suction and return channel 56 connected. Verdrändermaschine 40 promotes via its pressure line 44 and the control channels 52 _α-a in the pressure channel 58 , The second displacement machine 41 on wave 7 is intended for metering the pressure medium transfer from the left side of the vehicle to the right. Your pressure line 46 leads over the control channel 52 _γ-g also to the pressure line 57 , Its control edges are designed in such a way that there is an analogue control piston travel-dependent flow characteristic.

On the right side of the car promotes in this Schaltstatium II, the outer displacement pump 42 over the link 56 > 53 _s-η > 49 > 42 > 48 > 53 _θ-w > 56 low-pressure and low-loss in circles. displacement 43 is due to the pressure medium inflow from the pressure channel 57 via control channel 53 _m-ε on the one hand and by the connection of their other channel 50 over the control channel 53 _ζ-p with the suction and return channel 56 on the other hand, acting as a motor switched.

• III.) Aktivität der Einrichtung bei Lenkereinschlag 50 in Fahrtrichtung rechts, angestrebt und bewirkt wird die Antriebsverstärkung auf des Reibrad links und eine Verminderung rechts: Die Funktion der Verdrängermaschinen 40 bis 43 verhält sich spiegelbildlich zu II, die rechten Verdrängermaschinen 40, 43 wirken nun als Pumpen.

The flow rate of the pump 41 to the pressure line 57 determining control channels 52 _γ-g and the inlet flow of the hydraulic motor 43 determining spreader channels 53 _m-ε are designed so overlapping that they are to their neighboring control channels 52 _h and 53 _n both pressure medium the pressure channel 57 as well as the suction channel 56 respectively.

• III.) Activity of the device in steering impact 50 in the direction of travel to the right, aimed and causes the drive gain on the friction wheel left and a reduction to the right: The function of the displacement machines 40 to 43 behaves in mirror image to II, the right-hand displacement machines 40 . 43 now act as pumps.

pump 42 continuously conveys pressure medium out of suction line 56 above 53 _η-u . 53 _θ-x in the pressure line 57 , The flow rate of the pump 43 out 56 above 53 _o-ε is through control channel 53 _ζ-p , which has the same control characteristics as the under 53 _η-g described, to the pressure line 57 guided.

On the left side of the car, the positive displacement engine benefits 40 low-pressure and low-loss in circles. The other displacement machine 41 works by having its connection line 47 over the control channel 52 _l-δ with pressure medium off 57 is acted as a hydraulic motor, driving on shaft 7 ,

In both cases II and III exceeds for the same size displacement of the displacement machines si certainly the delivery volume of the two on one side of the vehicle acting as a pumping displacement machines far the displacement of a thus supplied, operated as a hydraulic motor displacement machine on the other side of the car. In order to avoid too high back pressure on the output side of each determining the load distribution pump are in their pressure lines 46 and 50 in the suction and return channel 56a leading pressure relief valves 61 and 62 arranged. Thus the energy of the "regulated flow rate" of the displacement machines operating as pumps 41 and 43 not lost, but the pressure level of the suction line 56a is good (in which, so to speak, the pumps are "preloaded"), is in the associated suction and discharge line 26 a check valve 68 arranged. Of course, this useful energy recovery effect only works if the geometric rolling conditions of the chassis during cornering are such that there is no need for any additional supply of pressure medium in the sum. Another economically useful embodiment of the device consists in that the energy content of excess delivery in one with the pressure line 57 connected accumulator 67 is deposited. When designing the control edges in the switching elements 52 . 53 It should be noted that in order to avoid harmful cavitation in the positive displacement machines and to ensure continuous availability in the area of (geometric) switching sections, no longer closed suction connections will be effective. For this purpose, in particular in the case of flow reversal, an "overlapped transition" of adjacent control channels and edges relevant in this respect is to be aimed for Advantageously, different adjustments of the delivery volumes to a plurality of displacement machines sitting on a shaft or the stages of a displacement machine may be required. On the one hand, during normal driving - where the useful effect of such devices is particularly relevant at higher driving speeds - the volumetric delivery surplus of the pumps can be kept low due to the small steering deflections occurring excess flow volumes in the accumulator 67 get saved. This can be especially when incorporating such facilities in modern vehicle stabilization systems where z. B. caused by ejection major track injuries (vehicle inclination) to correct their highly active one-sided drive actions are required to be very useful.

This energy transfer from one differential output shaft to the other according to the invention is performed by a computer-based rake control and regulating device 55 according to a predetermined algorithm according to various aspects and criteria, such as. As discussed in Refs. [1, 2, 3, 4, 5], controlled. Sensors for the control method, which report important values, are located on the output shafts 7 and 9 arranged (combined) torque and speed sensors 64 and 65 ,

Electronic / electrical Elements of such control devices are advantageously in automotive anti-lock and stability systems integrated. Also is economical Considerations to aim for control functions of the proposed facility taken from such existing or enhanced tax systems become.

to 3

The designed as a two-stage gear pump displacement machine is coaxial about the differential output shaft 71 arranged. Advantageous is an integration in the differential housing. Your pump housing 70 has an outer oval shape, adapted in about the shape of the inevitable from the large planetary gear 3 embossed differential housing. The middle impeller 72 is rotationally fixed to the pump shaft 71 ( 7 . 9 ) and stands with its teeth 72a with the gears 73a and 74a the side pump wheels 73 and 74 engaged. With a presumed direction of rotation "right" of the driven middle impeller 72 promote:
from the pump suction 75 teeth volumes 72a Pressure medium in the pump pressure chamber 78
from the pump suction 75 teeth volumes 73a Pressure medium in the pump pressure chamber 77
from the pump suction 76 teeth volumes 72a Pressure medium in the pump pressure chamber 77
from the pump suction 76 teeth volumes 74a Pressure medium in the pump pressure chamber 78 ,

How out 7 can be seen and described in more detail, with appropriate design of the control channels and assignment of the pump-connecting channels, the present networked Förderkreisstruktur for the inventive use of Mehrkreiszahnradpumpen suitable.

To 4 . 5 and 6

The pump housing 80 with a central bearing seat for the passing output shaft 79 of the differential, with its cavities for the seat of the middle impeller 82 and the outer pump wheels 83 . 84 as well as the suction and pressure chambers 75 . 76 and 77 . 78 has as a seat and bearing base for the inner impeller 82 a not over the entire inner width extending annular ridge 81 on. This inner impeller 82 is by means of a connecting web 85 with one on the differential output shaft 79 stored, act as an inner sun gear of a planetary gear the gear 86 connected. This stands with one on a shaft-fixed planet carrier 88 stored planetary gear 87 engaged, which in turn at one, in the housing web 81 arranged internal toothing 89 unwinds form-fitting. In these by the elements 86 . 87 . 89 educated, over his jetty 88 through wave 79 driven planetary gear is the rotational movement of the differential output shaft 79 to the middle impeller 82 translated into fast. As a result, the power and the torque of the pump which can also be operated as a hydraulic motor are increased, which allows a smaller installation space of such positive displacement machines. Space occupancies by the planetary gear inside the middle impeller are harmless, since a relatively large dimensions of the pump wheels is required anyway for the application of the required hydraulic power for these applications at the relatively low automotive axle drive speeds. However, this requirement is greatly mitigated by the use of such a pump gear faster driving gearbox.

In case of non-active dynamic driving, z. B. in an economic driving program, where the sought and made possible by the inventive idea "shifting the driving forces between achsgleichen drive wheels of the vehicle chassis" is not required to exclude idling losses of positive displacement machines, is an in 5 schematically shown arrangement of a switching or separating clutch provided that is able to decouple the positive displacement machine from the motor vehicle drive train. Here is the planet carrier 90 with one in the pump housing 80 coaxial around the shaft 79 arranged clutch 91 connected.

To 7 The present schematic represents a modification of the 2 in which the two displacement machines on each Differenzialabriebswelle by a multi-stage displacement machine after the 3 to 6 replaced with their networked conveyor lines. In essence, the interaction of the individual conveyor sections designed as a gear pump two-stage displacement machine (in clockwise rotation of the driven central impeller) should be clarified.

The position numbers of their connection lines are off 3 taken over and supplemented with the page labels L = left, R = right.

• I.) Inaktiver Betrieb der Einrichtung.

The differential items 1 to 9 correspond to those in FIG 1 and 2 ,

• I.) Inactive operation of the device.

• II.) Aktivität der Einrichtung bei Lenkereinschlag 56 in Fahrtrichtung links, angestrebt und bewirkt wird die Antriebsverstärkung auf das KFZ-Treibrad rechts und eine Verminderung links: Auf der linken KFZ-Seite sind Förderstufen der Verdrängermaschine 70R als Pumpen geschaltet.

In this mode of operation associated average operating position of the switching elements 52 . 53 are each all Pumpensaugräume 75L . 76L and 75R . 76R with the pressure chambers 77L . 78L and 77R . 78R connected. The flow between these suction and pressure chambers flows largely unpressurized and loss of power on their associated control channels of the hydraulic control elements 52 and 54 in circles. All other inactive control channels 52 _{a, e, d, f, g, i, j, i} and 53 _{m, o, p, r, s, u, v, x} are locked.

• II.) Activity of the device when steering 56 in the direction of travel left, aimed and causes the drive gain on the vehicle drive wheel right and a reduction left: On the left side of the car are conveyor stages of the displacement machine 70R switched as pumps.

pump room 75L is a first suction chamber of the pump 70L the over control channel 52 _β-d with the suction line 56 communicates. From him, a part of sucked pressure medium through the Verzahnungsvolumina 73a of the impeller 73 to the pressure room 77L and the other part of the sucked pressure medium through the Verzahnungsvolumina 72a of the impeller 72 to the pressure room 78L promoted.

pump room 76L is a second suction chamber of the pump 70L the over control channel 52 _g-γ with the suction line 56 communicates. From him, a part of sucked pressure medium through the Verzahnungsvolumina 74a of the impeller 74 to the pressure room 78L and the other part by the gear volumes 72a of the impeller 72 to the pressure room 77L promoted.

pump room 77L is above the control channel 52 _α-a and pressure room 78L via control channel 52 _δ-j with the pressure line 57 in connection.

On the right side of the car is a step of the positive displacement machine 70R switched as a motor, in the example given with the pump chamber 76R outgoing. It is over control channel 53 with the pressure line fed by the pumps of the left side of the vehicle 57 connected and acted upon in this way with pressure medium. This acts on one side on the teeth 72a and 74a impulsive. The pressure medium transported in these gears accumulates in the chambers 77R and 78R , From here it passes over 53 _ε-m and 53 _θ-v relaxed to the suction and return channel 56 back.

The second pump suction chamber 75R is over 53 _u-η with the suction line 56 connected. From her, the medium is depressurized in the chambers connected to the suction line 77R and 78R promoted.

By networking the conveyor lines 72a , 73a . 74a With two pump chambers each of these multi-stage displacement machines, it is expedient to have several pressure-side-active control channels with such a control piston path-dependent Flow characteristic to provide that excess pressure medium over overlapping control paths to the suction line 56 flow away. Of course, such multiple dividing control edge configurations can be used on any vehicle side in any way.

• III.) Aktivität der Einrichtung bei Lenkereinschlag 50 in Fahrtrichtung rechts, angestrebt und bewirkt wird die Antriebsverstärkung auf das KFZ-Treibrad links und eine Verminderung rechts: Hierzu sind die Funktionsschemata der Steuerelemente, wie aus der Darstellung erkennbar, seitenspiegelbildlich zu II wirksam. Der Energietransfer erfolgt in gleicher Weise in umgekehrter Richtung.

As under 2 dealt with, here is the additional arrangement of pressure relief valves 61 and 62 in the pressure lines of the positive displacement machines (as a protective measure with drain blocked in short control piston positions).

• III.) Activity of the device in steering impact 50 in the direction of travel on the right, the drive gain is aimed at the vehicle drive wheel on the left and a reduction on the right: For this purpose, the functional diagrams of the control elements, as can be seen from the illustration, are mirror-inverted to II. The energy transfer takes place in the same way in the opposite direction.

The advantages that can be gained with the present conception correspond to those already mentioned below 2 dealt with. Add to that the descriptions in the 3 to 6 highlighted advantageous functional and design features.

Considered pamphlets

Press articles

• [01] Gerd Gregor Feth: "More power on the outside rear wheel" FAZ from December 24, 2007
• [02] BW Kießler / M. Lindner: "Mechatronics distributes drive torques at any time" VDI news from 14.12.2007

Patents:

• [03] DE 10 2004 025 777 A1
• [04] DE 10 2004 013 542 A1
• [05] DE 39 00 638 C2
• [06] DE 102 41 918 A1
• [07] DE 14 25 779 U1
• [08] DE 10 2006 018 661 A1
• [09] DE 32 39 223 A1
• [10] DE 10 2004 024 086 A1

1

KFZ-Kardanwelle

2

Kegelrad (Differenzial-Eingansbasis)

3

Kegelrad

4

Planetenradträger an 3

5

Planetenkegelrad

6

Kegelrad (an 7)

7

Abtriebswelle (links)

8

Kegelrad (an 9)

9

Abtriebswelle (rechts)

10

Achse (von 12, 14, 15)

11

Kegelrad (an 12)

12

innere Kupplungsbasis

13

Schaltkupplung (äußere Basis)

14

CVT-Kegelreibscheibensatz

15

CVT-Übertragungsband- bzw. Kette

16

CVT-Kegelreibscheibensatz

17

inneres Sonnenrad

18

Planetenträger

19

Planetenrad

20

äußeres Sonnenrad

21

äußere Kupplungsbasis

22

innere Kupplungsbasis

23

Hydraulikpumpe

24

Pumpen-Saugleitung

25

Pumpen-Druckleitung

26

Stellelement

27, 28

Zyl.-Steuerleitungen (von 14, 16)

29

Abflußleitung

30

Überdruckventil

31

Verspannventil

32

Elektronisch/elektrische Regel- und Steuereinrichtung

33

Sensor der CVT-Übersetzung

34

Sensor des Pumpendruckes

35

Sensor des Druckverhältnisses beider CVT-Druckzylinder

36

Sensor der Eingangsdrehzahl

37

Sensor der Ausgangsdrehzahl

38

Sensor des Lenkwinkels

to 1

1

Car propshaft

2

Bevel gear (differential input base)

3

bevel gear

4

Planet carrier on 3

5

planetary bevel gear

6

Bevel gear (on 7 )

7

Output shaft (left)

8th

Bevel gear (on 9 )

9

Output shaft (right)

10

Axis (from 12 . 14 . 15 )

11

Bevel gear (on 12 )

12

inner clutch base

13

Clutch (outer base)

14

CVT Kegelreibscheibensatz

15

CVT transmission band or chain

16

CVT Kegelreibscheibensatz

17

inner sun wheel

18

planet carrier

19

planet

20

outer sun gear

21

outer coupling base

22

inner clutch base

23

hydraulic pump

24

Pump suction line

25

Pump pressure line

26

actuator

27, 28

Cyl. Control lines (from 14 . 16 )

29

drain line

30

Pressure relief valve

31

Verspannventil

32

Electronic / electrical control and regulating device

33

Sensor of CVT translation

34

Sensor of pump pressure

35

Sensor of the pressure ratio of both CVT pressure cylinders

36

Sensor of input speed

37

Sensor of output speed

38

Sensor of the steering angle

40, 41

Verdrängermaschine (an 7)

42, 43

Verdrängermaschine (an 9)

44, 45

Anschlussleitung (von 41)

46, 47

Anschlussleitung (von 42)

48, 49

Anschlussleitung (von 43)

50, 51

Anschlussleitung (von 42)

52

hydraulisches Mehrkanal-Mehrweg-Steuerelement

52_{(a,b,c,d,e,F,g,h,i,j,k,l,)}

kanalseitige Steuerkanäle in 52

52_α,β,γ,δ

verdrägermaschinenseitige Steuerkanäle in 52

53

hydraulisches Mehrkanal-Mehrweg-Steuerelement

⁵³(m,n,o,p,q,r,s,t,u,v,w,x)

kanalseitige Steuerkanä. in 53

53_ε,ζ,η,θ

verdrängermaschinenseitige Steuerka. in 53

54

Stellelement (von 52, 53)

55

Elektron./elektrische Regel und Steuereinrichtung

56

Saug- und Rückflusskanal (in 52, 53)

57

Druckkanal (in 52, 53)

58

Saugleitung

59

Lenkrad

60

Lenkwinkelsensor

61, 62, 63

Überdruckventil

64, 65

kombinierter Drehmoment-/Drehzahlsensor

66

Drucksensor (an 57)

67

Druckspeicher

68

Rückschlagventil

69

Saugleitung

to 2

40, 41

Positive displacement machine (at 7 )

42, 43

Positive displacement machine (at 9 )

44, 45

Connecting cable (from 41 )

46, 47

Connecting cable (from 42 )

48, 49

Connecting cable (from 43 )

50, 51

Connecting cable (from 42 )

52

Hydraulic multi-channel reusable control

52 _{(a, b, c, d, e, F, g, h, i, j, k, l,)}

Channel-side control channels in 52

52 _{α, β, γ, δ}

damper machine side control channels in 52

53

Hydraulic multi-channel reusable control

⁵³ (m, n, o, p, q, r, s, t, u, v, w, x)

Channel-side control channels. in 53

53 _{ε, ζ, η, θ}

displacement machine-side Steuerka. in 53

54

Actuator (from 52 . 53 )

55

Electron./electric control and regulating device

56

Suction and return channel (in 52 . 53 )

57

Pressure channel (in 52 . 53 )

58

suction

59

steering wheel

60

Steering angle sensor

61, 62, 63

Pressure relief valve

64, 65

combined torque / speed sensor

66

Pressure sensor (on 57 )

67

accumulator

68

check valve

69

suction

70

Pumpengehäuse

71

Differenzialabtriebswelle (= 7, 9)

72

mittleres Pumpenrad

72a

Verzahnung an 72

73,74

äußeres Pumpenrad

73a, 74a

Verzahnung (an 73, 74)

75,76

Pumpensaugraum

77,78

Pumpendruckraum

to 3

70

pump housing

71

Differential output shaft (= 7 . 9 )

72

middle impeller

72a

Toothing on 72

73.74

outer impeller

73a, 74a

Toothing (on 73 . 74 )

75.76

pump suction

77.78

Pump pressure chamber

79

Differenzialabtriebswelle (= 7, 9, 71)

80

Pumpengehäuse

81

ringförmiger Gehäusesteg (Sitz von 82)

82

mittleres Pumpenrad

82a

Verzahnung von 82

83, 84

äußeres Pumpenrad

83a, 84a

Verzahnung (von 83, 84)

85

Mitnehmersteg (86–82)

86

inneres Sonnenrad

87

Planetenrad

88

wellenfester Planetenträger

89

äußeres Sonnenrad (an 82)

90

kupplungsfester Planetenträger

91

Schaltkupplung

to 4 . 5 . 6 . 7

79

Differential output shaft (= 7 . 9 . 71 )

80

pump housing

81

ring-shaped housing web (seat of 82 )

82

middle impeller

82a

Toothing of 82

83, 84

outer impeller

83a, 84a

Toothing (from 83 . 84 )

85

Carrier web ( 86 - 82 )

86

inner sun wheel

87

planet

88

shaft-fixed planet carrier

89

outer sun gear (at 82 )

90

Clutch-proof planet carrier

91

clutch

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - DE 10241918 A1 [0004, 0076]
• - DE 1425779 U [0011]
• - DE 102006018661 A1 [0016, 0076]
• - DE 3239223 A1 [0020, 0076]
• - DE 101004024086 A1 [0025]
• - DE 3900638 C2 [0030, 0076]
• DE 102004013542 A1 [0030, 0076]
• - DE 102004025777 A1 [0076]
• - DE 1425779 U1 [0076]
• DE 102004024086 A1 [0076]

Cited non-patent literature

• - Gerd Gregor Feth: "More power on the outside rear wheel" FAZ from 24.12.2007 [0076]
• - BW Kießler / M. Lindner: "Mechatronics distributes drive torques at any time" VDI news from 14.12.2007 [0076]

Claims (18)

Means to automotive differential gears for shifting the driving forces between achsgleichen drive wheels of the vehicle chassis consisting of a distributor or differential gear known type (car differential) with an input base and two output bases, the output bases as a result of the internal design of the differential gear as a Planetary gear with a planetary ratio of i _Pl . = 1.0 torque balanced with a parallel to a transmission path between the input base and a base of the differential rotationally fixed continuously variable mechanical transmission device, characterized in that the continuously variable mechanical transmission means a belt pulley (CVT) (CVT) ( 14 . 15 . 16 ); wherein in the transmission path of the CVT such formed transmission elements ( 2 . 11 . 17 . 20 ) are arranged so that in a balanced operation of the differential (i _{output shafts} = 1: 1), the translation of the CVT ( 14 . 15 . 16 ) is about 1: 1. Device for vehicle differential gears for shifting the driving forces between achsgleichen drive wheels of the vehicle chassis consisting of a distributor or differential gear known type (automotive - differential) with an input base and two output bases, the output bases as a result of the internal design of the differential gear as a Planetary gear with a planetary ratio of i _Pl = 1.0 torque balanced, with at least one connected to an output shaft of the differential hydraulic machine, preferably a hydraulic pump, characterized in that each output shaft ( 7 and 9 ) of the differential with at least two (hydraulic) displacement machines ( 40 . 41 ) and ( 42 . 43 ), or with a multi-stage positive displacement machine ( 70L . 70R ) is in rotary connection, the suction and pressure sides ( 44 - 51 ) of these individual displacement machines ( 40 - 43 ) or individual conveyor stages ( 77L . 78L . 77R . 78R ) multi-stage positive displacement machines ( 70L . 70R ) with such hydraulic control and switching elements ( 52 . 53 ) are connected in such a way that, alternatively and alternately switchable, the delivery flows of several displacement machines or displacer stages connected as pumps of one side of the vehicle pressurize the displacement machines or displacer stages of the other vehicle side connected as hydraulic motors. Device according to claim 1, characterized in that the cone friction disk set ( 14 ) of the CVT on the drive side of the differential via a bevel gear connected to it ( 11 ) with the input bevel gear ( 2 ) of the differential is in rotary connection, the driven pulley set ( 16 ) of the CVT via a speed-reducing transmission with rotational direction reversing function with the output shaft 9 the differential is rotationally connected, the translations of the speed-reducing solid-state elements ( 2 / 11 . 17 / 19 / 20 ) in the transmission path of the CVT are designed and tuned so that at i = 1: 1 position of the CVT, the total translation conversion of this path at least 65% on the output shaft ( 9 ) inclined side of the CVT ( 14 / 15 / 16 ) he follows. Device according to claim 1 and 3, characterized in that the output shaft side conical frictional disk set ( 16 ) of the CVT coaxially about the output shaft ( 9 ) of the differential is formed and arranged. Device according to claim 1 and 3, characterized in that the output shaft ( 9 ) inclined turning and speed reducing transmission element of one, both functions effected coaxially about the output shaft ( 9 ) arranged planetary gear ( 17 . 18 . 19 . 20 ) consists Device according to claim 1, 3 and 5, characterized in that the output shaft ( 9 ) inclined conical friction disk set ( 16 ) of the CVT constructive in the planetary gear ( 17 / 18 / 19 / 20 ), wherein the output drive disk set ( 16 ) of the CVT an extended, the output shaft ( 9 ) coaxially enclosing seat base has at its end rotationally fixed the inner sun gear ( 17 ) of the planetary gear ( 17 / 18 / 19 / 20 ) sits. Device according to claim 1, 3 5 and 6, characterized in that between the planetary gear ( 17 . 18 . 19 . 20 ) and the output shaft ( 9 ) a clutch ( 21 . 22 ) is arranged as drehverbindendes element, the clutch ( 21 . 22 ) forms a constructive unit largely with the planetary gear. the coupling housing ( 21 ) serving as an outer sun gear of the planetary gear internal toothing ( 20 ), the planet gears ( 19 ) on a housing-fixed web ( 18 ) are stored. Device according to claim 1 and 3, characterized in that between the differential drive side inclined CVT Antriebsscheibensatzes ( 14 ) and its connection base to the differential a clutch ( 12 . 13 ) is arranged this clutch is designed largely with the adjacent friction disc of the CVT as a structural unit. Device according to claim 1 and any one of the preceding claims, characterized in that the pressure medium supply of the hydraulically pressed CVT at the input base ( 1 ) of the differential a hydraulic pump ( 23 ) is coupled. Device according to claim 1 and any preceding claims, characterized in that for the translation control of the CVT and for the control of the clutches ( 12 . 13 ) 21 . 22 ) and a controllable biasing valve ( 31 ) an electronic / electrical computing and control device operating according to a predetermined algorithm ( 32 ), said calculating and regulating device ( 32 ) is integrated into a motor vehicle antilocking or stabilization system or that such are designed to effect the predetermined function, furthermore associated with at least one of the following sensors and integrated in the function of the computing and control device: sensor for detecting the CVT Translation position ( 33 ) Sensor for detecting the pump pressure ( 34 ) Sensor for detecting the pressure ratio of both CVT pressure cylinders ( 35 ) Sensor for detecting the steering angle ( 38 ) Sensor for detecting the differential output speeds ( 36 . 37 ) Sensor for detecting the steering angle ( 38 ) Device according to claim 2, characterized in that the displacement machines are gear pumps, wherein the with the differential output shaft ( 7 . 9 . 71 . 79 ) connected impeller ( 72 ) on the output shaft ( 7 . 9 ) sits rotationally. Device according to claim 2, 11, characterized in that the gear pumps are designed in several stages, wherein the side of the output shaft ( 7 . 9 . 71 ) enclosing, driven central impeller ( 72 . 82 ) at least two pump wheels ( 73 . 74 . 83 . 84 ) are arranged. Device according to claim 2, 11, characterized in that both single-stage displacement machines ( 41 - 43 ) and individual stages ( 75 - 77 ) 75 - 78 ) 76 - 77 ) 76 - 78 ) multi-stage positive displacement machines ( 70 . 80 ) via connecting lines with a hydraulic control device ( 52 . 53 ) are connected, which has a switching system such that the individual displacement machine stages act as a hydraulic pump or as a hydraulic motor, are used individually or acting in groups, can be operated without pressure in circles promotional. Device according to claim 2, 11 and 12, characterized in that inside the driven impeller ( 82 ) a the speed of the wear shaft ( 7 . 9 . 79 ) fast translating planetary gear (( 86 / 87 / 88 / 89 ) is housed. Device according to claim 2, 11, 12 and 14, characterized in that the pump housing ( 80 ) as a bearing base of the centrally disposed annularly shaped, driven impeller ( 82 ) an annular housing web ( 81 ), the impeller ( 82 ) over a carrier web ( 85 ) with a centrally mounted on the output shaft inner sun gear (( 86 ) which is rotatably connected with which on a shaft fixed web ( 88 ) mounted planetary gears ( 87 ) is engaged, which in turn acting in a housing acting as an outer sun gear inner teeth ( 89 ) roll over in a form-fitting manner. Device according to claim 2 and 11 to 15, characterized in that the driven impeller ( 82 ) via a clutch ( 91 ) with the output shaft ( 7 . 9 . 79 ) is in rotary connection, wherein the planet carrier ( 90 ) at a base of the clutch, the other base with the shaft ( 7 . 8th . 79 ) is seated, the clutch ( 91 ) constructively in the pump housing ( 80 ) is integrated. Device according to claim 2 and 13, characterized in that the hydraulic control and switching element ( 52 . 53 ) consists of a multi-channel spool, its control edges are designed so that a path-dependent (analog) flow and pressure regulation is effected, control edges of the type known "multi-way valves without fixed switching position" are designed so that inflowing streams of a control channel (eg , 52 _g ) in a certain control piston position into two streams ( 52g ) and ( 52 _h ) is shared. Device according to claim 2, 13 and 17, characterized in that the hydraulic switching element ( 52 . 53 ) has an integrated in its housing suction and return channel ( 56 ) and a pressure channel ( 57 ), the suction and return channel ( 56 ) via a check valve ( 63 ) with a suction line ( 68 ), the pressure channel ( 57 ) to the suction channel ( 56 ) to lead the pressure relief valve ( 67 ) having.