IT202100012764A1

IT202100012764A1 - AUTOMATIC CONTINUOUSLY VARIABLE RATIO GEARBOX FOR TWO-WHEEL VEHICLES

Info

Publication number: IT202100012764A1
Application number: IT102021000012764A
Authority: IT
Inventors: Stefano Revel
Original assignee: Stefano Revel
Priority date: 2021-05-18
Filing date: 2021-05-18
Publication date: 2022-11-18

Description

DESCRIZIONE a corredo della domanda di brevetto per invenzione industriale dal titolo: CAMBIO A VARIAZIONE CONTINUA AUTOMATICA DEL RAPPORTO PER VEICOLI A DUE RUOTE DESCRIPTION accompanying the patent application for an industrial invention entitled: GEARBOX WITH AUTOMATIC CONTINUOUS RATIO VARIATION FOR TWO-WHEEL VEHICLES

DESCRIZIONE DESCRIPTION

La presente invenzione riguarda uno schema di trasmissione per veicoli a due ruote (biciclette, ciclomotori ecc.) che consente di variare il rapporto di rotazione tra i pedali o il motore e la ruota motrice in modo continuo in funzione della velocit? angolare di quest?ultima senza alcun intervento manuale, a vantaggio del confort dell?utilizzatore e della versatilit? d?uso del mezzo. The present invention relates to a transmission scheme for two-wheeled vehicles (bicycles, mopeds, etc.) which allows the rotation ratio between the pedals or the engine and the driving wheel to be varied continuously as a function of the speed. angle of the latter without any manual intervention, to the advantage of the comfort of the user and the versatility of use of the vehicle.

Nell?ambito delle soluzioni per ottenere la variazione del rapporto di trasmissione dei veicoli a due ruote al di fuori dei tradizionali schemi a deragliatore numerosi dispositivi di diverse tipologie sono stati oggetto di brevetto. Da una ricerca svolta a tutto il 9 dicembre 2020 (l?elenco completo dei documenti esaminati ? riportato in fondo alla presente descrizione) le scelte tecniche maggiormente utilizzate sono riepilogabili come segue: In the context of solutions for obtaining the variation of the transmission ratio of two-wheeled vehicles outside the traditional derailleur schemes, numerous devices of different types have been patented. From a research carried out up to 9 December 2020 (the complete list of documents examined is shown at the bottom of this description) the most used technical choices can be summarized as follows:

? variazione delle dimensioni radiali della moltiplica e/o del pignone ? ottenuta tramite leveraggi o camme rotanti, con interventi manuali o servomeccanismi; ? change in the radial dimensions of the multiplier and/or pinion ? obtained through levers or rotating cams, with manual interventions or servomechanisms;

? coppie di coni e controconi con cinghia di trasmissione trapezoidale ? tecnica analoga al CVT utilizzato in vari modelli ciclomotoristici ed automobilistici; ? pairs of cones and counter-cones with trapezoidal drive belt ? technique similar to the CVT used in various moped and car models;

? rotismi epicicloidali con accorgimenti vari ? ad esempio CN204942419U sfrutta ingranaggi planetari conici; ? epicycloidal gears with various tricks ? for example CN204942419U uses bevel planetary gears;

? meccanismi a frizione ? ad esempio DE102012023551, bench? concepito per l?utilizzo congiunto ad un motore di supporto alla pedalata; ? friction mechanisms? for example DE102012023551, although? designed for use in conjunction with a pedaling support motor;

? superfici di attrito a contatto di sfere ad asse inclinabile ? la recente soluzione di Fallbrook (US2016201772) realizza un cambio a variazione continua con questo schema, mentre Shimano (JP5795400B1) utilizza un circuito idraulico allo scopo; ? friction surfaces in contact with tilting axis balls ? the recent solution by Fallbrook (US2016201772) realizes a continuously variable gearbox with this scheme, while Shimano (JP5795400B1) uses a hydraulic circuit for the purpose;

? meccanismi idraulici ? in WO9504890A1 una pompa idraulica ed un motore sono accoppiati ad un differenziale meccanico, mentre in WO8905754A1 lo schema ? completamente idraulico ma la variazione del rapporto avviene con intervento esterno. Considerato quanto sopra esposto la presente invenzione si propone quale soluzione innovativa, presentando contestualmente le caratteristiche di totale automatismo, ottenendo l?allungamento o l?accorciamento del rapporto senza interventi da parte del conduttore, di compattezza e leggerezza, essendo composto da un numero limitato di elementi, e di relativa semplicit? costruttiva e manutentiva con il vantaggio quindi di costi contenuti. ? hydraulic mechanisms ? in WO9504890A1 a hydraulic pump and a motor are coupled to a mechanical differential, while in WO8905754A1 the diagram ? completely hydraulic but the variation of the ratio takes place with external intervention. Considering the foregoing, the present invention is proposed as an innovative solution, presenting at the same time the characteristics of total automation, obtaining the lengthening or shortening of the ratio without interventions by the driver, compactness and lightness, being composed of a limited number of elements , and of relative simplicity? construction and maintenance with the advantage of low costs.

Per conseguire tale scopo la trasmissione ? concepita in modo innovativo con una serie di caratteristiche e vantaggi che risulteranno dalla descrizione seguente, fatta a titolo esemplificativo, ma non limitativo, con riferimento agli annessi disegni, in cui: To achieve this purpose, the transmission ? conceived in an innovative way with a series of characteristics and advantages which will result from the following description, given by way of example, but not in limitation, with reference to the annexed drawings, in which:

? la fig. 1 rappresenta in sezione il complessivo della trasmissione con i principali componenti; ? the fig. 1 is a sectional view of the transmission assembly with the main components;

? la fig. 2 contiene l?esploso del medesimo complessivo per una pi? chiara rappresentazione; ? the fig. 2 contains the exploded view of the same assembly for a pi? clear representation;

? la fig.3 rappresenta gli elementi che agiscono sulla posizione dello statore scorrevole nella posizione relativa a velocit? angolare nulla o ridotta della ruota; ? fig.3 represents the elements that act on the position of the sliding stator in the position relative to speed? zero or reduced angle of the wheel;

? la fig. 4 riporta la sezione dello statore scorrevole nel corpo pompa nella posizione corrispondente a quella degli elementi di cui alla fig.3; ? the fig. 4 shows the section of the stator sliding in the pump body in the position corresponding to that of the elements in fig.3;

? le fig.5 e 6 rappresentano rispettivamente gli stessi elementi di cui alle fig.3 e 4, nelle posizioni assunte con una elevata velocit? di rotazione della ruota, con un effetto che sar? meglio illustrato pi? oltre nella presente descrizione; ? fig.5 and 6 respectively represent the same elements as in fig.3 and 4, in the positions assumed with a high speed? of rotation of the wheel, with an effect that sar? better illustrated pi? further in this description;

? le fig. 7 ed 8 raffigurano in vista di tre quarti lo schema di azionamento dello statore scorrevole per mezzo del movimento assiale delle guide, mosse dagli elementi visibili nei disegni delle fig. da 3 a 6, nelle diverse condizioni di velocit? angolare della ruota; ? figs. 7 and 8 show a three-quarter view of the actuation scheme of the sliding stator by means of the axial movement of the guides, moved by the elements visible in the drawings of figs. from 3 to 6, in the different conditions of speed? wheel angular;

? la fig. 9 raffigura una possibile variante costruttiva nella quale la soluzione dello statore scorrevole ? applicata alla turbina che trasmette il moto alla ruota anzich? al gruppo di pompaggio che riceve il moto dagli elementi della trasmissione. ? the fig. 9 shows a possible constructive variant in which the solution of the sliding stator ? applied to the turbine that transmits the motion to the wheel instead? to the pumping unit which receives the motion from the transmission elements.

? la fig. 10 rappresenta una possibile soluzione alternativa per ottenere la variazione della portata volumetrica del gruppo di pompaggio senza ricorrere allo statore scorrevole, per mezzo di elementi basculanti posizionati da una superficie guida con la quale entrano in interferenza meccanica; ? the fig. 10 represents a possible alternative solution for obtaining the variation of the volumetric flow rate of the pumping group without resorting to the sliding stator, by means of tilting elements positioned by a guide surface with which they enter into mechanical interference;

Con riferimento ai disegni, con 1 ? indicato il perno centrale di sostegno, con 2 il porta mozzo che sostiene il semi mozzo 4 con l?interposizione del cuscinetto a sfere 3, con 17, 18 e 19 i corrispondenti elementi dal lato opposto, detti semi mozzi 4 e 19 uniti dal tubo inter mozzi 5 che sostiene una serie di leve 13 le quali, tramite l?ingranaggio 15, muovono assialmente le astine 12, le quali agiscono sul disco 11 solidale con le guide 10, che a loro volta generano il movimento trasversale dello statore 9 che ha sede nel corpo pompa 8, dette leve 13 tenute in posizione dalle molle 14. Detto corpo pompa 8 da un lato funge da sede per il rotore 20, che supporta le palette mobili 21, e dall?altro lato per la turbina 23 che supporta le palette mobili 22, formando con detti elementi un circuito idraulico. Detti elementi 8, 9, 21, 22 e, parzialmente, 10, 20 e 23 risiedono all?interno del corpo contenitore 7, solidale al telaio del veicolo tramite detto porta mozzo 17, detto corpo 7 chiuso dal tappo 6 e riempito di fluido di adeguata viscosit?. Detto rotore 20 prende il moto dalla corona 16 e pompa il fluido verso detta turbina 23 che trasmette il moto rotatorio, tramite il dispositivo di ruota libera 24 e 25, al semi mozzo 4, solidale al semi mozzo 19 tramite detto tubo inter mozzi 5. With reference to the drawings, with 1 ? indicated the central support pin, with 2 the hub carrier which supports the half hub 4 with the interposition of the ball bearing 3, with 17, 18 and 19 the corresponding elements on the opposite side, called half hubs 4 and 19 joined by the tube inter hubs 5 which supports a series of levers 13 which, by means of the gear 15, axially move the rods 12, which act on the disk 11 integral with the guides 10, which in turn generate the transversal movement of the stator 9 which has seat in the pump body 8, said levers 13 held in position by the springs 14. Said pump body 8 on one side acts as a seat for the rotor 20, which supports the mobile blades 21, and on the other side for the turbine 23 which supports the movable vanes 22, forming a hydraulic circuit with said elements. Said elements 8, 9, 21, 22 and, partially, 10, 20 and 23 reside inside the container body 7, integral with the vehicle chassis through said hub holder 17, said body 7 closed by cap 6 and filled with adequate viscosity. Said rotor 20 takes motion from the crown 16 and pumps the fluid towards said turbine 23 which transmits the rotary motion, via the free wheel device 24 and 25, to the half hub 4, integral with the half hub 19 through said inter hub tube 5.

Come illustrato in fig.3, 4 e 7, in condizioni di velocit? angolare della ruota nulla o ridotta le guide 10 posizionano lo statore 9 in posizione tale che ad ogni giro della corona 16 il volume di fluido pompato verso la turbina 23 sia minimo, generando quindi una frequenza di rotazione limitata di detta turbina 23 e sviluppando pertanto un rapporto di trasmissione corto. As illustrated in fig.3, 4 and 7, in conditions of speed? angular angle of the wheel null or reduced the guides 10 position the stator 9 in such a position that at each revolution of the crown 16 the volume of fluid pumped towards the turbine 23 is minimal, thus generating a limited rotation frequency of said turbine 23 and therefore developing a short gear ratio.

Come rappresentato nelle fig. 5, 6 e 8, a velocit? di rotazione elevate la forza centrifuga sviluppata fa s? che le leve 13 vincano la resistenza delle molle 14 fino a porsi in posizione radiale rispetto al mozzo ruota, ed agendo sui componenti collegati 15, 12, 11 e 10 generino la traslazione trasversale dello statore 9 rispetto al corpo pompa 8. In dette condizioni, la portata unitaria di fluido per ogni giro della corona 16 del gruppo pompa 20, 21, 8 e 9 verso la turbina 23 e 22 ? massima, pertanto la frequenza di rotazione di detta turbina a parit? di rotazione della corona 16 sar? quella pi? elevata, ottenendo il rapporto di trasmissione pi? lungo. As represented in FIGS. 5, 6 and 8, at speed? high rotation centrifugal force developed ago s? that the levers 13 overcome the resistance of the springs 14 until they are placed in a radial position with respect to the wheel hub, and by acting on the connected components 15, 12, 11 and 10 they generate the transversal translation of the stator 9 with respect to the pump body 8. In these conditions, the unit flow rate of fluid for each revolution of the crown 16 of the pump group 20, 21, 8 and 9 towards the turbine 23 and 22 ? maximum, therefore, the rotation frequency of said turbine on equal terms? of rotation of the crown 16 sar? the most high, obtaining the transmission ratio pi? long.

Poich? alle velocit? intermedie la posizione di dette leve 13 risulter? dal punto di equilibrio fra la forza centrifuga, funzione della velocit? di rotazione, e la forza delle molle 14 che tendono a riportare dette leve 13 verso la posizione di cui alle fig.3 e 7, corrispondentemente lo statore 9 potr? assumere tutte le posizioni intermedie fra le due estreme, pertanto il rapporto di trasmissione sar? continuamente, progressivamente ed automaticamente adeguato alla velocit? del veicolo, con rapporti corti a bassa velocit? e via via pi? lunghi all?incremento della stessa, per riaccorciarsi in caso di decremento (ad es. frenate o salite). because at speeds the position of said levers 13 will be intermediate? from the point of equilibrium between the centrifugal force, function of the speed? of rotation, and the force of the springs 14 which tend to return said levers 13 towards the position shown in figs. 3 and 7, correspondingly the stator 9 will be able? take all the intermediate positions between the two extremes, therefore the transmission ratio sar? continuously, progressively and automatically adapted to the speed? of the vehicle, with short ratios at low speed? and gradually more long as it increases, to become shorter again in the event of a decrease (e.g. braking or climbing).

La fig.9 rappresenta una variante costruttiva che ottiene il medesimo effetto sopra descritto con l?applicazione della soluzione dello statore scorrevole al gruppo turbina anzich? a quello pompante. In questo caso, il rotore 30 con le palette 22 prendono il moto dalla corona 16 e ruotano entro uno statore fisso, mentre il gruppo turbina 8, 9, 21 e 29 varia la sua frequenza di rotazione per ciascun giro della corona 16 in funzione della posizione dello statore 9, azionato dalle guide 10 mosse dagli elementi 11, 28, 15 e 13 con le stesse modalit? sopra descritte. Gli altri elementi sono analoghi alla versione di cui alla Fig.1 con la differenza che il tappo 26 ? solidale al porta mozzo 17 e sostiene il corpo contenitore 27. Ovviamente ? anche possibile abbinare le due soluzioni applicando uno statore scorrevole sia al gruppo pompante che a quello turbina e configurando le guide in modo che possano agire contemporaneamente su entrambi gli statori. Fig. 9 represents a constructive variant which obtains the same effect described above with the application of the solution of the sliding stator to the turbine group instead of to the pumping one. In this case, the rotor 30 with the blades 22 take their motion from the crown 16 and rotate within a fixed stator, while the turbine unit 8, 9, 21 and 29 varies its rotation frequency for each revolution of the crown 16 according to the position of the stator 9, operated by the guides 10 moved by the elements 11, 28, 15 and 13 with the same modalities? described above. The other elements are similar to the version shown in Fig.1 with the difference that the plug 26 ? integral with the hub holder 17 and supports the container body 27. Obviously ? It is also possible to combine the two solutions by applying a sliding stator to both the pumping unit and the turbine unit and configuring the guides so that they can act simultaneously on both stators.

La fig. 10 raffigura una possibile alternativa alla soluzione dello statore scorrevole per ottenere la variazione della portata volumetrica della pompa o della turbina. Come rappresentato nel disegno, il rotore 31 ? configurato in modo da fungere da sede per una serie di componenti basculanti 33, configurati in modo che a seconda della propria posizione possano occupare pi? o meno spazio nelle camere fra le palette, con l?effetto di variare la quantit? di fluido contenuta entro dette camere nella fase di pompaggio. La posizione di detti componenti basculanti 33 ? determinata ad ogni giro dall?interferenza meccanica con la guida 32, che si muove assialmente secondo lo schema di azionamento descritto in precedenza fino al disco 11. A seconda della posizione di detta guida 32, i componenti 33 si posizioneranno a loro volta in modo da occupare pi? o meno spazio nelle camere di pompaggio con l?effetto di variare, in funzione della velocit? della ruota, la portata di detta pompa o turbina. fig. 10 shows a possible alternative to the solution of the sliding stator to obtain the variation of the volumetric flow rate of the pump or turbine. As shown in the drawing, rotor 31 is configured so as to act as a seat for a series of tilting components 33, configured so that depending on their position they can occupy more? or less space in the chambers between the pallets, with the effect of varying the quantity? of fluid contained within said chambers in the pumping phase. The position of said tilting components 33 ? determined at each turn by the mechanical interference with the guide 32, which moves axially according to the actuation scheme previously described up to the disc 11. Depending on the position of said guide 32, the components 33 will in turn position themselves so as to occupy more or less space in the pumping chambers with the effect of varying, according to the speed? of the wheel, the flow rate of said pump or turbine.

Lo schema innovativo proposto consente quindi di realizzare una trasmissione che adegua in modo automatico, progressivo e continuo il rapporto fra giri dei pedali o del motore e giri della ruota del veicolo in funzione della velocit? del veicolo medesimo, incrementandolo o riducendolo in maniera proporzionale alla velocit? stessa, senza alcun intervento manuale del conducente, con evidenti vantaggi nell?utilizzo. The proposed innovative scheme therefore makes it possible to create a transmission which automatically, progressively and continuously adjusts the ratio between the revolutions of the pedals or of the engine and the revolutions of the wheel of the vehicle according to the speed? of the vehicle itself, increasing it or reducing it proportionally to the speed? itself, without any manual intervention by the driver, with clear advantages in use.

Come anticipato in premessa, si elencano di seguito i brevetti pi? significativi fra i circa 700 attinenti l?argomento esaminati: As anticipated in the introduction, the most common patents are listed below. significant among the approximately 700 related to the topic examined:

? variazione delle dimensioni radiali della moltiplica e/o del pignone ? DE19600584A1, ? change in the radial dimensions of the multiplier and/or pinion ? DE19600584A1,

DE19735001A1, DE202004010309U1, GB191512398A, JPS5422635A, DE19735001A1, DE202004010309U1, GB191512398A, JPS5422635A,

KR20160026369A, NL1008944C2, US4030373A, US2010203990A1, WO03078240A1, KR20160026369A, NL1008944C2, US4030373A, US2010203990A1, WO03078240A1,

? coppie di coni e controconi con cinghia di trasmissione trapezoidale ? US3625079A, ? pairs of cones and counter-cones with trapezoidal drive belt ? US3625079A,

CN204802013U, NL1039763A, TW201350382A, TWM394950U, US3926020A, CN204802013U, NL1039763A, TW201350382A, TWM394950U, US3926020A,

? rotismi epicicloidali con accorgimenti vari ? CN202080416U, CN204942419U, ? epicycloidal gears with various tricks ? CN202080416U, CN204942419U,

CN204572956U, EP2762397A1, GB910585A, HU0202995A2, JPH02164685A, CN204572956U, EP2762397A1, GB910585A, HU0202995A2, JPH02164685A,

JPS5490739A, US3944253A, US2008207379A1, WO2016083080A1, ; JPS5490739A, US3944253A, US2008207379A1, WO2016083080A1, ;

? meccanismi a frizione ? DE102012023551, GB485900A, TWI274699B; ? friction mechanisms? DE102012023551, GB485900A, TWI274699B;

? superfici di attrito a contatto di sfere ad asse inclinabile ? US2016201772, JP5795400B1, EP0528382A1, JP2008232164A, US2016040763A1; ? friction surfaces in contact with tilting axis balls ? US2016201772, JP5795400B1, EP0528382A1, JP2008232164A, US2016040763A1;

? meccanismi idraulici ? DE3141676A1, DE19744608A1, DE102012021554A1, ? hydraulic mechanisms ? DE3141676A1, DE19744608A1, DE102012021554A1,

EP0425720A1, FR939917A, GB2530044A, US4684143A, US5423560A, EP0425720A1, FR939917A, GB2530044A, US4684143A, US5423560A,

US2004118243A1, WO8905754A1, WO9504890A1; US2004118243A1, WO8905754A1, WO9504890A1;

? vari - BG108804A, EP0392807A2, CN204937401U, GB2530044A, GEP20156385B, ? various - BG108804A, EP0392807A2, CN204937401U, GB2530044A, GEP20156385B,

JPS5438042A, US4133550A, US5771754A, US5971877A, KR100966120B1, JPS5438042A, US4133550A, US5771754A, US5971877A, KR100966120B1,

KR101222422B1, KR20110112562A, KR20150052754A, WO2010081440A1, KR101222422B1, KR20110112562A, KR20150052754A, WO2010081440A1,

CN87216835U, CN2088971U, CN87213977U, WO2010081440A1ta, CN201367091Y. CN87216835U, CN2088971U, CN87213977U, WO2010081440A1ta, CN201367091Y.

Claims

1. Gearbox with automatic continuous variation of the ratio for two-wheeled vehicles, composed of a container body (7) closed by a cap (6) and filled with fluid, said container body (7) integral with the vehicle frame, directly or through intermediate elements (17), said container body (7) partially or totally containing at least one pump rotor (20) with mobile blades (21) which receives the motion from a transmission element (16) of said vehicle, a pump body (8 ) integral with said container body (7), a mobile stator (9) supported by said pump body (8), a turbine rotor (23) with mobile blades (22) which transmits motion to the wheel of said vehicle and ? supported by said pump body (8) and at least one guide (10) supported by said container body (7), connected to said stator (9) and integral with an external disk (11), also composed of at least one elastic element (14 ), by an inter-hub tube (5) integral with the half wheel hubs (4 and 19), by at least one lever (13) supported by said inter-hub tube (5) and by at least one control rod (12) supported by said interhub tube (5) and connected to said disc (11).

2. Automatic continuously variable gearbox for two-wheeled vehicles, according to claim 1, wherein said elements pump rotor (20) with vanes (21), movable stator (9), pump casing (8), turbine rotor ( 23) with vanes (22) contained within said container body (7) form a hydraulic circuit.

3. Automatic continuously variable gearbox for two-wheeled vehicles, according to claim 1, wherein said or said rods (12) are supported by said interhub tube (5) so as to be slidable along an axis parallel to that of said wheel hub and are coupled to said lever(s) (13) directly with toothed profiles if said levers (13) are pivoted on an axis perpendicular to that of rotation of said wheel hub.

4. Gearbox with automatic continuous variation of the ratio for two-wheeled vehicles, according to claim 1, wherein said or said rods (12) are supported by said interhub tube (5) so as to be slidable along an axis parallel to that of said hub rotates and are coupled to said lever(s) (13) by means of a gear (15) supported by said inter-hub tube (5) which meshes externally with said lever (13) and internally with a threaded section of said rod (12) if said levers (13) are pivoted on an axis parallel to that of rotation of said wheel hub.

5. Automatic continuously variable gearbox for two-wheeled vehicles, according to the preceding claims, wherein said guide(s) (10) are mechanically coupled with said stator (9) so that with respect to the axis of rotation of said wheel the axial movement of said guides (10), actuated by said or said rods (12) via said disc (11) corresponds to a transversal movement of said stator (9).

6. Transmission with automatic continuous variation of the ratio for two-wheeled vehicles, according to claims 1, 3, 4 and 5 in which said elastic element (14) acts directly on at least one of the mechanically connected elements (13, 15, 12, 11 , 10) to said stator (9) or on said stator (9).

7. Gearbox with automatic continuous variation of the ratio for two-wheeled vehicles, according to the preceding claims, characterized in that, as a constructive variation, said mobile stator (9) can? be positioned alternatively on the side of said pump rotor (20) or on the side of said turbine rotor (29).

8. Transmission with automatic continuous variation of the ratio for two-wheeled vehicles, according to the preceding claims, characterized in that, as a constructive variant, said mobile stators (9) can be used both for the side of said pump rotor (20) and for the side of said turbine rotor (29), configuring said guides (10) so as to drive both said stators (9).

9. Automatic continuously variable gearbox for two-wheeled vehicles, according to claim 1, wherein said turbine rotor (23) transmits motion to said wheel through a freewheel device (24 and 25).

10. Transmission with automatic continuous variation of the ratio for two-wheeled vehicles, according to claims from 1 to 7, characterized in that said mobile stator (9) can, as a constructive variant, be replaced by a fixed stator and a rotor ( 31) adapted to act as a seat for a series of tilting mobile elements (33) which are positioned at each turn by mechanical interference with a guide (32) integral with said disc (11).