SI22917A - Hydrodynamic torque transducer - Google Patents
Hydrodynamic torque transducer Download PDFInfo
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- SI22917A SI22917A SI200800292A SI200800292A SI22917A SI 22917 A SI22917 A SI 22917A SI 200800292 A SI200800292 A SI 200800292A SI 200800292 A SI200800292 A SI 200800292A SI 22917 A SI22917 A SI 22917A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/04—Combined pump-turbine units
Abstract
Description
ENVITA d.o.o.ENVITA d.o.o.
MPK8: F 16 H 41/04 F 16 D 33/04MPK 8 : F 16 H 41/04 F 16 D 33/04
Hidrodinamični pretvornik vrtilnega momentaHydrodynamic torque converter
Izum v okviru strojništva spada k strojnim elementom in ukrepom za omogočanje in vzdrževanje učinkovitega delovanja naprav ali postrojenj, in sicer bodisi k rotacijskim fluidnim prenosnikom hidrokinetične vrste, pri katerih je predvidena kombinacija črpalne in turbinske enote, ali pa k hidravličnim sklopkam hidrokinetične vrste za prenos vrtilnega gibanja in pri katerih se krmiljenje vrši na osnovi spreminjanja položaja lopatic.The invention in the field of mechanical engineering belongs to the mechanical elements and measures for enabling and maintaining the effective operation of devices or plants, either for rotary fluid transmitters of the hydro-kinetic type, in which a combination of pump and turbine units is envisaged, or for hydraulic couplings of the hydro-kinetic type for transmitting rotary movements in which the steering is performed on the basis of changing the position of the blades.
Pri tem je izum osnovan na problemu, kako zasnovati hidrodinamični pretvornik vrtilnega momenta, pri katerem bodo v primerjavi z doslej znanimi tovrstnimi napravami hidravlične izgube manjše in bo zatorej posledično izkoristek lahko višji, področje obratovanja pri visokem izkoristku širše, obenem pa bo tudi karakteristika vrtilnega momenta na turbinski strani ugodnejša.The invention is based on the problem of how to design a hydrodynamic torque converter which, in comparison with the prior art devices of this kind, will reduce hydraulic losses and therefore the efficiency can be higher, the area of operation at high efficiency will be wider and at the same time the characteristic of torque will be wider. on the turbine side more favorable.
Predmet izuma je hidrodinamični pretvornik vrtilnega momenta, ki omogoča doseganje maksimalnega izkoristka v območju vrednosti razmerja vrtljajev 1 < n-p/tip < 4, pri čemer np predstavlja vrtilno hitrost črpalnega rotorja na pogonski gredi, tip pa predstavlja vrtilno hitrost turbinskega rotorja na odgonski gredi, in temu ustrezno v primerjavi z obstoječimi napravami omogoča doseganje znatnih obratovalnih in konstrukcijskih prednosti.The subject of the invention is a hydrodynamic torque converter that enables maximum efficiency in the range of values of the speed ratio 1 <np / type <4, where np represents the rotational speed of the pump rotor on the drive shaft and the type represents the rotational speed of the turbine rotor on the output shaft, and accordingly, it offers significant operational and structural advantages when compared to existing installations.
Hidrodinamični pretvornik vrtilnega momenta se uporablja za prenašanje moči s pogonskega stroja, zlasti npr. z elektromotorja, s parne ali plinske turbine ali tudi z motorja z notranjim zgorevanjem na delovni stroj. V primeru, da imata pogonski in delovni stroj različni karakteristiki momentov v odvisnosti od vrtilne hitrosti, je potrebno med pogonski in delovni stroj vgraditi menjalnik, ki v idealnem primeru pri konstantni moči pretvarja moment in vrtilno hitrost. Hidrodinamični pretvornik momenta torej v osnovi predstavlja menjalnik, za katerega velja, da nima konstantnega prestavnega razmerja, ampak se le-to spreminja brezstopenjsko in samodejno v odvisnosti od momenta na odgonski strani. Pomembno prednost hidrodinamičnega pretvornika momenta predstavlja tudi dušenje vibracij in torzijskih sunkov, ki se prenašajo med pogonskim in delovnim strojem. Preprosti hidrodinamični pretvornik momenta vključuje črpalni in turbinski rotor, sklop vodilnih lopatic in toroidno ohišje. Črpalni rotor se vrti skupaj s pogonsko gredjo in oddaja energijo delovnemu mediju. Delovni medij visoke specifične energije po izstopu iz črpalnega rotorja potuje do turbinskega rotorja, ki je vezan na odgonsko gred in kjer se visoka specifična energija delovnega medija pretvori v mehansko delo. Po izstopu iz turbinskega rotorja delovni medij potuje skozi sklop vodilnih lopatic nazaj do vstopa v črpalni rotor. Delovni medij za prenos moči je običajno mineralno olje z nizko stopnjo viskoznosti. Tovrstni pretvorniki so v stanju tehnike sicer znani, stanje tehnike pa bo tako v pogledu splošno znane oz. konvencionalne izvedbe kot tudi v pogledu konkretne rešitve po US 7,155,904 podrobneje analizirano v nadaljevanju skupaj z opisom primerov izvedbe pričujočega izuma.A hydrodynamic torque converter is used to transfer power from a drive machine, especially e.g. from an electric motor, from a steam or gas turbine, or also from an internal combustion engine to a working machine. If the drive and the running machine have different torque characteristics depending on the speed, a gearbox must be installed between the drive and the running machine, ideally converting torque and speed at constant power. The hydrodynamic torque converter is therefore basically a gearbox that is considered to have no constant gear ratio, but which changes continuously and automatically depending on the torque on the output side. An important advantage of the hydrodynamic torque converter is the damping of vibrations and torsional shocks transmitted between the drive and the machine. The simple hydrodynamic torque converter includes a pump and turbine rotor, a guide vanes assembly and a toroidal housing. The pump rotor rotates with the drive shaft and transmits energy to the working medium. After leaving the pump rotor, the high specific energy medium travels to the turbine rotor, which is connected to the output shaft and where the high specific energy of the working medium is converted into mechanical work. After exiting the turbine rotor, the working medium travels through the set of guide vanes back to the inlet of the pump rotor. Power transmission medium is usually a low viscosity mineral oil. Such converters are known in the prior art, but the prior art will thus be generally known in the art. conventional embodiments as well as in terms of a particular solution of US 7,155,904 are analyzed in more detail below with a description of embodiments of the present invention.
Pričujoči izum se nanaša na hidrodinamični pretvornik vrtilnega momenta, ki v splošnem obsega toroidno ohišje, v katerem je okoli geometrijske osi vrtljivo uležiščena pogonska gred z na sebi nameščenim Črpalnim rotorjem s končnim številom osno-simetrično razporejenih lopatic in okoli taiste osi vrtljiva odgonska gred z na sebi nameščenim turbinskim rotorjem s končnim številom osno-simetrično razporejenih lopatic. Pri tem je omenjeni turbinski rotor gnan s pomočjo v omenjenem ohišju prisotnega in zahvaljujoč vrtenju omenjenega črpalnega rotorja okoli osi v izbrani smeri pretakajočega se delovnega medija, tako da delovni medij iz črpalnega rotorja izstopa na njegovem izstopnem premeru in vstopa v turbinski rotor na njegovem vstopnem premeru. Pri tem sta nadalje za usmerjanje oz. preusmerjanje toka omenjenega delovnega medija v notranjosti ohišja predvidena sklop fiksnih vodilnih lopatic in sklop regulacijskih vodilnih lopatic, položaj slednjih pa je vsakokrat po izbiri nastavljiv s pomočjo ustreznega regulacijskega mehanizma.The present invention relates to a hydrodynamic torque converter, generally comprising a toroidal housing, in which a drive shaft with a self-mounted pump rotor with a finite number of axially symmetrically arranged blades and a rotating driven rotational axis is rotatably arranged about the geometric axis. self-mounted turbine rotors with finely-axially symmetrically arranged blades. Said turbine rotor is driven by means of said housing being present and thanks to rotation of said pump rotor about an axis in the selected direction of the flowing working medium so that the working medium exits the pump rotor at its outlet diameter and enters the turbine rotor at its inlet diameter . In doing so, they are further directed or directed. the flow diversion of said working medium inside the housing is provided with a set of fixed guide vanes and a set of control guide vanes and the position of the latter is optionally adjustable each time by means of a suitable control mechanism.
Po izumu je predlagano, da sta črpalni rotor in turbinski rotor pretvornika vrtilnega momenta tako zasnovana, da je vstopni premer turbinskega rotorja manjši od izstopnega premera črpalnega rotorja in da črpalni rotor omogoča črpanje delovnega medija v smeri radialno navznoter proti rotacijski osi.According to the invention, it is proposed that the pump rotor and the torque converter of the torque converter be so designed that the inlet diameter of the turbine rotor is smaller than the outlet diameter of the pump rotor and that the pump rotor allows the working medium to be pumped radially inwards towards the rotary axis.
Sklopa regulacijskih vodilnih lopatic in fiksnih vodilnih lopatic sta razporejena v neposredni bližini črpalnega rotorja. Pri tem je prednostno - gledano v smeri pretoka delovnega medija sklop regulacijskih vodilnih lopatic razporejen neposredno pred črpalnim rotorjem, sklop fiksnih vodilnih lopatic pa neposredno za črpalnim rotorjem in pred turbinskim rotorjem.The sets of control guide vanes and fixed guide vanes are arranged in close proximity to the pump rotor. Preferably, in the direction of the flow of the working medium, the set of control guide vanes is arranged directly in front of the pump rotor and the set of fixed guide vanes directly behind the pump rotor and in front of the turbine rotor.
Pri tem je sklop regulacijskih vodilnih lopatic v ohišju razporejen na premeru, ki je večji od vstopnega premera črpalnega rotorja in obenem tudi večji od vstopnega premera turbinskega rotorja. Po drugi strani je sklop fiksnih vodilnih lopatic v ohišju razporejen na premeru, ki je večji od vstopnega premera turbinskega rotorja in prednostno manjši od izstopnega premera črpalnega rotorja.In this case, the set of control guide vanes in the housing is arranged at a diameter larger than the inlet diameter of the pump rotor and at the same time larger than the inlet diameter of the turbine rotor. On the other hand, the assembly of fixed guide vanes in the housing is arranged in a diameter larger than the inlet diameter of the turbine rotor and preferably smaller than the outlet diameter of the pump rotor.
Pri eni od različic izuma je turbinski rotor tako zasnovan, da v ohišju razpoložljiv in od črpalnega rotorja dotekajoč delovni medij v turbinski rotor vstopa in izstopa v radialni smeri, namreč vsaj približno v smeri radialno navznoter proti osi vrtenja turbinskega rotorja.In one embodiment of the invention, the turbine rotor is designed in such a way that the working medium accessible and pumped into the turbine rotor by the inlet and outlet enters and exits in a radial direction, at least approximately radially inwards towards the axis of rotation of the turbine rotor.
Pri nadaljnji različici pretvornika vrtilnega momenta po izumu je turbinski rotor tako zasnovan, da v ohišju razpoložljiv in od črpalnega rotorja dotekajoč delovni medij v turbinski rotor vstopa v radialni smeri, namreč v smeri navznoter proti osi vrtenja turbinskega rotoija, iz omenjenega turbinskega rotorja pa izstopa v aksialni smeri, namreč vsaj približno v smeri osi vrtenja turbinskega rotorja.In a further embodiment of the torque converter according to the invention, the turbine rotor is designed so that the working medium accessible to and from the pump rotor enters the turbine rotor in a radial direction, namely in the inward direction towards the axis of rotation of the turbine rotor, and exits from said turbine rotor. the axial direction, at least approximately in the direction of the axis of rotation of the turbine rotor.
Pri še nadaljnji različici izuma je turbinski rotor tako zasnovan, da v ohišju razpoložljiv in od črpalnega rotorja dotekajoč delovni medij v turbinski rotor vstopa in izstopa v aksialni smeri, namreč vsaj približno v smeri osi vrtenja turbinskega rotorja.In a still further embodiment of the invention, the turbine rotor is designed such that the working medium accessible and from the pump rotor flows in and out in the axial direction to the turbine rotor, namely at least approximately in the direction of the axis of rotation of the turbine rotor.
Primer izvedbe hidrodinamičnega pretvornika momenta po izumu bo v nadaljevanju podrobneje obrazložen na osnovi priložene skice vključno s primerjalnima izvedbama, pri čemerAn example embodiment of a hydrodynamic torque converter according to the invention will now be explained in more detail on the basis of the accompanying drawing, including comparative embodiments, wherein
Sl. 1 shematično ponazarja prvo primerjalno izvedbo konvencionalnega pretvornika vrtilnega momenta;FIG. 1 schematically illustrates a first comparative embodiment of a conventional torque converter;
Sl. 2 prav tako shematično ponazarja pretvornik vrtilnega momenta iz US 7,155,904;FIG. 2 also schematically illustrates a torque converter of US 7,155,904;
Sl. 3 shematično ponazarja različico pretvornika vrtilnega momenta po izumu s turbinskim rotorjem radialne izvedbe;FIG. 3 schematically illustrates an embodiment of a torque converter of the invention with a turbine rotor of radial design;
Sl. 4 prav tako shematično ponazarja različico pretvornika vrtilnega momenta po izumu s turbinskim rotorjem radialno-aksialne izvedbe;FIG. 4 also schematically illustrates a torque converter version of the invention with a radial-axial turbine rotor;
Sl. 5 spet shematično ponazarja različico pretvornika vrtilnega momenta po izumu s turbinskim rotorjem aksialne izvedbe; medtem koFIG. 5 again schematically illustrates an embodiment of a torque converter of the invention with an axial turbine rotor; while
Sl. 6 vključuje diagrame, iz katerih so razvidne primerjave s HPM3 označenih ključnih karakteristik pretvornika vrtilnega momenta z radialnim turbinskim rotorjem po izumu z relevantnimi karakteristikami konvencionalnega pretvornika po Sl. 1, katerega karakteristike so v diagramih označene s HPM1, in pretvornika iz US 7,155,904 po Sl. 2, katerega karakteristike so v diagramih označene s HPM2.FIG. 6 includes diagrams showing comparisons of the HPM3-tagged key characteristics of a torque converter with a radial turbine rotor of the invention with the relevant characteristics of a conventional converter of FIG. 1, the characteristics of which are indicated in the diagrams by HPM1, and the inverter of US 7,155,904 according to FIG. 2, the characteristics of which are indicated in the diagrams by HPM2.
Konvencionalni hidrodinamični pretvornik momenta iz stanja tehnike, ki je shematično ponazorjen na Sl. 1, sestoji iz črpalnega rotorja 11, turbinskega rotorja 12, nepremakljivih vodilnih lopatic 13, premakljivih regulacijskih lopatic 14 in toroidnega ohišja 15. Črpalni rotor lije povezan s pogonsko gredjo 16, turbinski rotor 12 je povezan z odgonsko gredjo 17. Omenjeni gredi 16, 17 sta soosno razporejeni in potekata v osi 18 vrtenja. Smer kroženja delovnega medija je na Sl. 1 označena s puščicama 19 in 110. Črpalni rotor 11 omogoča črpanje delovnega medija skozi rotor 11 v smeri vstran od rotacijske osi 18 in hkrati povečuje specifično energijo delovnemu mediju v smeri vstran od rotacijske osi 18. V turbinskem rotorju 12, ki ima večji vstopni premer D121 od izstopnega premera d, 12 črpalnega rotorja 11 in je glede na smer toka delovnega medija nameščen radialno neposredno za črpalnim rotorjem 11, se specifična energija delovnega medija pretvarja v mehansko delo. Delovni medij se po kanalih toroidnega ohišja 15 preko kaskad fiksnih vodilnih lopatic 13 in regulacijskih lopatic 14 vrača nazaj do črpalnega rotorja 11. Premikanje oz. nastavljanje regulacijskih lopatic 14 se vrši z rotacijo aksialno postavljenih palic 111 okoli osi 112. Tovrstna konvencionalna naprava se uporablja v območju razmerja vrtljajev 0 < ητ/η,ρ < 1,2.The conventional hydrodynamic torque converter of the prior art is schematically illustrated in FIG. 1, consists of pump rotor 11, turbine rotor 12, fixed guide vanes 13, movable control blades 14 and toroidal housing 15. The pump rotor is connected to the drive shaft 16, the turbine rotor 12 is connected to the output shaft 17. Said shafts 16, 17 they are arranged coaxially and run in the axis of rotation 18. The direction of circulation of the working medium is in Figs. 1 indicated by arrows 19 and 110. The pump rotor 11 allows pumping of the working medium through the rotor 11 in the direction away from the rotary axis 18 while increasing the specific energy to the working medium in the direction away from the rotary axis 18. In the turbine rotor 12 having a larger inlet diameter D121 from the exit diameter d, 12 of the pump rotor 11 and, depending on the direction of flow of the working medium, is positioned radially directly behind the pump rotor 11, the specific energy of the working medium is converted to mechanical work. The working medium is fed back to the pump rotor 11 via the channels of the toroidal housing 15 via the cascades of fixed guide blades 13 and the control blades 14. the adjustment of the control blades 14 is accomplished by rotating the axially positioned rods 111 about the axis 112. This conventional device is used in the range of the rotation ratio 0 <ητ / η, ρ <1,2.
Glavne karakteristike, ki vključujejo moment MP na črpalni t.j. pogonski strani, moment MT na turbinski t.j. odgonski strani in izkoristek ETA hidrodinamičnega pretvornika momenta, so na Sl. 6 ponazorjene v normirani obliki in v odvisnosti od razmerja vrtljajev nj/np. Moment MP na črpalni strani je v odvisnosti od razmerja vrtljajev nj/np vsaj približno konstanten Moment MT na turbinski strani je stalno naraščajoč v smeri zmanjševanja razmerja vrtljajev nT/tip. Omenjena konvencionalna izvedba pretvornika vrtilnega momenta po Sl. 1 dosega maksimalni izkoristek v območju okoli vrednosti razmerja vrtljajev np/np = 0,6.The main features that include the MP torque on the pump ie drive side, the MT torque on the turbine ie drive side, and the efficiency of the ETA hydrodynamic torque converter are in Figs. 6 illustrated in standardized form and depending on the rpm / np ratio. The MP torque on the pump side is at least approximately constant, depending on the speed ratio nj / np, and the torque MT on the turbine side is steadily increasing in the direction of decreasing speed n T / type. Said conventional embodiment of the torque converter according to FIG. 1 achieves maximum efficiency in the range around the rp value np / np = 0.6.
Za doseganje maksimalnega izkoristka v območju vrednosti razmerja vrtljajev 1 < n-p/tip < 4 so potrebne bistvene spremembe v hidravlični konfiguraciji hidrodinamičnega pretvornika momenta v primerjavi s tisto pri doslej obravnavani konvencionalni izvedbi po Sl. 1. Tako je v US 7,155,904 predlagana osnovna hidravlična konfiguracija hidrodinamičnega pretvornika momenta, ki je shematično ponazorjena na Sl. 2 in ki omogoča doseganje maksimalnega izkoristka v območju vrednosti razmerja vrtljajev 1 < «7/np < 4. Rešitev po v US 7,155,904 vključuje črpalni rotor 21, turbinski rotor 22, nepremakljive vodilne lopatice 23 na zunanjem obodu hidrodinamičnega pretvornika momenta, nepremakljive vodilne lopatice 24 na notranjem obodu hidrodinamičnega pretvornika momenta, regulacijske lopatice 25 in toroidno ohišje 26. Črpalni rotor 21 je povezan s pogonsko gredjo 27, turbinski rotor 22 pa je povezan z odgonsko gredjo 28. Omenjeni gredi 27, 28 sta vrtljivi okoli taiste osi 29 vrtenja. Smer kroženja delovnega medija je označena s puščicama 210 in 211. Črpalni rotor 21 omogoča črpanje delovnega medija skozi rotor 21 v smeri stran od rotacijske osi 29 in hkrati povečuje specifično energijo delovnemu mediju v smeri stran od rotacijske osi 29. Delovni medij z visoko specifično energijo potuje po kanalih toroidnega ohišja 26 in preko kaskade vodilnih lopatic 23 na zunanjem obodu hidrodinamičnega pretvornika momenta do turbinskega rotorjaIn order to achieve maximum efficiency in the range of values of the speed ratio 1 <n-p / type <4, significant changes in the hydraulic configuration of the hydrodynamic torque converter are required compared to that in the conventional embodiment described in FIG. 1. Thus, in US 7,155,904, a basic hydraulic configuration of a hydrodynamic torque converter is proposed, which is schematically illustrated in FIG. 2 and allowing maximum efficiency in the range of rpm values 1 <«7 / np <4. Solution in US 7,155,904 includes pump rotor 21, turbine rotor 22, fixed guide vanes 23 at the outer circumference of the hydrodynamic torque converter, stationary guide vanes 24 at the inner circumference of the hydrodynamic torque converter, control blade 25 and toroidal housing 26. The pump rotor 21 is connected to the drive shaft 27 and the turbine rotor 22 is connected to the output shaft 28. The said shafts 27, 28 are rotatable about the same axis 29 of rotation. The direction of rotation of the working medium is indicated by arrows 210 and 211. The pump rotor 21 allows the working medium to be pumped through the rotor 21 away from the rotary axis 29 while increasing the specific energy to the working medium away from the rotary axis 29. The high specific energy working medium travels through the channels of the toroidal housing 26 and through the cascade of guide blades 23 at the outer circumference of the hydrodynamic torque converter to the turbine rotor
22. V turbinskem rotorju 22, katerega vstopni premer D221 je manjši od izstopnega premera d2i2 črpalnega rotorja 21 in je glede na smer toka delovnega medija nameščen na strani, kjer ima tok delovnega medija smer proti rotacijski osi 29, se specifična energija delovnega medija pretvarja v mehansko delo. Delovni medij se po kanalih toroidnega ohišja 26 preko kaskad nepremakljivih vodilnih lopatic 24 na notranjem obodu hidrodinamičnega pretvornika momenta in regulacijskih lopatic 25 vrača nazaj do črpalnega rotoija 21. Nastavljanje regulacijskih lopatic 25 se vrši z rotacijo radialno postavljenih palic 212 okoli osi 213.22. In the turbine rotor 22 whose inlet diameter D221 is smaller than the outlet diameter d 2 i2 of the pump rotor 21 and is positioned on the side where the flow of the work medium has a direction toward the rotary axis 29, the specific energy of the work medium translates into mechanical work. The working medium is fed back through the channels of the toroidal housing 26 through the cascades of fixed guide vanes 24 on the inner perimeter of the hydrodynamic torque converter and control blades 25 to the pump rotoi 21. Adjustment of the control blades 25 is accomplished by rotation of radially positioned rods 212 about axis 213.
Opisana hidravlična konfiguracija hidrodinamičnega pretvornika momenta sicer omogoča doseganje maksimalnega izkoristka v območju vrednosti razmerja vrtljajev 1 < nj/np < 4, a ima nekatere bistvene pomanjkljivosti, namreč:The hydraulic configuration of the hydrodynamic torque converter described above enables maximum efficiency to be obtained in the range of 1 <nj / np <4, but has some significant disadvantages, namely:
- turbinski rotor 22, katerega vstopni premer D221 je manjši od izstopnega premera črpalnega rotorja d2!2 črpalnega rotorja 21, je glede na smer toka delovnega medija nameščen na tisti strani, kjer ima tok delovnega medija smer proti rotacijski osi 29, kar ima zaradi oddaljenosti turbinskega rotorja 22 od črpalnega rotorja 21 za posledico znatne hidravlične izgube ki so posledica toka delovnega medija z veliko obodno komponento hitrosti od črpalnega rotorja 21 skozi dolge kanale, kolena in nepremakljive vodilne lopatice 23 na zunanjem obodu hidrodinamičnega pretvornika momenta do turbinskega rotorja 22;- the turbine rotor 22, whose inlet diameter D221 is smaller than the outlet diameter of the pump rotor d 2! 2 of the pump rotor 21, is mounted on the side where the flow of the working medium has a direction toward the rotary axis 29, which is due to the distance of the turbine rotor 22 from the pump rotor 21 resulting in significant hydraulic loss resulting from the flow of the medium with a large circumferential velocity component from the pump rotor 21 through long ducts, elbows and a fixed guide vanes 23 at the outer perimeter of the hydrodynamic torque converter 22;
- nepremakljive vodilne lopatice 24 na notranjem obodu hidrodinamičnega pretvornika momenta in regulacijske lopatice 25 so nameščene v področju majhnih pretočnih prerezov, kar vodi k visokim hitrostim delovnega medija in posledično spet do znatnih hidravličnih izgub;- the fixed guide vanes 24 on the inner circumference of the hydrodynamic torque converter and the control vanes 25 are mounted in the region of small cross-sections, which leads to high speeds of the working medium and, consequently, to significant hydraulic losses;
- regulacijske lopatice 25 so nameščene na notranjem obodu hidrodinamičnega pretvornika momenta med turbinskim rotorjem 22 in črpalnim rotorjem 21, kar terja občutno zahtevnejšo zasnovo geometrije lopatic 25 in regulacijskega mehanizma kot pri konvencionalni izvedbi hidrodinamičnega pretvornika momenta po Sl. 1;- the control blades 25 are mounted on the inner circumference of the hydrodynamic torque converter between the turbine rotor 22 and the pump rotor 21, which requires a much more complex design of the geometry of the blades 25 and the control mechanism than in the conventional embodiment of the hydrodynamic torque converter according to FIG. 1;
- hidrodinamični pretvornik momenta v izvedbi po US 7,155,904 je v aksialni smeri daljši kot konvencionalne izvedbe hidrodinamičnega pretvornika momenta po Sl. 1;- the hydrodynamic torque converter in the embodiment according to US 7,155,904 is longer in the axial direction than the conventional embodiments of the hydrodynamic torque converter according to FIG. 1;
- moment MT na turbinski strani v smeri zmanjševanja razmerja vrtljajev np/np (Sl. 6) ni stalno naraščajoč, kar načeloma vodi k omejitvam pri obratovanju.- the torque MT on the turbine side in the direction of decreasing the speed np / np (Fig. 6) is not constantly increasing, which in principle leads to operating restrictions.
Hidrodinamični pretvornik momenta, ki je predmet pričujoče patentne prijave in katerega karakteristike so v diagramih po Sl. 6 označene s HPM3, bo v nadaljevanju podrobneje obrazložen s primeri izvedbe, ki so shematično ponazorjeni na Sl. 3-5. Obravnavani pretvornik podobno kot tisti po US 7,155,904 (Sl. 2) omogoča doseganje maksimalnega izkoristka v območju vrednosti razmerja vrtljajev 1 < np/np < 4.The hydrodynamic torque converter which is the subject of the present patent application and whose characteristics are shown in the diagrams of FIG. 6, denoted by HPM3, will be further explained in the following with exemplary embodiments schematically illustrated in FIG. 3-5. The converter in question, similar to that of US 7,155,904 (Fig. 2), allows for maximum efficiency to be obtained in the range of 1 <np / np <4.
Pretvornik po izumu obsega toroidno ohišje 35, v katerem so vgrajeni črpalni rotor 31, turbinski rotor 32, sklop regulacijskih vodilnih lopatic 33, ki je razporejen radialno izven zunanjega premera črpalnega rotorja 31, in sklop fiksnih vodilnih lopatic 34, ki je razporejen radialno znotraj notranjega premera črpalnega rotoija 31 in radialno izven zunanjega premera turbinskega rotorja 32.The converter of the invention comprises a toroidal housing 35 comprising a pump rotor 31, a turbine rotor 32, a set of control guide vanes 33 arranged radially outside the outer diameter of the pump rotor 31, and a set of fixed guide vanes 34 arranged radially inside the inner pump rotor diameter 31 and radially outside the outer diameter of the turbine rotor 32.
Črpalni rotor 31 je povezan s pogonsko gredjo 37, turbinski rotor 32, 32', 32 (Sl. 3 - 5) pa z odgonsko gredjo 36, pri čemer sta omenjeni gredi 36, 37 vrtljivi okoli taiste geometrijske osi in sta torej soosni. Smer kroženja delovnega medija je na Sl. 4 - 6 označena s puščicama in 310.The pump rotor 31 is connected to the drive shaft 37 and the turbine rotor 32, 32 ', 32 (Figs. 3 - 5) to the drive shaft 36, said shafts 36, 37 rotating about the same geometric axis and thus coaxial. The direction of circulation of the working medium is in Figs. 4 - 6 marked with arrows and 310.
Pretvornik po izumu je tako zasnovan, da si - gledano v smeri pretoka delovnega medija t.j. v smeri puščic 39, 310 - regulacijske vodilne lopatice lopatice 33, črpalni rotor 31, fiksne vodilne lopatice 34 in turbinski rotor 32 sledijo radialno drug za drugim, načeloma v smeri radialno navznoter, pri čemer je vstopni premer največji v območju regulacijskih vodilnih lopatic 33, v območju turbinskega rotorja 32 pa najmanjši.The converter according to the invention is so designed that when viewed from the direction of the flow of the working medium, i.e. in the direction of the arrows 39, 310 - the control guide vanes of the blades 33, the pump rotor 31, the fixed guide vanes 34 and the turbine rotor 32 follow radially one after the other, in principle in the radial inwards direction, the inlet diameter being greatest in the area of the regulating guide vanes 33, in the area of the turbine rotor 32 the smallest.
Črpalni rotor 31 je tako zasnovan, da omogoča črpanje delovnega medija v smeri proti rotacijski osi 38 in povečuje specifično energijo delovnega medija skozi rotor 31 v smeri proti rotacijski osi 38, kar pomeni, da je specifična energija delovnega medija na izstopnem premeru d3j2 črpalnega rotorja 31 večja kot na njegovem vstopnem premeru, pri čemer je izstopni premer d3i2 črpalnega rotorja 31 manjši od njegovega vstopnega premera.The pump rotor 31 is designed to allow the pumping of the working medium in the direction of the rotary axis 38 and increases the specific energy of the working medium through the rotor 31 in the direction of the rotary axis 38, which means that the specific energy of the working medium is at the exit diameter d 3 j 2 the pump rotor 31 is larger than its inlet diameter, the outlet diameter d 3 and 2 of the pump rotor 31 being smaller than its inlet diameter.
Delovni medij z visoko specifično energijo zapušča črpalni rotor 31 in potuje skozi sklop fiksnih vodilnih lopatic 34 do turbinskega rotorja 32, katerega vstopni premer D32i je manjši od izstopnega premera d3i2 črpalnega rotorja 31. V turbinskem rotorju 32 se specifična energija delovnega medija pretvarja v mehansko delo.High specific energy medium leaves the pump rotor 31 and travels through a set of fixed guide vanes 34 to a turbine rotor 32 whose inlet diameter D 32 i is smaller than the outlet diameter d 3 and 2 of the pump rotor 31. In the turbine rotor 32, the specific energy of the working converts media into mechanical work.
Pri primeru izvedbe po Sl. 3 gre za različico pretvornika vrtilnega momenta po izumu, pri kateri je tok delovnega medija skozi turbinski rotor 32 usmerjen radialno navznoter proti rotacijski osi 38.In the embodiment of FIG. 3 is a variant of a torque converter according to the invention, in which the flow of the working medium through the turbine rotor 32 is directed radially inwardly towards the rotary axis 38.
Pri nadaljnji različici pretvornika po izumu, ki je prikazana na Sl. 4, je namesto radialnega turbinskega rotorja 32 iz predhodne različice uporabljen radialno-aksialni turbinski rotor 32', katerega princip delovanja je analogen strokovnjakom znani Francisovi turbini. V tem primeru je pretok delovnega medija v turbinskem rotorju 32 iz smeri radialno navznoter proti osi 38 preusmerjen v aksialno smer t.j. vzdolž osi 38.In a further embodiment of the converter of the invention shown in FIG. 4, instead of the radial turbine rotor 32 of the previous version, a radial-axial turbine rotor 32 'is used, the principle of operation of which is analogous to those known to Francis skilled turbine. In this case, the flow of the working medium in the turbine rotor 32 from the radial inward direction to the axis 38 is diverted to the axial direction, i.e. along the axis 38.
Pri še nadaljnji različici pretvornika po izumu, ki je prikazana na Sl. 5, je namesto radialnega turbinskega rotoija 32 iz različice po Sl. 3 ali radialno-aksialne izvedbe turbinskega rotorja 32' iz predhodne različice uporabljen turbinski rotor 32, katerega princip delovanja je analogen strokovnjakom znani Kaplanovi turbini. V tem primeru je pretok delovnega medija, ki sicer proti rotorju 32 doteka v radialni smeri, skozi sam turbinski rotor 32 usmerjen v aksialni smeri t.j. vzdolž osi 38.In still a further embodiment of the converter of the invention shown in FIG. 5, instead of the radial turbine rotoi 32 of the version of FIG. 3 or radial-axial embodiment of the turbine rotor 32 'of the previous version used turbine rotor 32, the principle of operation of which is analogous to the experts known to Kaplan turbine. In this case, the flow of the working medium, which otherwise flows towards the rotor 32 in the radial direction, through the turbine rotor 32 itself is directed in the axial direction, i.e. along the axis 38.
Turbinski rotor 32 pretvornika po izumu torej načeloma omogoča zmanjševanje specifične energije delovnega medija skozi rotor 32 v smeri radialno navznoter proti rotacijski osi 38, če gre za radialni turbinski rotor 32 (Sl. 3), ali tudi s kombiniranjem smeri aksialno in/ali radialno glede na rotacijsko os 38 z zamenjavo radialnega turbinskega rotorja 32 z radialnoaksialnim turbinskim rotorjem 32' (Sl. 4) oz. aksialnim rotorjem 32” (Sl. 5).The turbine rotor 32 of the converter according to the invention therefore allows, in principle, the reduction of the specific energy of the working medium through the rotor 32 radially inwardly towards the rotary axis 38, in the case of a radial turbine rotor 32 (Fig. 3), or also by combining the direction axially and / or radially with respect to to the rotary axis 38 by replacing the radial turbine rotor 32 with the radial axial turbine rotor 32 '(Fig. 4) or. 32 ”axial rotor (Fig. 5).
Delovni medij se pretaka po kanalih toroidnega ohišja 35 do regulacijskih vodilnih lopatic 33 na zunanjem premeru črpalnega rotorja 31 in vstopa v črpalni rotor 31. Premikanje oz. nastavljanje regulacijskih vodilnih lopatic 33 se v prikazanem primeru vrši z rotacijo aksialno postavljenih palic 311 okoli osi 312, pri čemer so med drugim odpravljene tudi pomanjkljivosti, ki izhajajo oz pred tem znane rešitve po Sl. 2. Poleg tega se pretvornik vrtilnega momenta po izumu v kontekstu omenjene primeijave z znanim pretvornikom po Sl. 2 odlikuje še po nekaterih drugih konstrukcijskih in obratovalnih prednostih, in sicerThe working medium flows through the channels of the toroidal housing 35 to the control guide blades 33 at the outside diameter of the pump rotor 31 and enters the pump rotor 31. in this example, the adjustment of the guide vanes 33 is accomplished by rotating the axially positioned bars 311 about the axis 312, which also eliminates, among other things, the disadvantages resulting from, or previously known solutions of, FIG. 2. In addition, the torque converter of the invention in the context of said priming with the known transducer of FIG. 2 also has some other structural and operational advantages, namely
- delovni medij z visoko specifično energijo in veliko obodno komponento toka, ki izstopa iz črpalnega rotorja 31 v smeri proti rotacijski osi 38, do vstopa v turbinski rotor 32 potuje zgolj skozi sklop oz. kaskado fiksnih vodilnih lopatic, kar očitno privede do zmanjšanja hidravličnih izgub v območju med črpalnim rotorjem 31 in turbinskim rotorjem 32, ki so v tem kontekstu pri rešitvi po Sl. 2, kjer delovni medij opravi bistveno daljšo pot od izstopa iz črpalnega rotorja 31 do vstopa v turbinski rotor 32, nedvomno večje;- a medium with a high specific energy and a large circumferential component of the current exiting the pump rotor 31 in the direction of the rotary axis 38, only enters the inlet of the turbine rotor 32 through the assembly, or a cascade of fixed guide vanes, which obviously results in the reduction of hydraulic losses in the area between the pump rotor 31 and the turbine rotor 32, which are in this context the solution of FIG. 2, where the working medium takes a substantially longer path from the outlet of the pump rotor 31 to the inlet of the turbine rotor 32, no doubt larger;
- regulacijske vodilne lopatice 33 so pri pretvorniku po izumu razporejene na večjem premeru kot pri prej znani rešitvi po Sl. 2, kar zaradi manjših hitrosti obtekajočega delovnega medija spet prispeva k zmanjšanju hidravličnih izgub;- the control guide vanes 33 are arranged in a larger diameter in the converter of the invention than in the previously known solution of FIG. 2, which again contributes to the reduction of hydraulic losses due to the slow speed of the flowing work medium;
- geometrija in konstrukcijska zasnova regulacijskih vodilnih lopatic 33 in pripadajočega mehanizma za regulacijo le-teh sta pri rešitvi po izumu znatno poenostavljeni;- the geometry and structural design of the control guide vanes 33 and the associated control mechanism thereof are greatly simplified in the solution according to the invention;
ohišje 35 pretvornika po izumu je v aksialni smeri lahko znatno krajše kot pri znani rešitvi (Sl. 2) moment MT (Sl. 6) na strani turbinskega rotoija 32 pri pretvorniku po izumu stalno narašča v smeri zmanjševanja razmerja vrtljajev ηγ/ηΡ, kar pa ne velja za karakteristiko momenta MT na strani turbinskega rotorja pri znani rešitvi po sl. 2; področje obratovanja pri visokem izkoristku je pri pretvorniku po izumu bistveno širše kot pri pred tem znanem pretvorniku po Sl. 2, kar je prav tako razvidno v priloženem diagramu po Sl. 6.the housing of the converter of the invention according to the invention may be substantially shorter in the axial direction than the known solution (Fig. 2), the MT (Fig. 6) moment on the turbine rotoi side 32 of the converter according to the invention is steadily increasing in the direction of decreasing the rpm η / η Ρ , however, the torque characteristic MT on the turbine rotor side is not considered in the known solution of FIG. 2; the field of operation at high efficiency is significantly wider in the converter of the invention than in the previously known converter of FIG. 2, which is also evident in the accompanying diagram of FIG. 6.
Claims (11)
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| SI200800292A SI22917A (en) | 2008-11-27 | 2008-11-27 | Hydrodynamic torque transducer |
| PCT/SI2009/000051 WO2010062269A1 (en) | 2008-11-27 | 2009-10-15 | Hydrodynamic torque converter |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| SI200800292A SI22917A (en) | 2008-11-27 | 2008-11-27 | Hydrodynamic torque transducer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| SI22917A true SI22917A (en) | 2010-05-31 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| SI200800292A SI22917A (en) | 2008-11-27 | 2008-11-27 | Hydrodynamic torque transducer |
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| SI (1) | SI22917A (en) |
| WO (1) | WO2010062269A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104358852B (en) * | 2014-11-07 | 2016-08-24 | 吉林大学 | A kind of axial-flow type stator adjustable hydraulic torque converter and stator control method |
| CN106321771B (en) * | 2016-11-08 | 2018-12-18 | 哈尔滨广瀚动力传动有限公司 | A kind of double guide wheel guide vane adjustable hydraulic torque converters of novel twin turbines |
| WO2020099031A1 (en) | 2018-11-14 | 2020-05-22 | Voith Patent Gmbh | Hydrodynamic converter |
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| DE10039811A1 (en) * | 2000-08-16 | 2002-03-07 | Voith Turbo Kg | Hydrodynamic converter |
| DE102004011033B3 (en) * | 2004-03-06 | 2005-12-29 | Voith Turbo Gmbh & Co. Kg | Hydrodynamic converter |
-
2008
- 2008-11-27 SI SI200800292A patent/SI22917A/en not_active IP Right Cessation
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