NO130491B - - Google Patents
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- Publication number
- NO130491B NO130491B NO205172A NO205172A NO130491B NO 130491 B NO130491 B NO 130491B NO 205172 A NO205172 A NO 205172A NO 205172 A NO205172 A NO 205172A NO 130491 B NO130491 B NO 130491B
- Authority
- NO
- Norway
- Prior art keywords
- elastic
- ring
- coupling according
- coil body
- magnetizing current
- Prior art date
Links
- 230000008878 coupling Effects 0.000 claims description 23
- 238000010168 coupling process Methods 0.000 claims description 23
- 238000005859 coupling reaction Methods 0.000 claims description 23
- 238000013016 damping Methods 0.000 claims description 20
- 230000010355 oscillation Effects 0.000 claims description 11
- 238000001816 cooling Methods 0.000 claims description 4
- 230000001105 regulatory effect Effects 0.000 claims description 2
- 238000010276 construction Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 230000001939 inductive effect Effects 0.000 description 2
- 206010057175 Mass conditions Diseases 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000005520 electrodynamics Effects 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Classifications
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0632—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with conical friction surfaces, e.g. cone clutches
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
- F16D3/76—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members shaped as an elastic ring centered on the axis, surrounding a portion of one coupling part and surrounded by a sleeve of the other coupling part
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
- Dynamo-Electric Clutches, Dynamo-Electric Brakes (AREA)
Description
Ela-stisk akselkopling. Elastic axle coupling.
Oppfinnelsen angår en elastisk akselkopling bestående The invention relates to an elastic shaft coupling consisting of
av en primærdel og en sekundærdel, der sekundærdelen oppviser en stiv innerring (prirnærring), en stiv ytterring (sekundærring) som konsentrisk omgir innerringen, samt et elastisk lag som sammenbinder de to ringene. of a primary part and a secondary part, where the secondary part has a rigid inner ring (primary ring), a rigid outer ring (secondary ring) which concentrically surrounds the inner ring, and an elastic layer which connects the two rings.
Ved dieselmotoraggregater er det en fordel å anvende elastiske koplinger for å nedsette de lave svingnings.grader i den hensikt å kunne kjøre hele anlegget over det kritiske punkt. Dette har man hittil greid med disse anleggene da materialdempningen i gummien var tilstrekkelig, da den elastiske kopling bare for en li-ten del var innrettet til å dempe svingningene i systemet. In the case of diesel engine units, it is an advantage to use elastic couplings to reduce the low degrees of oscillation in order to be able to drive the entire system above the critical point. This has so far been managed with these systems as the material damping in the rubber was sufficient, as the elastic coupling was only designed to dampen the oscillations in the system to a small extent.
Tendensen innen dieselmotorbyggingen for nedsettelse av vekten i forhold til effekten bringer tvangsmessig med seg større for-styrrelseskrefter ve'd ugunstigere masseforhold. Derved blir' de veks-lende påkjenninger på grunn av høyere svingningsgrader i veivakselen så stor at motorsvingningsdempere alene ikke lenger er tilstrekkelig og den elastiske kopling må ta en større del av systemets dempning. Derved blir det nødvendig å tilpasse koplingen til alle' betingelser og forsyne den med en regulerbar innretning til tilleggsdempning under driften. The tendency in diesel engine construction to reduce the weight in relation to the power inevitably brings with it greater disturbance forces due to less favorable mass conditions. Thereby, the alternating stresses due to higher degrees of oscillation in the crankshaft become so great that engine vibration dampers alone are no longer sufficient and the elastic coupling must take up a larger part of the system's damping. This makes it necessary to adapt the coupling to all conditions and provide it with an adjustable device for additional damping during operation.
Det er tidligere kjent elastiske koplinger omfattende en primær-og en sekundærdel, der en stiv ytterring konsentrisk omgir en stiv innerring,. idet et elastisk mellomlag forbinder de to ringene med hverandre. Previously known elastic couplings comprising a primary and a secondary part, where a rigid outer ring concentrically surrounds a rigid inner ring. with an elastic intermediate layer connecting the two rings to each other.
Det er videre kjent en elektro-dynamisk innretning for dempning av dreiesvingninger, der et spolelegeme er fast forbundet til en innerring og der det videre er en ytterring som omgir innerringen. Til ytterringen er det forbundet en ankerring som konsentrisk omgir spolelegemet under dannelse av en luftspalte og det er sørget for strømtilførsel til spolelegemet på en slik måte at magnetiserings-strømmen er regulerbar. An electro-dynamic device for dampening rotational oscillations is also known, where a coil body is firmly connected to an inner ring and where there is also an outer ring that surrounds the inner ring. An anchor ring is connected to the outer ring which concentrically surrounds the coil body while forming an air gap and provision is made for power supply to the coil body in such a way that the magnetizing current is adjustable.
Hensikten med foreliggende oppfinnelse er å forbedre The purpose of the present invention is to improve
de tidligere kjente elastiske koplinger og dette oppnås ifølge oppfinnelsen ved en elastisk kopling som består av en primær-og en sekundærdel , der sekundærdelen oppviser en stiv innerring (primærringen), en stiv ytterring (sekundærdelen) som konsentrisk omgir innerringen samt et elastisk lag som sammenbinder de to ringene, og der det i tillegg er anordnet midler til dreiesvingningsdempning, og der det karakte-ristiske ved oppfinnelsen består i at et spolelegeme er festet til innerringen, at det til ytterringen er festet en ankerring som konsentrisk omgir spolelegemet under dannelse av et luftgap, og at det er anordnet en strømtilførsel for spolelegemet på en slik måte at magnetiseringsstrømmen kan reguleres. the previously known elastic couplings and this is achieved according to the invention by an elastic coupling which consists of a primary and a secondary part, where the secondary part has a rigid inner ring (the primary ring), a rigid outer ring (the secondary part) which concentrically surrounds the inner ring and an elastic layer which connects the two rings, and where there are additionally arranged means for rotational vibration damping, and where the characteristic of the invention consists in that a coil body is attached to the inner ring, that an anchor ring is attached to the outer ring which concentrically surrounds the coil body while forming an air gap , and that a power supply is arranged for the coil body in such a way that the magnetizing current can be regulated.
Derved oppnås at de overlagrede vekselmomenter dempes uten at den ytterligere dempningsinnretning selv tar del i kraftover-føringen. Det er altså bare overlagrede vekselmomenter ved en bestemt lastavhengig.dreievinkel som dempes, uten at derved fjærstivheten på elastiske deler forandrer seg eller blir påvirket. Thereby it is achieved that the superimposed alternating torques are damped without the further damping device itself taking part in the power transmission. It is therefore only superimposed alternating torques at a specific load-dependent angle of rotation that are damped, without thereby changing or being affected the spring stiffness of elastic parts.
En ytterligere fordel oppnås ved innretningen ifølge oppfinnelsen ved at man ved en .åndring av den tilførte magnetiserings-strøm under driften kan variere dempningskreftene, slik at f.eks. ved ulikeformet tenningstrykk i motoren og/eller ved temporær utkopling av en el l-er flere sylindre, ved hjelp av en økning av dempningen kan anlegget holdes uforandret i drift. A further advantage is achieved with the device according to the invention in that, by changing the applied magnetizing current during operation, the damping forces can be varied, so that e.g. with differently shaped ignition pressure in the engine and/or with temporary disconnection of one or more cylinders, by means of an increase in damping, the system can be kept unchanged in operation.
Videre kan reguleringen av magnetiseringsstrømmen gjøres avhengig av stillingen av de forskjellige kritiske egensvingninger i anlegget. Magnetiseringsstrømmen kan, avhengig-av omdreiningstallet, tilpasses slik at ved tilnærming av bestemte systembetingede kritiske egensvingninger bli forstørret og etter gjennomgang av det kritiske området igjen forminskes. Da det bare er skadelig med en dempning ved gang over det kritiske .punkt og dessuten bruker energi, kan man med denne løsning bidra til en gunstig energibalanse i hele anlegget. Furthermore, the regulation of the magnetizing current can be made depending on the position of the various critical self-oscillations in the plant. The magnetizing current can, depending on the number of revolutions, be adapted so that upon approaching certain system-related critical self-oscillations, they are enlarged and after passing through the critical area are reduced again. As it is only harmful to dampen when going above the critical point and also consumes energy, this solution can contribute to a favorable energy balance in the entire plant.
Dersom koplingens primærdel forbindes med drivakselen, tjener innretningen som en elastisk kopling. If the primary part of the coupling is connected to the drive shaft, the device serves as an elastic coupling.
Ifølge et ytterligere trekk ved oppfinnelsen kan sekundærdelen forbindes med drivakselen mens primærdelen er fritt bevegelig. Derved er det frembrakt en anordning for dempning av motoren, f.eks. for dempning av veivakselsvingningene. According to a further feature of the invention, the secondary part can be connected to the drive shaft while the primary part is freely movable. Thereby, a device for dampening the engine has been produced, e.g. for dampening the crankshaft oscillations.
Ifølge'et ytterligere trekk ved oppfinnelsen oppviser ankerringen kjøleribber på utsiden eller er ved den frie ende utformet som en vifte. Varmen som ved dempningen oppstår i den elektromagnetiske del kan på den måte føres bort fra ankerringen. According to a further feature of the invention, the anchor ring has cooling ribs on the outside or is designed as a fan at the free end. In this way, the heat that occurs in the electromagnetic part during damping can be led away from the armature ring.
Magnetiseringsstrømmen kan ifølge et ytterligere trekk ved oppfinnelsen tilføres gjennom en boring i drivakselen til spolebæreren. Videre kan magnetiseringsstrømmen imidlertid også være in-duktiv eller tilføres over sleperinger som er anordnet direkte på spolebæreren. Som magnetiseringsstrøm blir det fortrinnsvis brukt en lav spenning på 12 - 2k Volt for å unngå mulige isolerongsproblemer og for å gjøre koplingen uavhengig av den eksisterende spenning ombord. According to a further feature of the invention, the magnetizing current can be supplied through a bore in the drive shaft of the coil carrier. Furthermore, however, the magnetizing current can also be inductive or supplied via slip rings which are arranged directly on the coil carrier. As magnetizing current, a low voltage of 12 - 2k Volts is preferably used to avoid possible insulation problems and to make the connection independent of the existing voltage on board.
Oppfinnelsen skal i det følgende forklares nærmere under henvisning til tegningen som i In the following, the invention will be explained in more detail with reference to the drawing as in
fig0l viser et delvis snitt gjennom en utkoplbar elastisk akselkopling med en elektromagnetisk dempningsdel, og fig01 shows a partial section through a detachable elastic shaft coupling with an electromagnetic damping part, and
fig.2 viser en ikke-utkoplbar elastisk akselkopling med dempningsdelo fig.2 shows a non-detachable elastic shaft coupling with damping part
Koplingens primærdel ] og ^ er forbundet; med drivakselen, The primary part of the conjunction ] and ^ are connected; with the drive shaft,
Sekundærdelen som er forbundet med den drevne aksel, oppviser en stiv innerring (primærring) 2, en stiv ytterring (sekundærring) 4 som konsentrisk omgir innerringen, samt et gummi-elastisk mellomlag 3 som forbinder de to ringer. Koplingen er i figur 1 vist i innkoplet til-stand. The secondary part which is connected to the driven shaft has a rigid inner ring (primary ring) 2, a rigid outer ring (secondary ring) 4 which concentrically surrounds the inner ring, as well as a rubber-elastic intermediate layer 3 which connects the two rings. The coupling is shown in Figure 1 in the engaged state.
Ved den ikke-utkoplbare kopling er bare delen 1 beteg-net som primærdel, da i det tilfellet ytterringen 3 blir regnet som sekundærdelen. Med innerringen 2 er det forbundet en spolebærer 6. Spolebæreren 6 kan være enpolet. Spolebæreren 6 kan tilføres magneti-saingsstrøm gjennom boringen 10 i drivakselen. Strømtilførselen kan imidlertid også skje på andre måter, f.eks. ved hjelp av sleperinger som direkte er forbundet med spolebæreren,. eller berøringsløst induk-tiv. Spolebæreren 6 omgis konsentrisk av en ankerring 7 under dannelse av et luftgap 8, hvilken ankerring 7 er forbundet med ytterringen 4. With the non-detachable coupling, only part 1 is designated as the primary part, as in that case the outer ring 3 is considered the secondary part. A coil carrier 6 is connected to the inner ring 2. The coil carrier 6 can be unipolar. The coil carrier 6 can be supplied with magnetic current through the bore 10 in the drive shaft. However, the power supply can also take place in other ways, e.g. by means of drag rings which are directly connected to the coil carrier,. or contactless inductive. The coil carrier 6 is surrounded concentrically by an anchor ring 7 forming an air gap 8, which anchor ring 7 is connected to the outer ring 4.
Ved den ovenfor beskrevne utførelse oppviser ankerringen en ventilator 5 og også kjøleribber 9 for fjerning av varme. Varmefjerningen kan imidlertid skje utelukkende ved hjelp av kjølerib-ben. De svingninger som opptas av det elastiske mellomlag 3 fører til en relativ bevegelse mellom spolebæreren og ankerringen. Herved blir det i ankerringen 7 indusert en spenning som er avhengig av magneti-seringsstrømmens størrelse og av Sekvensen og amplituden for den overlagrede relative bevegelse (torsjonssvingning). In the embodiment described above, the anchor ring has a fan 5 and also cooling fins 9 for removing heat. However, the heat can be removed exclusively with the help of the cooling fins. The oscillations absorbed by the elastic intermediate layer 3 lead to a relative movement between the coil carrier and the anchor ring. Hereby, a voltage is induced in the armature ring 7 which is dependent on the size of the magnetizing current and on the sequence and amplitude of the superimposed relative movement (torsional oscillation).
Ved hjelp av utførelsen ifølge oppfinnelsen løses to vesentlige oppgaver når det gjelder svingninger ved dieselmotoraggregater. For det første oppnås ved hjelp av den variable dreiefjærstiv-het på de elastiske deler den ønskede svingningsforandring, og for det andre oppnås en ønsket og innstillbar dempning av det samlede system ved hjelp av den elektromagnetiske del. With the help of the design according to the invention, two important tasks are solved when it comes to oscillations in diesel engine units. Firstly, the desired oscillation change is achieved by means of the variable torsional spring stiffness of the elastic parts, and secondly, a desired and adjustable damping of the overall system is achieved by means of the electromagnetic part.
Alle fordeler som oppnås- ellers ved en elektrisk kopling, f0eks. med hensyn til opptagelse av forskyvninger i ønsket retning, beholdes ubeskåret. All advantages that are otherwise achieved by an electrical connection, e.g. with regard to the recording of displacements in the desired direction, is kept uncut.
Ved den konstruktive atskillelse av den elastiske del og dempedelen er det mulig å bygge til den nevnte dempningsdel etterpå på en allerede for hånden værende elastisk -kopling. With the constructive separation of the elastic part and the damping part, it is possible to build the aforementioned damping part afterwards on an elastic coupling that is already at hand.
Utførelsesformen ifølge fig.2 kan fordelaktig også brukes som motordemper, idet den alt etter valget av fjærstivheten virker svingningsforskyvende og dempende eller bare dempende. Også her er •«. v V i i; x regulerbarheten fordelaktig. The embodiment according to fig.2 can advantageously also be used as a motor damper, as it acts as a vibration-displacing and damping or simply damping function, depending on the choice of spring stiffness. Here too is •«. v V i i; x adjustability beneficial.
Endelig kan denne utførelse brukes som systemdempning, da nemlig dempedelen kan anordnes på en hvilken som helst fri aksel-ende i et system, f„eks. mellomakselen i en veksel. Finally, this design can be used as system damping, since the damping part can be arranged on any free shaft end in a system, e.g. the intermediate shaft in a gearbox.
Ved hjelp av den beskrevne løsning er begge forutset-ninger for en eksakt beregning av dreiesvingningsområdet gitt, da dreiestivheten er lineær og den elektromagnetiske dempning hastig-hetsproporsjonal. Den elektromagnetiske dels frekvensavhengighet kan man uten videre ta hensyn til ved konstruksjonen, uten at man behøver stille opp noen ytterligere ligning for omforming av hastighetspropor--sjonal dempning. With the help of the described solution, both prerequisites for an exact calculation of the rotational oscillation range are given, as the rotational stiffness is linear and the electromagnetic damping is speed-proportional. The frequency dependence of the electromagnetic part can easily be taken into account during the construction, without the need to set up any further equations for the conversion of speed-proportional damping.
Claims (7)
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19712139249 DE2139249C3 (en) | 1971-08-02 | 1971-08-02 | Highly flexible shaft coupling |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| NO130491B true NO130491B (en) | 1974-09-09 |
| NO130491C NO130491C (en) | 1974-12-18 |
Family
ID=5815897
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| NO205172A NO130491C (en) | 1971-08-02 | 1972-06-09 |
Country Status (13)
| Country | Link |
|---|---|
| JP (1) | JPS5750977B1 (en) |
| BE (1) | BE786989A (en) |
| CA (1) | CA950221A (en) |
| CS (1) | CS178872B2 (en) |
| DD (1) | DD98348A5 (en) |
| DE (1) | DE2139249C3 (en) |
| FI (1) | FI54389C (en) |
| FR (1) | FR2144503A5 (en) |
| GB (1) | GB1378056A (en) |
| IT (1) | IT955629B (en) |
| NL (1) | NL7208085A (en) |
| NO (1) | NO130491C (en) |
| SE (1) | SE383654B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5976100U (en) * | 1982-11-12 | 1984-05-23 | 株式会社エ−ビ−シ−商会 | Structure of the joint part of the breast conductor |
| DE3330080C2 (en) * | 1983-08-17 | 1986-10-23 | Mannesmann AG, 4000 Düsseldorf | Highly elastic damping coupling |
| JPS61180463U (en) * | 1985-04-30 | 1986-11-11 | ||
| DE102014013453A1 (en) | 2014-09-17 | 2016-03-17 | Centa-Antriebe Kirschey Gmbh | Device for transmitting torques |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1024065A (en) * | 1962-10-20 | 1966-03-30 | Lohmann & Stolterfort A G | Improvements in and relating to shaft couplings |
-
1971
- 1971-08-02 DE DE19712139249 patent/DE2139249C3/en not_active Expired
-
1972
- 1972-05-18 IT IT2452172A patent/IT955629B/en active
- 1972-05-31 FI FI152872A patent/FI54389C/en active
- 1972-06-09 NO NO205172A patent/NO130491C/no unknown
- 1972-06-13 NL NL7208085A patent/NL7208085A/xx unknown
- 1972-06-21 DD DD16387972A patent/DD98348A5/xx unknown
- 1972-06-27 GB GB3000472A patent/GB1378056A/en not_active Expired
- 1972-07-13 CS CS498572A patent/CS178872B2/en unknown
- 1972-07-21 FR FR7227179A patent/FR2144503A5/fr not_active Expired
- 1972-07-28 SE SE990272A patent/SE383654B/en unknown
- 1972-07-31 BE BE786989A patent/BE786989A/en unknown
- 1972-08-01 JP JP7724772A patent/JPS5750977B1/ja active Pending
- 1972-08-02 CA CA148,532,A patent/CA950221A/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| CS178872B2 (en) | 1977-10-31 |
| SU384247A3 (en) | 1973-05-23 |
| CA950221A (en) | 1974-07-02 |
| DE2139249A1 (en) | 1973-02-22 |
| FI54389B (en) | 1978-07-31 |
| IT955629B (en) | 1973-09-29 |
| FI54389C (en) | 1978-11-10 |
| GB1378056A (en) | 1974-12-18 |
| FR2144503A5 (en) | 1973-02-09 |
| JPS5750977B1 (en) | 1982-10-29 |
| DE2139249C3 (en) | 1974-11-28 |
| NL7208085A (en) | 1973-02-06 |
| BE786989A (en) | 1972-11-16 |
| SE383654B (en) | 1976-03-22 |
| DE2139249B2 (en) | 1974-04-25 |
| DD98348A5 (en) | 1973-06-12 |
| NO130491C (en) | 1974-12-18 |
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