SE507894C2 - Rope drum with transmission wholly or partially stored therein - Google Patents
Rope drum with transmission wholly or partially stored thereinInfo
- Publication number
- SE507894C2 SE507894C2 SE8705128A SE8705128A SE507894C2 SE 507894 C2 SE507894 C2 SE 507894C2 SE 8705128 A SE8705128 A SE 8705128A SE 8705128 A SE8705128 A SE 8705128A SE 507894 C2 SE507894 C2 SE 507894C2
- Authority
- SE
- Sweden
- Prior art keywords
- gear
- transmission
- toothed
- wholly
- rope drum
- Prior art date
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract 9
- 230000008878 coupling Effects 0.000 claims description 13
- 238000010168 coupling process Methods 0.000 claims description 13
- 238000005859 coupling reaction Methods 0.000 claims description 13
- 238000010586 diagram Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/02—Driving gear
- B66D1/14—Power transmissions between power sources and drums or barrels
- B66D1/22—Planetary or differential gearings, i.e. with planet gears having movable axes of rotation
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
- Handcart (AREA)
- Forklifts And Lifting Vehicles (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
507 894 2 ökar belastningståligheten och livslängden samt säkerheten. Växelns totala nyttoeffekt är god. 507 894 2 increases load resistance and service life as well as safety. The overall useful effect of the gear is good.
Kännetecknande för en annan förmånlig utföringsforrn av uppfinningen är, att kuggväxeln och planetvâxeln är belågnai en cylindrisk trumma, på vilken lintrumman är lagrad. Då den cylindriska trurnrnans hårdhet ännu väljs så, att trumman kan användas som lageryta och som planetvåxelns kuggkrans, erhålles en mycket stadig och funktionssäker enhet utan onödigt invecklade lösningar och delar.Characteristic of another advantageous embodiment of the invention is that the gear and the planetary gear are located in a cylindrical drum, on which the line drum is mounted. Since the hardness of the cylindrical drum is still chosen so that the drum can be used as a bearing surface and as the gear ring of the planetary gear, a very stable and functionally reliable unit is obtained without unnecessarily complicated solutions and parts.
Uppfinníngen beskrivs i det följande med hjälp av ett exempel genom att hänvisa till föl- jande ritningar, ivilka Figur 1 visar lyftmaskineriets växel i genomskäming.The invention is described in the following by means of an example by referring to the following drawings, in which Figure 1 shows the gear of the lifting machinery in cross-section.
Figur 2 visar ett principschema av lyftrnaskineriets växel sedd från ingångssidan.Figure 2 shows a schematic diagram of the lifting gear of the lift seen from the entrance side.
Figur 3 visar en kombination av kuggväxelns och planetväxelns principscheman enligt en utföringsforrn av uppfinningen.Figure 3 shows a combination of the gear diagrams of the gear unit and the planetary gear unit according to an embodiment of the invention.
Lyftrnaskineriets växel består av en i en lintrurnma 1 lagrad kuggväxel 2 med ett eller flera steg, som via en planetvåxel 3 är kopplad till lintrurnman. Planetväxeln 3 är med hjälp av kuggkopplingar 4 och 5 kopplad till både kuggväxeln 2 och lintrurnman 1. Kuggväxeln 2 och planetväxeln 3 är belägna i en cylindrisk trumma 6, på vilken lintrumman 1 är lagrad medelst nållager 7, 8. Effekten tillförs växeln med axeln 9. Kuggstegens lager befinner sig vid trummans 6 mellanskiva och vid dess ände. Kuggstegen är placerade radiellt i växel- huset så, att det sista kuggsteget 10 driver solaxeln 11 med hjälp av kuggkopplingen 4.The gear of the lifting machinery consists of a gear 2 stored in a cable gear 1 with one or more steps, which are connected to the cable gear via a planetary gear 3. The planetary gear 3 is connected by means of toothed couplings 4 and 5 to both the gearbox 2 and the line gear 1. The gear 2 and the gear 3 are located in a cylindrical drum 6, on which the gear drum 1 is mounted by means of needle bearings 7, 8. The power is supplied to the gear The bearing of the rack is located at the intermediate disc of the drum 6 and at its end. The gear stages are located radially in the gear housing so that the last gear stage 10 drives the solar shaft 11 by means of the gear coupling 4.
Kuggkopplingen 4 är så utformad, att den invändigt tandade 4a kopplingshylsan 4 drivs med kuggstegets 10 tandade axel l0a. Kopplingshylsan överför vridmomentet på samma sätt till den tandade solaxeln 11. Glappet mellan axlama 10a och 11 saint kopplingshylsan 4 är valt tillräckligt stort så, att kopplingshylsan 4 kan lägga sig i ett snett läge, då solaxeln söker sig i det av planethjulen 12 definierade gångläget så, att kuggkontakten blir så god 507 894 3 som möjligt. Den radiella förskjutningen hos solaxeln sker som en enkelriktad förflyttning i förhållande till planethjulen. På grund av växelns integrerade konstruktion är behovet av radiell förskjutning litet, varav följer att kuggningen kan ha den normala evolventkuggfor- men. Solaxeln driver planethjulsystemet 12. Från planetbärare 13 överförs vridmomentet med hjälp av kuggkopplingen 5 via mellanskivan 14 till lintrumman 1. Kuggkopplingens 5 fimktionsprincip är densamma som hos kopplingen 4. Avvikande är endast det, att den in- vândiga tandningen finns i planetbäraren 13 och i valsens mellanskiva 14. Vridmomentet överförs av delen 5, som kan lägga sig i ett snett läge. Lösningen garanterar det, att planet- hjulens 12 kontakt mot kuggkransen blir sâ god som möjligt. Såsom framgått ovan, kräver en dylik kombination ett mycket litet antal delar, av vilket följer, att växeln är förmånlig både vad tillverknings- och servicekostnader beträffar. Likaledes är driftpositionen god, eftersom antalet förband som förorsakar centreringsfel är rninimerat.The gear coupling 4 is designed such that the internally toothed 4a coupling sleeve 4 is driven with the toothed shaft 10a of the toothed step 10. The coupling sleeve transmits the torque in the same way to the toothed solar shaft 11. The gap between the shafts 10a and 11 saint the coupling sleeve 4 is chosen large enough so that the coupling sleeve 4 can lie in an oblique position, when the solar shaft seeks in the position defined by the planet wheels 12 , that the gear contact is as good 507 894 3 as possible. The radial displacement of the solar axis occurs as a unidirectional fl relative to the planetary wheels. Due to the integrated design of the gear, the need for radial displacement is small, from which it follows that the gearing can have the normal involute gear shape. The solar shaft drives the planetary gear system 12. From the planet carrier 13 the torque is transmitted by means of the gear coupling 5 via the intermediate disc 14 to the line drum 1. The principle of operation of the gear coupling 5 is the same as with the coupling 4. The only difference is that the internal toothing is in the planet carrier 13 intermediate disc 14. The torque is transmitted by the part 5, which can lie in an oblique position. The solution guarantees that the contact of the planet gears 12 with the gear ring is as good as possible. As stated above, such a combination requires a very small number of parts, from which it follows that the gear unit is advantageous both in terms of manufacturing and service costs. Likewise, the operating position is good, since the number of joints causing centering errors is minimized.
Claims (2)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FI865293A FI76540C (en) | 1986-12-23 | 1986-12-23 | Transmission for lifting machinery |
Publications (3)
Publication Number | Publication Date |
---|---|
SE8705128D0 SE8705128D0 (en) | 1987-12-22 |
SE8705128L SE8705128L (en) | 1988-06-24 |
SE507894C2 true SE507894C2 (en) | 1998-07-27 |
Family
ID=8523702
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
SE8705128A SE507894C2 (en) | 1986-12-23 | 1987-12-22 | Rope drum with transmission wholly or partially stored therein |
Country Status (10)
Country | Link |
---|---|
CA (1) | CA1317126C (en) |
DE (1) | DE3743911A1 (en) |
ES (1) | ES2006008A6 (en) |
FI (1) | FI76540C (en) |
FR (1) | FR2608578B1 (en) |
GB (1) | GB2199389B (en) |
IT (1) | IT1213952B (en) |
NL (1) | NL190895C (en) |
NO (1) | NO166579C (en) |
SE (1) | SE507894C2 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7862009B2 (en) | 2006-11-22 | 2011-01-04 | Victory Rig Equipment Corporation | Electric winch motor |
CN109915566B (en) * | 2019-03-29 | 2022-03-08 | 重庆大学 | Self-elevating ocean platform lifting gear box |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB819512A (en) * | 1956-04-27 | 1959-09-02 | Charles Auguste Maire | Improvements in motor-driven winches |
FR1516473A (en) * | 1967-03-08 | 1968-03-08 | Winch | |
DE2061059C3 (en) * | 1970-12-11 | 1975-07-03 | O & K Orenstein & Koppel Ag, 1000 Berlin | Drum winch with internal gear and floating bearing |
DK135891B (en) * | 1973-01-26 | 1977-07-11 | Mannesmann Meer Ag | Play with a planetary gear placed in its closed drum. |
DE3002139A1 (en) * | 1980-01-22 | 1981-07-23 | Thyssen Industrie Ag, 4300 Essen | Hoist winch multistage gearbox - has outer casing detachable from drum and forming annulus for output gear train |
DE3240345C3 (en) * | 1982-10-30 | 1993-12-02 | Mannesmann Ag | Rope drum drive |
-
1986
- 1986-12-23 FI FI865293A patent/FI76540C/en not_active IP Right Cessation
-
1987
- 1987-12-03 GB GB8728305A patent/GB2199389B/en not_active Expired - Lifetime
- 1987-12-15 CA CA000554369A patent/CA1317126C/en not_active Expired - Lifetime
- 1987-12-16 NO NO875246A patent/NO166579C/en not_active IP Right Cessation
- 1987-12-16 IT IT8712603A patent/IT1213952B/en active
- 1987-12-18 NL NL8703080A patent/NL190895C/en not_active IP Right Cessation
- 1987-12-21 FR FR8717801A patent/FR2608578B1/en not_active Expired - Lifetime
- 1987-12-22 ES ES8703681A patent/ES2006008A6/en not_active Expired
- 1987-12-22 SE SE8705128A patent/SE507894C2/en not_active IP Right Cessation
- 1987-12-23 DE DE19873743911 patent/DE3743911A1/en active Granted
Also Published As
Publication number | Publication date |
---|---|
DE3743911C2 (en) | 1992-04-09 |
DE3743911A1 (en) | 1988-07-07 |
FI76540B (en) | 1988-07-29 |
ES2006008A6 (en) | 1989-04-01 |
NL190895B (en) | 1994-05-16 |
NL190895C (en) | 1994-10-17 |
NO875246D0 (en) | 1987-12-16 |
GB2199389A (en) | 1988-07-06 |
NL8703080A (en) | 1988-07-18 |
NO166579B (en) | 1991-05-06 |
NO166579C (en) | 1991-08-14 |
FI865293A0 (en) | 1986-12-23 |
IT8712603A0 (en) | 1987-12-16 |
GB2199389B (en) | 1991-07-24 |
CA1317126C (en) | 1993-05-04 |
FI76540C (en) | 1988-11-10 |
FR2608578A1 (en) | 1988-06-24 |
SE8705128D0 (en) | 1987-12-22 |
SE8705128L (en) | 1988-06-24 |
NO875246L (en) | 1988-06-24 |
FR2608578B1 (en) | 1990-12-21 |
GB8728305D0 (en) | 1988-01-06 |
IT1213952B (en) | 1990-01-05 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
NUG | Patent has lapsed | ||
NUG | Patent has lapsed |