GB2094922A - Marine gear system which can be shifted from fast mode operation to slow mode operation - Google Patents

Marine gear system which can be shifted from fast mode operation to slow mode operation Download PDF

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Publication number
GB2094922A
GB2094922A GB8204329A GB8204329A GB2094922A GB 2094922 A GB2094922 A GB 2094922A GB 8204329 A GB8204329 A GB 8204329A GB 8204329 A GB8204329 A GB 8204329A GB 2094922 A GB2094922 A GB 2094922A
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GB
United Kingdom
Prior art keywords
gear system
clutch
shaft
planetary
planetary gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
GB8204329A
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GB2094922B (en
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Renk GmbH
Original Assignee
Renk GmbH
Zahnraederfabrik Renk AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Renk GmbH, Zahnraederfabrik Renk AG filed Critical Renk GmbH
Publication of GB2094922A publication Critical patent/GB2094922A/en
Application granted granted Critical
Publication of GB2094922B publication Critical patent/GB2094922B/en
Expired legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H23/00—Transmitting power from propulsion power plant to propulsive elements
    • B63H23/02—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing
    • B63H23/10—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing for transmitting drive from more than one propulsion power unit
    • B63H23/18—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing for transmitting drive from more than one propulsion power unit for alternative use of the propulsion power units
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/065—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with a plurality of driving or driven shafts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H23/00—Transmitting power from propulsion power plant to propulsive elements
    • B63H23/02—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing
    • B63H2023/0283—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing using gears having orbital motion

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Retarders (AREA)

Abstract

In the kinematic connection between a main driving shaft (1) and an output shaft (3) there is located a clutch (8) whose secondary part (7) is connected to the planet carrier (18) of a planetary gear system (16). The shaft (21) of the sun-wheel (20) of the planetary gear system is driven from an auxiliary motor for low speed operation, and the annular wheel (22) of the planetary gear system can be held stationary with respect to a gear system housing (24) by means of a brake (23). The clutch 8 has teeth 10 engaging teeth 11 of a clutch 38 such that selective operation of these clutches provides forward or reverse drive between the shafts 1 and 3. <IMAGE>

Description

SPECIFICATION Marine gear system which can be shifted from fast mode operation to slow mode operation This invention relates to a marine gear system which can be shifted from a high-speed mode to a low-speed mode, and which comprises a drive shaft, a take-off shaft, a clutch arranged in the kinematic path between these two shafts, and a planetary gear system comprising a sun-wheel, planet wheels, and a planet carrier, with the planet carrier connected to the second part of the clutch.
One such marine gear system is described in German patent specification DE-AS 29 13 385.
There, the drive for fast mode operation and for slow mode operation is effected by a single main motor. In order to switch over, a planetary gear system with two planetary gearsets is provided, with the sun-wheels being capable of being held stationary by brakes and with their annular wheels connected by way of hydraulic coupling members.
Additionally, it is known to use a main motor for high-speed operation and a separate auxiliary motor for low-speed operation, in order to conserve energy and to avoid damage to the main motor by underloading it at low speeds. The propeller shaft of the vessel runs at a considerable reduced efficiency at reduced speeds of rotation in accordance with the laws or propeller design. The power consumption varies approximately with the third power of the speed of rotation.
It is an object of the present invention to produce a gear system which is simple, which is structurally compact and which can be produced economically.
This is achieved in accordance with the present invention, in a gear system of the type first referred to above, in that the sun-wheel of the planecary gear system is arranged to be rotated oy an auxiliary drive shaft which is arranged to be driven by an auxiliary motor for low speed operation, and in which the planetary gear system includes an annular wheel which can be held stationary by a brake.
In one embodiment, the gear system is one in which the secondary part of the clutch and the planet carrier of the planetary gear system are connected to each other by an intermediate shaft which carries a driven pinion for driving a gearwheel on the take-off shaft, and in which the clutch is located on one side of said driven pinion and the planetary gear system is located on the other side of said driven pinion.
According to a preferred embodiment of the invention the planetary gear system comprises two planetary gearsets which are switched in a manner known per se to enable them to be used as a reversible or change-over gear system. This gives rise to the possibility of travelling either ahead or astern in the low-speed mode by means of the auxiliary motor. This can be achieved by a gear system in which the planetary gear system includes a second planetary gearset with the sunwheels of the two planetary gearsets being connected to each other, the annular wheel of the second planetary gearset being connected to the planet carrier of the first planetary gearset, and the planet carrier of the second planetary gearset being capable of being held stationary by a brake.
Preferably, in order to provide a change-over gear system for the main drive, the drive shaft is provided with a drive pinion, a second clutch is provided having a secondary part which is connected kinematically to a gearwheel on the take-off shaft, the primary parts of the two clutches are connected kinematically to each other, and the drive pinion is connected kinematicaily to the primary part of only one of the two clutches.
In order that the invention may be fully understood, two embodiments of marine gear system in accordance with the invention will now be described by way of example and with reference to the accompanying drawings, in which: Fig. 1 is a schematic side view of a first embodiment of marine gear system in accordance with the invention; Fig. 2 is a schematic view of a second embodiment of marine gear system in accordance with the invention; and Fig. 3 is a schematic view of the driving shaft of a main drive provided for the gear system of Fig. 1 or Fig. 2.
The marine gear system shown in Fig. 1 comprises a driving shaft 1 which is powered by a main motor, a driving pinion 2 on the driving shaft, a take-off or driven shaft 3 carrying a gearwheel 4 and leading to the ship's propeller, a driven pinion 5 in meshing engagement with the gearwheel 4 and having an intermediate shaft 6 extending therethrough, one end of the intermediate shaft 6 being connected to the secondary part 7 of a clutch 8 wi ose primary part 9 is provided with external teeth 10 which are in engagement with external teeth 11 on a primary part 39 of a further clutch 38. Further external teeth 12 on the primary part 39 of clutch 38 are in engagement with the driving pinion 2.
On the side of the driven pinion 5 remote from the clutch 8 there is provided a planetary gear system 1 6 of an auxiliary drive comprising a planetary gearset 17, with a planet carrier 18 for the planet wheels 1 9 being connected to the adjacent end of the intermediate shaft 6. A sunwheel 20 is set on an auxiliary driving shaft 21 which is powered from an auxiliary motor which is not shown. An annular wheel 22,of the planetary gearset can be held stationary with respect to a gear system housing 24 by means of a brake 23.
The gear system is designed as a change-over gear system, in which the further clutch 38 has its primary part 39 in engagement with the driving pinion 2 and its secondary part 37 connected by means of an intermediate shaft 36 and a driven pinion 35 to the driven gearwheel 4 on the takeoff shaft 3.
The following operational states are possible: (a) The clutches 8 and 38 are disengaged and the brake is released. Thus there can be not torque transmission to the take-off shaft 3. When the main motor is switched on, the driving pinion 2 rotates only the primary parts 9 and 39 of the clutches 8 and 38 but not the secondary parts.
When the auxiliary motor is switched on, the auxiliary driving shaft 21 rotates the annular wheel 22 as well as the sun-wheel 20 but without entraining the planet carrier 18, so that, again, no torque is transmitted to the take-off shaft 3 from the auxiliary drive.
(b) Clutch 8 is engaged and brake 23 is released, with clutch 38 disengaged. In this case a driving torque is transmitted from the driving pinon 2 to the take-off shaft 3 by way of the clutch 8 and the driven pinion 5.
(c) Both clutches 8 and 39 are disengaged and brake 23 is applied. In this case the annular wheel 22 of the planetary gear system 16 remains stationary and the planet carrier 1 8 is driven by the sun-wheel 20. This causes torque to be transmited from the planet carrier 1 8 to the takeoff shaft 3 by way of the driven pinion 5.
(d) Clutch 38 is engaged, and clutch 8 and brake 23 are disengaged. Now, the take-off shaft 3 is driven from the driving shaft 1 by way of the further clutch 38 and the driven pinion 35 with a reversed direction of rotation as compared with clutch 8 engaged according to operation state (b) above.
The clutches 8 and 38 serve to transmit the comparatively high torque for high speed motion, while the brake 23 and the planetary gear system 1 6 serve to transmit the comparatively smaller torque for low speed motion.
If high speed travel in only one direction is all that is required, then clutch 38 and driven pinion 35 can be omitted. In this case the driving pinion 2 must be brought directly into engagement with the external teeth 10 of clutch 8.
According to a further possibility, the planetary gear system can be mounted on the intermediate shaft 36, instead of on the intermediate shaft 6.
This alternative is shown in Fig. 2.
In the embodiment shown in Fig. 2 those parts which are the same as the corresponding parts in Fig. 1 are shown by the same reference numbers.
In the gear system of Fig. 2 the planetary gearset 1 7 is contained within a planetary gear system 46, and a further planetary gearset 48 is also provided within this system. The two planetary gearsets 1 7 and 48 together form a reversible gear system for the auxiliary drive. In this way, the take-off shaft 3 can be driven at the comparatively low speed of rotation of the auxiliary drive both in a direction of rotation corresponding to the forward movement of the vessel and also in the other direction of rotation corresponding to the astern movement of the vessel. The sun-wheel 20 of the one set 17 is connected by means of a connecting member 49 to the sun-wheel 50 of the other set 48 and thus also to the auxiliary drive shaft 21.The planet carrier 1 8 of the one set 1 7 is connected by way of a connecting member 51 to the annular wheel 52 of the other set 48. The planet carrier 53 of the other set 48 can be held stationary with respect to the gear system casing 24 by means of a brake 54. By applying the brake 23 of the one planetary gearset 17, or by applying the brake 54 of the other planetary gearset 48, the take-off shaft 3 is driven in the one direction of rotation or the other by means of the auxiliary drive from the auxiliary driveshaft 21. The two planetary gearsets 1 7 and 48 together form an independent unit which can be connected in any chosen manner to the main gear system.
In Figures 1 and 2 the clutches 8 and 38 are shown spaced from one another for greater clarity in the drawings. In practice, the tooth rings 10 and 11 of the two toothed clutches 8 and 38 are in meshing engagement with one another. This can be appreciated from Fig. 3. The toothed wheels 10,11 and 12 have to be shown as being of different sizes in order to give a ciear representation of them, although they could equaily well all be the same size.

Claims (5)

1. A marine gear system which can be shifted from a high-speed mode to a low-speed mode, comprising a drive shaft, a take-off shaft, a clutch arranged in the kinematic path between said two shafts, a planetary gear system comprising a sunwheel, planet wheels and a planet carrier, the planet carrier being connected to the secondary part of the clutch, wherein the sun-wheel of the planetary gear system is arranged to be rotated by an auxiliary drive shaft which is arranged to be driven by an auxiliary motor for low-speed operation, and wherein the planetary gear system includes an annular wheel which can be held stationary by a brake.
2. A marine gear system as claimed in claim 1, in which the secondary part of the clutch and the planet carrier of the planetary gear system are connected to each other by an intermediate shaft which carries a driven pinion for driving a gearwheel on the take-off shaft, and in which the clutch is located on one side of said driven pinion and the planetary gear system is located on the other side oi said driven pinion.
3. A marine gear system as claimed in claim 1 or 2, in which the planetary gear system constitutes a reversible gear system for the auxiliary drive, and in which the planetary gear system includes a second planetary gearset with the sun-wheels of the two planetary gearsets being connected to each other, the annular wheel of the second planetary gearset being connected to the planet carrier of the first planetary gearset, and the planet carrier of the second planetary gearset being capable of being held stationary by a brake.
4. A marine gear system as claimed in claim 2 or 3, in which, in order to provide a change-over gear system for the main drive, the drive shaft is provided with a drive pinion, a second clutch is provided having a secondary part which is connected kinematically to a gearwheel on the take-off shaft, the primary parts of the two clutches are connected kinematically to each other, and the drive pinion is connected kinematically to the primary part of only one of the two clutches.
5. A marine gear system substantially as hereinbefore described with reference to Figs. 1 and 3 or Figs. 2 and 3 of the accompanying drawings.
GB8204329A 1981-03-14 1982-02-15 Marine gear system which can be shifted from fast mode operation to slow mode operation Expired GB2094922B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE3109871A DE3109871C2 (en) 1981-03-14 1981-03-14 Marine gear with switching from high speed to slow speed

Publications (2)

Publication Number Publication Date
GB2094922A true GB2094922A (en) 1982-09-22
GB2094922B GB2094922B (en) 1984-09-19

Family

ID=6127263

Family Applications (1)

Application Number Title Priority Date Filing Date
GB8204329A Expired GB2094922B (en) 1981-03-14 1982-02-15 Marine gear system which can be shifted from fast mode operation to slow mode operation

Country Status (5)

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DE (1) DE3109871C2 (en)
ES (1) ES8303218A1 (en)
FR (1) FR2501620B1 (en)
GB (1) GB2094922B (en)
IT (1) IT1153430B (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7384320B2 (en) * 2002-10-31 2008-06-10 Tae-Hwan Ha Power train of a marine transport vessel
ITPC20080032A1 (en) * 2008-07-15 2010-01-16 R T N S R L BRAKING SYSTEM FOR TRANSMISSIONS OF MARINE ENGINES AND TRANSMISSION PROVIDED WITH THIS BRAKING SYSTEM

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3338950A1 (en) * 1983-10-27 1985-05-23 Zahnräderfabrik Renk AG, 8900 Augsburg SHIP TRANSMISSION ARRANGEMENT
DE10005538B4 (en) * 2000-02-08 2009-03-05 Zf Friedrichshafen Ag boot drive
DE102017223424A1 (en) 2017-12-20 2019-06-27 Zf Friedrichshafen Ag Transmission for an outboard drive

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2450214A (en) * 1944-03-27 1948-09-28 Packard Motor Car Co Dual drive mechanism
US3145779A (en) * 1961-07-12 1964-08-25 Wilhelm G Stoeckicht Multi-engine main propulsion gearing arrangements
DE1198233B (en) * 1963-06-29 1965-08-05 Wagner Hochdruck Dampfturbinen Ship propulsion system with several propulsion engines
FR1373635A (en) * 1963-11-12 1964-09-25 Beteiligungs & Patentverw Gmbh Epicyclic gear shift mechanism
FR1377206A (en) * 1963-12-17 1964-10-31 Ass Elect Ind Propulsion transmission of a boat
CH622748A5 (en) * 1977-07-15 1981-04-30 Maag Zahnraeder & Maschinen Ag
DE2758555C2 (en) * 1977-12-23 1980-01-03 Mannesmann Ag, 4000 Duesseldorf Two-stage gearbox for driving a generator from a ship propulsion system
DE2913375C2 (en) * 1979-03-30 1981-03-26 Mannesmann AG, 40213 Düsseldorf The ship's gearbox can be switched from cruising to slow speed

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7384320B2 (en) * 2002-10-31 2008-06-10 Tae-Hwan Ha Power train of a marine transport vessel
ITPC20080032A1 (en) * 2008-07-15 2010-01-16 R T N S R L BRAKING SYSTEM FOR TRANSMISSIONS OF MARINE ENGINES AND TRANSMISSION PROVIDED WITH THIS BRAKING SYSTEM

Also Published As

Publication number Publication date
DE3109871C2 (en) 1986-03-13
ES509831A0 (en) 1983-02-01
GB2094922B (en) 1984-09-19
DE3109871A1 (en) 1982-10-14
ES8303218A1 (en) 1983-02-01
FR2501620A1 (en) 1982-09-17
FR2501620B1 (en) 1985-11-08
IT1153430B (en) 1987-01-14
IT8219709A0 (en) 1982-02-17

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PCNP Patent ceased through non-payment of renewal fee