GB1575060A - Reversing transmission gear - Google Patents

Reversing transmission gear Download PDF

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Publication number
GB1575060A
GB1575060A GB2761777A GB2761777A GB1575060A GB 1575060 A GB1575060 A GB 1575060A GB 2761777 A GB2761777 A GB 2761777A GB 2761777 A GB2761777 A GB 2761777A GB 1575060 A GB1575060 A GB 1575060A
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GB
United Kingdom
Prior art keywords
input
shaft
transmission gear
clutch
gearwheels
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.)
Expired
Application number
GB2761777A
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ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen 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 ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Priority to GB2761777A priority Critical patent/GB1575060A/en
Publication of GB1575060A publication Critical patent/GB1575060A/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
    • B63H23/08—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing with provision for reversing 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
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/14—Gearings for reversal only

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Gear Transmission (AREA)

Description

(54) REVERSING TRANSMISSION GEAR (71) We, ZAHNRADFABRIK FRIEDRICH SHAFEN AKTIENGESELLSCHAFT, of Friedrichshafen-on-the-Bodensee, Federal Republic of Germany, a Joint-Stock Company organised under the laws of the Federal Republic of Germany, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement:- This invention relates to a reversing transmission gear, such as is used particularly in marine propulsion units.
In known reversing transmission gears (German Published Patent Specifications 2,059,820 and 2,358,778), particularly in marine propulsion units, an output shaft is inclined relative to an input shaft and an intermediate shaft. A bevel gearwheel on the inclined output shaft meshes with a spur pinion on the input shaft and with a preferably bevel pinion on the intermediate shaft, the latter being connected to the input shaft by way of another pair of gearwheels. Depending on the desired direction of travel the output shaft is driven by one or the other of the two pinions.
In marine drives it is often expedient for the drive unit to be accommodated as far back as possible in the stern of the ship. At the same time the overall height of the drive unit should be kept as low as possible. A drive unit may have an engine having a deep or a shallow oil sump.
Depending on installation conditions, such as the shape of the stern of the ship, and depending on the shape of the oil sump, a space-saving arrangement comprises either a transmission gear having parallel input and output shafts or a transmission gear having input and output shafts inclined relative to one another. According to the prior art, these two possible arrangements can be achieved only with the aid of two fundamentally different transmission gears, which entail doubled expense for design and manufacture.
The invention aims at providing a transmission gear which by a slight modification can be used either as a parallel-axis or as an inclined-axis transmission gear, depending on requirements. The transmission gears should substantially comprise identical components, in order to obtain the desired variant rapidly and economically.
Accordingly, the present invention consists in a reversing transmission gear, comprising a two-part casing of which one part is selectively exchangeable, an input shaft, an output shaft, an intermediate shaft rotatably mounted in said casing, an input journal and five gearwheels, one gearwheel being provided on the output shaft and being in constant mesh with second and third gearwheels respectively provided on the other two shafts which second and third gearwheels are selectively operable by respective clutches to transmit power to said output shaft, the input (or intermediate) shaft being inclined and the intermediate (or input) shaft being parallel relative to the output shaft, said input journal being selectively mountable, with the fourth or the fifth gearwheels and with one or the other of the two clutches, both on the input (or intermediate) shaft and also on the intermediate (or input) shaft, by utilising the appropriate exchangeable casing part.
The transmission gear of the invention makes it possible for both variants to be achieved by using the same components, with the exception of the casing part at the input end. By virtue of the arrangement of the three shafts according to the invention, wherein the output shaft is parallel to one shaft and inclined relative to the other, it is made possible to drive selectively through one shaft or the other and thus to obtain an output which is parallel or inclined in relation to the input shaft. The inclination of one shaft in relation to the other two is preferably achieved by using beveloid teeth, which are preferably provided on all five gearwheels. However, fewer than five, but at least two bevel gearwheels, may have beveloid teeth, while the other gearwheels have involute gear teeth.
From German Published Patent Specification 1,909,414 a transmission gear is known in which the input shaft and intermediate shaft together with the parts associated with them can be transposed in order to achieve a more advantageous alignment of the transmission gear. In this case, however, the two shafts are parallel to one another, so that the position of the output relative to the drive shaft remains the same, that is to say parallel.
A marine transmission gear ("Motortechnische Zeitschrift" 35 (1974) 11, Page 382) is also known in which the output shaft is inclined in relation to one of the remaining shafts and parallel to the other shaft, one of the two shafts being the input shaft and the other the intermediate shaft.
However, this known transmission gear has no reversing means, nor is it possible for the transmission gear to be used selectively with a parallel or angular output by transposing the input and intermediate shafts.
In order that the invention may be more readily understood, reference is made to the accompanying drawings which illustrate diagrammatically and by way of example embodiments thereof, and in which: Fig. 1 shows a diagram of the arrangement of the shafts of the transmission gear according to the invention Fig. 2 is a section through a transmission gear according to the invention, with the output shaft inclined relative to the input shaft, in a first- embodiment, Fig. 3 is a diagrammatical representation of the transmission gear shown in Fig. 2, Fig. 4 is a diagrammatical representation of a transmission gear according to the invention with an output shaft inclined relative to the input shaft, in a second embodiment, Fig. 5 is a diagrammatical side view of the transmission gear according to the invention, Fig. 6 is a diagrammatical representation of a transmission gear of the invention, with parallel input and output shafts, Fig. 7 shows an example of the installation of a drive unit having a transmission gear according to the invention, in which the input and output shafts are parallel to one another, and Fig. 8 shows another example of installation of a drive unit in which the input and output shafts are inclined relative to one another.
In Figs. 2, 3, 4 and 8, reference numeral 1 designates a transmission gear according to the invention which has input and output shafts inclined relative to one another, reference numeral 2 in Fig. 8 designating a constructionally identical transmission gear having parallel input and output shafts.
The construction of the transmission gear will be described more particularly with reference to the transmission gear having input and output shafts inclined in relation to one another.
As can be seen in Fig. 1, an output shaft 10 is inclined relative to an input shaft 20, with the axes of the shafts lying in the same plane 9. An intermediate shaft 30, the axis of which is situated outside the plane 9, is arranged with its axis parallel to the axis of the output shaft 10 and at the same time inclined to the axis of the input shaft 20.
Fig. 2 shows a bevel gearwheel 22 rotationally fast with the input shaft 20 and provided at one end with an input journal 23, while at the other end it is equipped in known manner with a friction disc clutch 24. In this arrangement the outer part (driver) of the clutch may be detachably connected to the gearwheel 22 by screws or constitute a non-detachable part of the gearwheel 22. A bevel pinion 21 is mounted on the input shaft 20 so as to be freely rotatable but axially immoveable thereon.
The gearwheel 22 meshes with a reversing spur gearwheel 32 keyed to an intermediate shaft 30. The reversing spur gearwheel 32 incorporates a friction disc clutch 34, and is in other respects identical in construction to the gearwheel 22 except for the absence of an input journal. The intermediate shaft 30 further carries a spur-toothed pinion 31, which is mounted on the shaft 30 in The same manner as the pinion 21 is mounted on the shaft 20. The two pinions 21 and 31 mesh, separated from one another, with a spur gearwheel 11 keyed to the output shaft 10 and secured against axial sliding thereon (Fig. 5).
The transmission gearing is arranged in a casing which comprises a casing part 5 on the output side -and a selectively exchangeable casing part 6 or 7 on the input side. The shafts 20 and 30 are mounted in a similar manner in the gear casing, - that is to say directly by means of appropriate bearings on the output side, while on the input side these shafts are supported in the gearwheels 22 and 32 respectively, which in turn are mounted by means of appropriate bearings in the casing part 6 or 7. The output shaft 10 is supported by means of bearings in the two casing parts 5 and 6 or 7.
Fig. 4 shows another embodiment of the invention. The two clutches 24 and 34 of Figs. 2 and 3 are replaced by one double clutch 25. The clutch casing or outer part is rotationally fast with the input 20 shaft ,while the gearwheel 22 and the pinion 21 are freely rotatably mounted on the shaft 20 and rotationally fast with the inner discs of the clutch. The reversing gearwheel 32 and the pinion 31 are rotationally fast with the intermediate shaft 30 and secured thereon against axial sliding.
Since in the embodiment shown in Fig.
3 the shafts 20 and 30, their mountings, and the components mounted on them are identical in construction, by transposing the gearwheels 32 and 22 with or without the outer drivers of the appertaining clutches depending on whether a detachable or non-detachable connection exists between the driver and the gearwheel, it is possible by using a different casing part 7, on the input side and appropriately turning the transmission gear through an angle (Fig. 5) for the intermediate shaft 30 to serve as input shaft and conversely for the input shaft 20 to serve as intermediate shaft, as shown in Fig. 6. A transmission gear having parallel input and output shafts is obtained.
A driving unit may have an engine having a deep oil sump 3 or an engine having a shallow oil sump 4. Depending on the installation conditions existing, a transmission gear 2 (Fig. 6) having parallel input and output shafts or a transmission gear 1 (Figs. 2 to 5) having input and output shafts inclined relative to one another, in conjunction with the associated engine 3 or 4, is the space-saving arrangement which is shown in full lines in Figs. 7 and 8, while the space-consuming arrangement is shown in broken lines.
By using beveloid teeth known per se for the gearwheels of the transmission gear the inclination of the input shaft 20 relative to the other two shafts 10 and 30, which together with the exchangeability of the gearwheels permit the versatile utilisation of the transmission gear, can be achieved without problems. All five gearwheels may have beveloid teeth. At least two of the gear wheels, the reversing gear wheel 32 and the pinion 21, should have beveloid teeth, while the remaining three wheels may have involute teeth.
The transmission gear of the invention.
operates in the following manner: If, for example, with a transmission gear having input and output shafts inclined relative to one another as shown in Fig. 3 the trans mission gear is to rotate in the opposite direction to the engine, the clutch 24 is engaged while the clutch 34 is disengaged.
The output shaft 10 is driven by the input journal 23, the shaft 20, the clutch 24, the pinion 21, and the gearwheel 11.
If it is desired to achieve rotation in the same direction as the engine, the clutch 34 is engaged while at the same time the clutch 24 is disengaged. The output shaft 10 is now driven by the input journal 23 by way of the shaft 20, the gearwheel 22, the reversing gearwheel 32, the clutch 34, the pinion 31, and the gear wheel 11.
In the case of the transmission gear having parallel input and output shafts inclined relative to one another and having a double clutch, as illustrated in Fig. 4, for rotation in the opposite direction to the driving engine, the clutch half 25a of the clutch 25 is engaged and thus the output shaft 10 is driven by the input journal 23 by way of the gearwheel 11, pinion 21, clutch 25, and input shaft 20. For rotation in the same direction as the engine, the clutch half 25b is engaged, while at the same time the clutch half 25a is disengaged. The output shaft 10 receives its rotational movement from the input journal 23 via the gearwheel 11, pinion 31, reversing gearwheel 32, gearwheel 22, clutch 25b, and input shaft 20.
WHAT WE CLAIM IS: 1. A reversing transmission gear, comprising a two-part casing of which one part is selectively exchangeable, an input shaft, an output shaft, an intermediate shaft rotatably mounted in said casing, an input journal and five gearwheels, one gearwheel being provided on the output shaft and being in constant mesh with second and third gearwheels respectively provided on ttle other two shafts which second and third gearwheels are selectively operable by respective clutches to transmit power to said output shaft, the input (or intermediate) shaft being inclined and the intermediate (or input) shaft being parallel relative to the output shaft, said input journal being selectively mountable, with the fourth or the fifth gearwheels and with one or the other of the two clutches, both on the input (or intermediate) shaft and also on the intermediate (or input) shaft, by utilising the appropriate exchangeable casing part.
2. A reversing transmission gear according to claim 1, wherein all said five gearwheels have beveloid teeth.
3. A reversing transmission gear according to claim 1, wherein only two of the five gearwheels namely one of the fourth and fifth gearwheels and one of the second and third gearwheels, have beveloid teeth, while the remaining three gearwheels have
**WARNING** end of DESC field may overlap start of CLMS **.

Claims (4)

  1. **WARNING** start of CLMS field may overlap end of DESC **.
    Fig. 4 shows another embodiment of the invention. The two clutches 24 and 34 of Figs. 2 and 3 are replaced by one double clutch 25. The clutch casing or outer part is rotationally fast with the input 20 shaft ,while the gearwheel 22 and the pinion 21 are freely rotatably mounted on the shaft
    20 and rotationally fast with the inner discs of the clutch. The reversing gearwheel 32 and the pinion 31 are rotationally fast with the intermediate shaft 30 and secured thereon against axial sliding.
    Since in the embodiment shown in Fig.
    3 the shafts 20 and 30, their mountings, and the components mounted on them are identical in construction, by transposing the gearwheels 32 and 22 with or without the outer drivers of the appertaining clutches depending on whether a detachable or non-detachable connection exists between the driver and the gearwheel, it is possible by using a different casing part 7, on the input side and appropriately turning the transmission gear through an angle (Fig. 5) for the intermediate shaft 30 to serve as input shaft and conversely for the input shaft 20 to serve as intermediate shaft, as shown in Fig. 6. A transmission gear having parallel input and output shafts is obtained.
    A driving unit may have an engine having a deep oil sump 3 or an engine having a shallow oil sump 4. Depending on the installation conditions existing, a transmission gear 2 (Fig. 6) having parallel input and output shafts or a transmission gear 1 (Figs. 2 to 5) having input and output shafts inclined relative to one another, in conjunction with the associated engine 3 or 4, is the space-saving arrangement which is shown in full lines in Figs. 7 and 8, while the space-consuming arrangement is shown in broken lines.
    By using beveloid teeth known per se for the gearwheels of the transmission gear the inclination of the input shaft 20 relative to the other two shafts 10 and 30, which together with the exchangeability of the gearwheels permit the versatile utilisation of the transmission gear, can be achieved without problems. All five gearwheels may have beveloid teeth. At least two of the gear wheels, the reversing gear wheel 32 and the pinion 21, should have beveloid teeth, while the remaining three wheels may have involute teeth.
    The transmission gear of the invention.
    operates in the following manner: If, for example, with a transmission gear having input and output shafts inclined relative to one another as shown in Fig. 3 the trans mission gear is to rotate in the opposite direction to the engine, the clutch 24 is engaged while the clutch 34 is disengaged.
    The output shaft 10 is driven by the input journal 23, the shaft 20, the clutch 24, the pinion 21, and the gearwheel 11.
    If it is desired to achieve rotation in the same direction as the engine, the clutch 34 is engaged while at the same time the clutch 24 is disengaged. The output shaft 10 is now driven by the input journal 23 by way of the shaft 20, the gearwheel 22, the reversing gearwheel 32, the clutch 34, the pinion 31, and the gear wheel 11.
    In the case of the transmission gear having parallel input and output shafts inclined relative to one another and having a double clutch, as illustrated in Fig. 4, for rotation in the opposite direction to the driving engine, the clutch half 25a of the clutch 25 is engaged and thus the output shaft 10 is driven by the input journal 23 by way of the gearwheel 11, pinion 21, clutch 25, and input shaft 20. For rotation in the same direction as the engine, the clutch half 25b is engaged, while at the same time the clutch half 25a is disengaged. The output shaft 10 receives its rotational movement from the input journal 23 via the gearwheel 11, pinion 31, reversing gearwheel 32, gearwheel 22, clutch 25b, and input shaft 20.
    WHAT WE CLAIM IS: 1. A reversing transmission gear, comprising a two-part casing of which one part is selectively exchangeable, an input shaft, an output shaft, an intermediate shaft rotatably mounted in said casing, an input journal and five gearwheels, one gearwheel being provided on the output shaft and being in constant mesh with second and third gearwheels respectively provided on ttle other two shafts which second and third gearwheels are selectively operable by respective clutches to transmit power to said output shaft, the input (or intermediate) shaft being inclined and the intermediate (or input) shaft being parallel relative to the output shaft, said input journal being selectively mountable, with the fourth or the fifth gearwheels and with one or the other of the two clutches, both on the input (or intermediate) shaft and also on the intermediate (or input) shaft, by utilising the appropriate exchangeable casing part.
  2. 2. A reversing transmission gear according to claim 1, wherein all said five gearwheels have beveloid teeth.
  3. 3. A reversing transmission gear according to claim 1, wherein only two of the five gearwheels namely one of the fourth and fifth gearwheels and one of the second and third gearwheels, have beveloid teeth, while the remaining three gearwheels have
    involute teeth.
  4. 4. A reversing transmission gear, sub stantially as herein described with reference 5 to and as shown in the accompanying drawings.
GB2761777A 1977-07-01 1977-07-01 Reversing transmission gear Expired GB1575060A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
GB2761777A GB1575060A (en) 1977-07-01 1977-07-01 Reversing transmission gear

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB2761777A GB1575060A (en) 1977-07-01 1977-07-01 Reversing transmission gear

Publications (1)

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GB1575060A true GB1575060A (en) 1980-09-17

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2576072A1 (en) * 1985-01-14 1986-07-18 Kanzaki Kokyukoki Mfg Co Ltd REVERSIBLE CLUTCH ASSEMBLY FOR THE MARINE
EP0205111A1 (en) * 1985-06-12 1986-12-17 M.P.M. MECCANICA PADANA MONTEVERDE S.p.A. Drive transmission unit
GB2261199A (en) * 1991-10-18 1993-05-12 Dana Corp Angled vehicle axle assembly.

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2576072A1 (en) * 1985-01-14 1986-07-18 Kanzaki Kokyukoki Mfg Co Ltd REVERSIBLE CLUTCH ASSEMBLY FOR THE MARINE
EP0205111A1 (en) * 1985-06-12 1986-12-17 M.P.M. MECCANICA PADANA MONTEVERDE S.p.A. Drive transmission unit
GB2261199A (en) * 1991-10-18 1993-05-12 Dana Corp Angled vehicle axle assembly.
GB2261199B (en) * 1991-10-18 1995-03-22 Dana Corp Angled vehicle axle assembly

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PS Patent sealed
PCNP Patent ceased through non-payment of renewal fee