US3872675A - Propulsion installations for boats, more particularly for high-speed launches - Google Patents

Propulsion installations for boats, more particularly for high-speed launches Download PDF

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Publication number
US3872675A
US3872675A US289264A US28926472A US3872675A US 3872675 A US3872675 A US 3872675A US 289264 A US289264 A US 289264A US 28926472 A US28926472 A US 28926472A US 3872675 A US3872675 A US 3872675A
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Prior art keywords
reduction gear
gear mechanism
shaft
input shaft
power unit
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US289264A
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English (en)
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Felix Amiot
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Individual
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    • 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19014—Plural prime movers selectively coupled to common output

Definitions

  • ABSTRACT The specification discloses a very compact installation for a high-speed launch, such installation comprising a main internal combustion power unit and an auxiliary power unit, each unit having a drive shaft extending into a reduction gear mechanism which also has an output shaft driving a screw, the reduction gear mechanism being arranged so that the auxiliary power unit can selectively either (a) drive water and oil pumps of the main power unit to preheat the unit, (b) drive the main power unit to start the same, or (c) drive the screw during low speed manoeuvres.
  • This invention relates to propulsion installations for boats, of the type which develop a relatively high power (above 1,000 HP. and up to 10,000 HP, and even several tens of thousands horse-power); the invention relates more particularly because this would appear to be the most advantageous application but not exclusively to propulsion installations of this type intended for high-speed launches or patrol-boats, i.e., boats requiring powerful propulsion installations with only limited space available for their accommodation.
  • Boat propulsion installations of this type generally comprise, inter alia, a power unit coupled to a reduction gear mechanism, the output shaft of which is coupled to a propulsion means such as a screw, the power unit being equipped with auxiliaries, some of which are pumps (cooling liquid pumps, lubricating pumps), which contribute more particularly by their operation to bringing the power unit up to the required operating temperature during the time from the start order until the operation of the main engines at the required temperature.
  • auxiliaries some of which are pumps (cooling liquid pumps, lubricating pumps), which contribute more particularly by their operation to bringing the power unit up to the required operating temperature during the time from the start order until the operation of the main engines at the required temperature.
  • Propulsion installations of this kind should advantageously satisfy in the best possible way a number of criteria, some of which are mechanical, others of a marine nature while yet others are of an economic nature or tactical or strategic in the case of propulsion installations for naval vessels (i.e., particularly high-speed surveillance and attack launches).
  • a power unit a reduction gear mechanism; a primary input shaft of the reduction gearmechanism drivingly connected with said power unit; an output shaft of the reductiongear mechanism arranged to drive prop ulsion means; wherein the improvement comprises the provision of:
  • an auxiliary engine a secondary input shaft of the reduction-gear mechanism arranged to be driven by the auxiliary engine; means to decouple the said output shaft from the primary input shaft; said reduction gear mechanism including means to drivingly connect the secondary power input shaft to the output shaft with such output shaft decoupled from the primary input shaft; and means including a freewheel device to drivingly connect the secondary power input shaft to the primary input shaft for starting of the power unit, said freewheel device permitting transmission of torque from the secondary power input shaft to the primary power input shaft to rotate a shaft of the power unit in the direction in which such shaft is rotated for starting of the power unit.
  • the installation power unit comprises a plurality of engine units coupled respectively to as many input shafts provided for this purpose in the reduction gear mechanism
  • the gear train and the coupling means of the said reduction gear mechanism are so arranged for starting as to allow the user selectively to couple the power take-off shaft driven by the auxiliary engine to any ofthe input shafts associated with the said engine units so that the engine units in question can then be started successively.
  • the reduction gear mechanism comprises for the purposes of starting one or other of the said engine units, a transmission mechanism comprising gearwheels mounted on a rocking support which can be brought from a neutral position into one or other oftwo end positions in which one of two output gearwheels of the said transmission mechanism meshes with one or other of the starting means for the said engine units.
  • the main feature of the invention enables the auxiliary engine associated with the propulsion installation to perform a double role, i.e., enables the auxiliary engine to carry out the harbour manoeuvres on its own and carry out starting of the power unit of the propulsion installation at the required time.
  • the marine propulsion installation according to the invention may also have other advantages by applying to it, in addition to the main feature above, one or more of the following additional features which form part of the invention and which will now be discussed more exp QitlX-
  • the gear train and transmission means of the reduction gear mechanism are also so arranged as to allow selective coupling of the power take-off shaft driven by the auxiliary engine to some or all of the accessories of the power unit (more particularly lubricant and cooling liquid pumps) which, by their operation, are adapted to assist the power unit in running up to temperature, this first additional arrangement allowing the auxiliary engine provided in the propulsion installation to perform a third beneficial role.
  • the said auxiliaries are driven at areduced speed in relation to their normal operating speed.
  • auxiliaries of the power unit are borne by the reduction gear mechanism and driven by the latter, thus facilitating their inspection and maintenance, simplifying their drive system and making any repairs more convenient.
  • the reduction gear mechanism of the installation comprises a casing having a joint plane at the level of each input or output shaft leading to the said reduction gear mechanism so that it is a simple matter to expose and repair at each of its levels the essential components of the power transmission at the level in question, inspection bellhousings or covers advantageously being provided in the walls of the said casing at the end of each line of shafting, said bell-housings or covers straddling the joint planes of the casing and, in the casing of bellhousings, also protecting some of the components of the reduction gear mechanism.
  • FIG. 1 is a highly diagrammatic perspective view of the essential elements of a propulsion installation according to the invention for a high-speed launch, said installation comprising a power unit consisting of two superposed engine units;
  • FIGS. 1a and lb are more detailed perspective views respectively in right-hand and left-hand three-quarter view showing a reduction gear mechanism belonging to this installation;
  • FIG. 2 is a perspective view of the complete gear train and transmission and coupling elements housed in the casing of the said reduction gear mechanism;
  • FIGS. 2a and 2b are elevations of two transverse lines of shafting of the reduction gear mechanism corresponding respectively to the bottom engine unit and the top engine unit of the installation power unit;
  • FIGS. to 2 fillustrate details of FIG. 2 respectively in the direction of the arrows F0 to Ff;
  • FIG. 2g is a section of the said reduction gear mechanism in elevation
  • FIG. 2h is a similar view to FIG. 2 and bears the reference of all the internal components of the reduction gear mechanism;
  • FIG. 3 shows in the same conditions the same elements of the reduction gear mechanism as FIG. 2, but the in this FIG. 3 double arrows show those of the said elements which are in motion during the preheating procedure of the power unit;
  • FIG. 4 is a similar view to FIG. 3 except that double arrows show the elements which are in motion on a harbour manoeuvre accompanied by simultaneous preheating of the power unit;
  • FIG. 4a is a similar view to FIG. 4 but differs from FIG. 4 in that further double arrows show the elements which are in movement in a harbour manoeuvre carried out without preheating of the power unit;
  • FIG. 5 is a similar view to FIG. 3 except that double arrows show the elements which are in movement during starting of the top engine unit of the power unit;
  • FIG. 6 a view similar to FIG. 5 but differs from FIG. 5 in that double arrows show the elements which are in movement on starting of the bottom engine unit of the power unit;
  • FIG. 7 a similar view to FIG. 3 but differs from FIG. 3 in that further double arrows show the elements shaded grey are those which are in motion when the two engine elements of the power unit are in operation;
  • FIGS. 8 and 9 are views similar to those above wherein double arrows indicate the components in motion illustrating, respectively, propulsion of the boat by the bottom engine unit on its own and by the top engine unit on its own, and
  • FIG. 10 differs from FIG. 9 only in that the bottom engine element is not only stopped but also under repair
  • the high-speed launch propulsion installation shown diagrammatically in FIG. 1 comprises essentially a drive unit 1 formed from two superposed engine units 10 and 1b each having their own output shaft 20 and 2b respectively; a reduction gear mechanism 3 to which the output shafts 2a and 2b of the engine units la and lb are coupled, and a single output shaft 4 of which is coupled to the installation screw shaft 4a, preferably through a resilient coupling system; an auxiliary engine 5 coupled, for example via cardan shaft 6, to a power input shaft or secondary power shaft 6a which extends to the interior of the reduction gear mechanism 3; and a number of accessories, including accessories for bringing the power unit 1 to operating temperature, comprising, in the case of each engine unit, at least one cooling freshwater pump 7 and at least one circulating and lubricating oil pump 8, all these pumps being carried and driven by the reduction gear mechanism 3.
  • the engine unit 1 is preferably constructed in accordance with the French Pat. application filed by the same applicant on 23rd Aug., 1971 under the number 7l-30,52l for Improvements in and relating to propulsion installations for vehicles or vessels, more particularly for boats, new French Pat. No. 2,151,163 the said power unit then being formed from two superposed diesel engine units la and lb with turbocompressors and each comprising ten pairs of horizontal opposed cylinders. In these conditions each engine unit can develop a power of the order of 4,000 to 5,000 HP.
  • the auxiliary engine 5 is preferably a diesel piston engine of a power of the order of 200 to 300 H.P., and this auxiliary engine may also be used if required to drive an electrical generator feeding the auxiliary equipment.
  • the reduction gear 3 which is shown in perspective at two different angles in FIGS. 1a and lb, comprises generally a casing 9 formed from four superposed elements which are connected detachably in three horizontal joint planes p (FIG. la), which from top to bottom are respectively situated at the level of the line of shafting L2b of the top element, L2a of the bottom engine unit and L4 of the reduction gear output.
  • the driving torque produced by the bottom engine unit la and collected at the output shaft 2a of the said engine unit is transmitted through a releasable coupling device a to a first input shaft 2a1 belonging to the line of shafting L2a and entering the reduction gear casing 9.
  • the driving torque produced by the top engine unit 1b and collected from the output shaft 2b of said engine unit is transmitted via a doubletoothing coupling 10b similar to coupling 10a to a second input shaft 2b1 belonging to the line of shafting L2b and entering the reduction gear casing 9.
  • a control box 11 is provided at the end of the shafting line L4 for varying the pitch of the boat screw.
  • Detachable bell housings or covers co-axial with the shafting lines are also provided for ease ofremoval and installation on the lateral walls of the casing 9 through which the lines of shafting extend, and the following are examples of these:
  • a general structure of this kind for the reduction gear mechanism 3 makes inspection and any repaid of the internal elements of the mechanism very simple and rapid for the following reasons:
  • coupling 10b is decoupled and bell 13b and cover 12b are removed, whereupon the fixing elements of the top element of the casing 9 are removed to release the said top element in the upward direction, access then being possible from the top to the interior of the reduction gear mechanism at the line of shafting L2b.
  • FIGS. 2 and 2a to 2b generally and, initially, more particularly to FIG. 2g.
  • the top input shaft 2b drives a rotary coupling 16b and through this a shaft 17b extending into the bell 13b and bearing, inside said bell 13b, a clutch device 18b lockable in the engaged position by means of a dog clutch system 19b provided at the shaft end.
  • the driven, i.e. output part of the clutch 18b is connected to a tubular shaft 20b on which is secured a gearwheel 21b meshing with an identical gearwheel 21a which will be discussed hereinafter.
  • the bottom input shaft 211 drives a resilient angular coupling 16a and, through the agency thereof, a shaft 17a extending as far as the bell 13a and bearing inside the latter a clutch device 18a which can be locked in the engaged position by a dog clutch system provided at the end of the shaft.
  • the driven, i.e., output part of the clutch 18a is connected to a.tubular shaft 20a to which there are secured the gearwheel 21a mentioned above and a gearwheel 22 meshing with the gearwheel 23 ekeyed on the output shaft 4 of the reduction gear (screw shaft line L4).
  • the said reduction gear comprises a number of auxiliary elements which have been referred to hereinbefore, and which are used during preheating of the power unit, during starting of the power unit, and during manoeuvres of the craft as low speed at ports. These other elements are controlled by the auxiliary engine 5 through the agency of the secondary input shaft 6a.
  • the secondary input shaft 6a drives the following:
  • the top transverse shaft 27b bears the driving part of a dog clutch 30b, the driven part of which is connected to a shaft 31b extending through the tubular shaft 27b and bearing the freshwater pump 7b at one end and the oil pump 8b at its other end, these two pumps being associated with the top engine unit lb.
  • a second dog clutch 32b is provided on the same transverse line of shafting and is combined with the dog clutch 30b so that when one of these two dog clutches is in the operative position the other dog clutch is in the disengaged position, a neutral position in which both dog clutches are disengaged being provided in the control system for such dog clutches.
  • the driven part of the dog clutch 32b is connected to a tubular shaft 33b co-axial with shaft 31b and driving a bevel gear 34b which will be discussed hereinafter.
  • the bottom transverse shaft 27a is associated with elements identical to those described in connection with the top transverse shaft 27b, i.e., a dog clutch 30a, shaft 31a, a freshwater pump 7a, an oil pump 8a (these two pumps being associated with the bottom engine unit la), a second dog clutch 32a combined with the dog clutch 30a, and a tubular shaft 330 driving a bevel gear 34a which will also be discussed hereinafter.
  • the bottom transverse shaft 27a is also coupled by a bevel gearwheel 35 meshing with the bevel gearwheel arrangement 29a to a vertical shaft 36 driving a secondary pump 37 for recovery of oil from the bottom of the reduction gear casing when only the auxiliary engine is in operation and, through a gearwheel 38, to a vertical shaft 39 driving a main pump 40 for drawing oil from the bottom of the reduction gear casing if at least one of the engine units laand lb is in operation.
  • the driven gearwheel of the bevel gear 34b (see more particularly FIGS. 2e and 211) is secured on a shaft 41 connected to a gearwheel 42 meshing with a gearwheel 43 connected to another larger-diameter gearwheel 44 meshing with a gearwheel 45 meshing with the power take-off gearwheel 25b already mentioned and belonging to the line of shafting L2b, the shaft of the gearwheel 44 rotating a fuel circulating pump associated with the top engine unit.
  • the driven gearwheel of the bevel gear 34a is secured on a shaft 46 connected to a gearwheel 47 meshing with a gearwheel 48 connected to another largerdiameter gearwheel 49 meshing with the power takeoff gearwheel 25a already mentioned and belonging to the line of shaftinf L2a, the shaft of the gearwheel 49 rotating a fuel circulating pump associated with the bottom engine unit.
  • the reduction gear 3 also comprises (FIGS. 2d
  • the gearing of the reduction gear is completed by a three-position transmission device or quadrant of the type which can pass from a neutral position to one or other of two end positions corresponding to coupling of the vertical shaft 28 (which is adapted to be driven by the auxiliary engine 5) to respectively the starting gearwheel 24a or the starting gearwheel 24b.
  • This transmission device (FIGS. 20 and 211) comprises a bevel gear 56, the driving gearwheel of which is secured to the vertical shaft 28 and the driven gearwheel of which is secured to a shaft 57 on which the driving part of a dog clutch 58 is secured for rotation, the driven part of the dog clutch 58 being connected to a tubular shaft 59 surrounding the shaft 57 and bearing at its end a gearwheel 60, the shaft of which forms the pivot for the support 61 of the quadrant of the gearing, of which the gearwheel is the input gearwheel.
  • the gearing also comprises a gearwheel 62 meshing with gearwheel 60 and comprising a freewheel (the direction of which will be adapted to the starting problem to be solved), the driven part of which is connected to a gearwheel 63 meshing with a gearwheel 64 connected for rotation to a smaller-diameter gearwheel 65 meshing with an identical gearwheel 66.
  • the support 61 For starting the bottom engine unit 1a, the support 61 is moved downwardly and the output gearwheel of the three-position transmission is the gearwheel 65 which then engages with the starting gearwheel 24b.
  • control systems which have been omitted from the drawing for clarity, and these control systems may be of a conventional type, for example hydraulic.
  • FIGS. 3 to 10. which have been made identical as regards the relative positions of the elements'(for simplification purposes), but in which those elements which are in motion have been indicated using double arrows and been given their reference numeral in order to distinguish the various stages of operation.
  • the operations carried out on the dog clutches or clutches will also be indicated hereinafter in connection with each Figure.
  • the boat is at the quayside with the power unit cold.
  • a special heating installation (for example an electrical heating installation) is provided to heat the freshwater and oil involved in the propulsion installation. All the clutches and dog clutches of the reduction gear and of the three-position transmission are assumed to be in the neutral position.
  • Auxiliary engine 5 is started if it has not already been started for other purposes.
  • Dog clutches 30a and 30b are brought into the operative position.
  • Clutch 26 of auxiliary engine is brought into operative position.
  • clutch 26 is disengaged and when the gearhweels have stopped dog clutche 53 is engaged, and then clutch 26 is engaged so that while preheating is restored the gearwheel 21a coupled to the screw shaft is driven and thus receives all the power of the auxiliary engine but rotates at a reduced speed because of the internal step-down ratios of the reduction gear.
  • the screw pitch is initially set to zero and is progressively brought to a suitable intermediate value.
  • top engine unit lb is to be started first, preheating of the engine unit having been completed.
  • the screw is reset to zero pitch.
  • Clutch 26 is disengaged to stop the gearing.
  • Dog clutches 30b and 32a are brought into the operative position as is also dog clutch 58 which controls all the gearing in the three-position transmission 61.
  • the three-position transmission 61 is swung up to couple gearwheel 66 to starting gearwheel 24b.
  • Clutch 26 is engaged gently by successive pulses.
  • dog clutch 30b is disengaged by engaging dog clutch 32b.
  • Clutch 18b is brought into the operative position to ensure effective starting of top engine unit, the freewheel of gearwheel 62 then coming into operation, and then the three-position transmission 61 is returned to the neutral position.
  • the screw is reset to zero pitch clutch 26 is disengaged to stop the gearing controlled by the auxiliary engine
  • the dog clutches 30a and 32b are brought into the operative position as is also the dog clutch 58 controlling all the gearing of the three-position transmission device 61
  • the device 61 is swung down to couple the gearwheel 65 to the starting gearwheel 24a
  • clutch 26 is engaged gently by successive pulses
  • the gearwheel 24a has started the dog clutch 30a is disengaged by engaging the dog clutch 320
  • the clutch 18a is brought into the operative position so as to ensure effective starting of the bottom engine unit, the freewheel of the gearwheel 62 then coming into operation, and then the transmission device 61 is returned to its neutral position.
  • clutch 26 is disengaged to disconnect the auxiliary engine 5
  • dog clutches 19a and 19b are brought into the operative position, dog clutches 32a and 32b being engaged, and the screw pitch is progressively increased by means of pitch control box 11.
  • the total power of the two engine units 10 and 1b is transmitted positively to the screw shaft 4 and the auxiliaries associated with the said engine units (freshwater pumps 7a, 7b, oil pumps 8a, 8b, main oil recovery pump 40 and fuel circulation pumps) are effectively driven at normal speed.

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  • Chemical & Material Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Gear Transmission (AREA)
  • Transmission Devices (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US289264A 1972-01-13 1972-09-15 Propulsion installations for boats, more particularly for high-speed launches Expired - Lifetime US3872675A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR7201106A FR2167341A5 (it) 1972-01-13 1972-01-13

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US3872675A true US3872675A (en) 1975-03-25

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US289264A Expired - Lifetime US3872675A (en) 1972-01-13 1972-09-15 Propulsion installations for boats, more particularly for high-speed launches

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US (1) US3872675A (it)
JP (1) JPS4878692A (it)
DE (1) DE2228956C3 (it)
ES (1) ES406039A1 (it)
FR (1) FR2167341A5 (it)
GB (1) GB1356728A (it)
IL (1) IL40112A (it)
IT (1) IT962177B (it)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4955561A (en) * 1986-09-02 1990-09-11 U. Christian Seefluth Cogwheel drive mechanism for aircraft
US20070210582A1 (en) * 2005-08-30 2007-09-13 Caterpillar Inc. Machine with an electrical system
US7270030B1 (en) * 2005-04-01 2007-09-18 Belloso Gregorio M Transmission with multiple input ports for multiple-engine vehicles

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013219346B4 (de) 2013-09-26 2023-11-02 Zf Friedrichshafen Ag Getriebe für einen Schiffsantrieb
DE102016121672A1 (de) * 2016-11-11 2018-05-17 Rheinmetall Landsysteme Gmbh Antrieb für Fahrzeuge insbesondere Gefechtsfahrzeuge

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2504833A (en) * 1946-06-20 1950-04-18 Hann William Edward Internal-combustion outboard motor having auxiliary electric motor for starting and trolling
US3230698A (en) * 1964-12-09 1966-01-25 Henry D Nettles Marine engine drive
US3601980A (en) * 1968-08-23 1971-08-31 Mtu Friedrichshafen Gmbh Power plant for surface skimmers and hydrofoils
US3683719A (en) * 1969-05-14 1972-08-15 Mtu Friedrichshafen Gmbh Reversing transmission with dual inputs

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2504833A (en) * 1946-06-20 1950-04-18 Hann William Edward Internal-combustion outboard motor having auxiliary electric motor for starting and trolling
US3230698A (en) * 1964-12-09 1966-01-25 Henry D Nettles Marine engine drive
US3601980A (en) * 1968-08-23 1971-08-31 Mtu Friedrichshafen Gmbh Power plant for surface skimmers and hydrofoils
US3683719A (en) * 1969-05-14 1972-08-15 Mtu Friedrichshafen Gmbh Reversing transmission with dual inputs

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4955561A (en) * 1986-09-02 1990-09-11 U. Christian Seefluth Cogwheel drive mechanism for aircraft
US7270030B1 (en) * 2005-04-01 2007-09-18 Belloso Gregorio M Transmission with multiple input ports for multiple-engine vehicles
US20070210582A1 (en) * 2005-08-30 2007-09-13 Caterpillar Inc. Machine with an electrical system
US7291934B2 (en) 2005-08-30 2007-11-06 Caterpillar Inc. Machine with an electrical system

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Publication number Publication date
GB1356728A (en) 1974-06-12
FR2167341A5 (it) 1973-08-24
DE2228956C3 (de) 1975-06-19
IL40112A0 (en) 1972-11-28
IL40112A (en) 1975-02-10
JPS4878692A (it) 1973-10-22
ES406039A1 (es) 1975-08-16
DE2228956A1 (de) 1973-07-26
DE2228956B2 (de) 1974-10-31
IT962177B (it) 1973-12-20

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