EP3974309A1 - Plateforme de moteur hors-bord à refroidissement - Google Patents

Plateforme de moteur hors-bord à refroidissement Download PDF

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Publication number
EP3974309A1
EP3974309A1 EP20197882.2A EP20197882A EP3974309A1 EP 3974309 A1 EP3974309 A1 EP 3974309A1 EP 20197882 A EP20197882 A EP 20197882A EP 3974309 A1 EP3974309 A1 EP 3974309A1
Authority
EP
European Patent Office
Prior art keywords
outboard engine
cooling liquid
heat exchanger
electric motor
cooling
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.)
Withdrawn
Application number
EP20197882.2A
Other languages
German (de)
English (en)
Inventor
Claus Bruestle
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.)
Yanmar Marine International BV
Original Assignee
Yanmar Marine International BV
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 Yanmar Marine International BV filed Critical Yanmar Marine International BV
Priority to EP20197882.2A priority Critical patent/EP3974309A1/fr
Priority to US17/070,090 priority patent/US20220089266A1/en
Publication of EP3974309A1 publication Critical patent/EP3974309A1/fr
Withdrawn legal-status Critical Current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
    • B63H20/00—Outboard propulsion units, e.g. outboard motors or Z-drives; Arrangements thereof on vessels
    • B63H20/007—Trolling propulsion units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H20/00—Outboard propulsion units, e.g. outboard motors or Z-drives; Arrangements thereof on vessels
    • B63H20/001—Arrangements, apparatus and methods for handling fluids used in outboard drives
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H20/00—Outboard propulsion units, e.g. outboard motors or Z-drives; Arrangements thereof on vessels
    • B63H20/28—Arrangements, apparatus and methods for handling cooling-water in outboard drives, e.g. cooling-water intakes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H20/00—Outboard propulsion units, e.g. outboard motors or Z-drives; Arrangements thereof on vessels
    • B63H20/32—Housings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H21/00—Use of propulsion power plant or units on vessels
    • B63H21/12—Use of propulsion power plant or units on vessels the vessels being motor-driven
    • B63H21/17—Use of propulsion power plant or units on vessels the vessels being motor-driven by electric motor

Definitions

  • the invention relates to a cooled outboard engine platform.
  • Outboard engines are widely known for propulsion of boats in fresh or offshore waters.
  • gasoline or diesel fueled internal combustion engines are used to power an outboard engine.
  • electric motors have been used to power outboard engine arrangements, in response to the increasing performance of rechargeable batteries and other electric power generation means, for example fuel cells, as well as by environmental needs.
  • conventional air-cooling equipment does not provide the required cooling performance in all circumstances required to maintain the temperature of the motor and invertor in a normal operational temperature range.
  • the cooling performance of conventional air-cooling equipment can be insufficient under any atmospheric conditions, but particularly when utilized during periods of hot atmospheric conditions.
  • the invention aims at providing a safe and reliable cooled outboard engine platform.
  • a cooled outboard engine platform may comprise an electric motor having an output shaft for outboard propulsion, and an invertor for driving the electric motor, the platform further comprising a cooling system for cooling the electric motor and/or the invertor with a cooling liquid.
  • the electric motor and/or the invertor can be maintained within a pre-determined operational temperature range to realize a safer and more reliable cooled outboard engine platform.
  • a cooled outboard engine platform includes a fluid tight enclosure enclosing a chamber that accommodates the electric motor and the invertor.
  • the enclosure may house or be in communication with a cooling liquid interface for exchanging the cooling liquid in a fluid tight manner, thereby maintaining dry atmospheric conditions around the motor and invertor, as well as providing effective liquid cooling to the platform.
  • a cooled outboard engine platform according to claim 3 may be provided.
  • the cooling liquid interface may include interconnection channels that are integrated in the enclosure, e.g. in an adapter plate supporting the electric motor and the invertor. In some embodiments, the interconnection channels run between interior chamber side connection openings and exterior side connection openings.
  • the cooling system may be of an open type, using seawater, lake water, river water or water from another environmentally available source as cooling liquid.
  • An open cooling system configured to utilize seawater will typically include cooling channels in or on the electric motor and invertor that are corrosion resistant.
  • the cooling system may be of a closed type.
  • a closed cooling system will typically include a heat exchanger e.g. as specified in claim 6, e.g. in thermal communication with and exchanging thermal energy between each of a secondary cooling liquid in a closed secondary cooling circuit and a primary cooling liquid in a primary cooling circuit.
  • the primary cooling circuit can be open and utilize environmentally available water as the primary cooling fluid.
  • a closed cooling system with primary and secondary cooling circuits is advantageous in implementations where parts of the electric motor and/or invertor are not corrosion resistant.
  • the heat exchanger may have the same orientation as the electric motor output shaft, preferably extending along said output shaft, and more preferably having an arrangement that is mainly concentric to said shaft, thereby enabling a compact and efficient design.
  • a driving shaft for propulsion may be sealed in a central channel of the heat exchanger that may having a mainly annular shaped structure surrounding the central channel for passage of the driving shaft.
  • the heat exchanger can be implemented as defined in claim 7 and/or 8.
  • the heat exchanger has a standardized or modular design with standardized attachment mechanisms providing a heat exchanger that can be modified in dimensions with interchangeable parts providing the flexibility to match the heat exchanger to the power and thermal rating of a specific electric motor.
  • One embodiment of heat exchanger having modular construction may include stacked sections including pipe elements that are arranged in a concentric design around the output shaft of the electric motor, so as to facilitate easy assembly and de-assembly of the heat exchanger, and to enable flexible use of standardized components in different heat exchanger configurations.
  • a cooled outboard engine platform according to claim 10 is provided.
  • the heat exchanger includes a first series of cooling channels for downward flow of a closed circuit cooling liquid and a second series of cooling channels for upward flow of the closed circuit cooling liquid, and wherein the first and second series of cooling channels are arranged in respective mutually complementary annular sectors or adjacent semi-annular sectors, thereby providing an efficient concentric design.
  • a cooled outboard engine platform may be provided.
  • the cooling channels of the heat exchanger are connected to the exterior side connection openings of the cooling liquid interface via hose-less connections, e.g. using clamped pipe connections.
  • a cooled outboard engine platform may be provided.
  • a transmission unit can be interposed between the adapter plate and the heat exchanger, thereby maintaining an efficient and compact design.
  • the heat exchanger may comprise an output channel for flowing heated primary cooling liquid towards a gear casing of the outboard engine.
  • a cooled outboard engine platform may be provided.
  • the heat exchanger may be arranged for controlling a temperature of the closed-circuit cooling liquid below a selected temperature level, e.g. below about 45 degrees Celsius.
  • FIG. 1 shows a schematic side view of a cooled outboard engine platform 100 or cooled outboard engine according to the invention.
  • the platform 100 comprises an electric motor 2 having an output shaft 3 for outboard propulsion, and an invertor 4 for driving the electric motor 2.
  • the electric motor 2 may for example be an AC motor, such as a permanent-magnet synchronous motor, PMSM. However, other electric motor types including AC motors, such as an asynchronous or induction motor, may also be used.
  • the platform is provided with electric power lines 16, 16' to deliver power to the invertor 4 and/or electric motor 2.
  • the platform 100 also includes an adapter plate 6 that supports the electric motor 2 as well as the invertor 4.
  • the adapter plate 6 may be formed from a metal or metals, e.g. using a sandcasting process, another casting process, or an alternative technique.
  • the adapter plate 6 has a predominantly flat structure having a top side or a top surface 6a and a bottom side or a bottom surface 6b opposite to the top surface 6a.
  • the electric motor 2 is mounted on the top surface 6a of the adapter plate 6 such that the output shaft 3 is oriented substantially transverse to the generally planar orientation of the adapter plate 6.
  • a longitudinal axis L of the output shaft 3 is oriented mainly transverse to a plane P defined by a surface of the adapter plate 6 or wherein the adapter plate 6 extends.
  • the platform 100 further includes a coupler 40 providing a sealed coupling of the output shaft 3 of the electric motor 2 to a driving shaft 19.
  • the platform 100 further includes a cowling 5 forming a top cover of a chamber 7 wherein the electric motor 2 and the invertor 4 are enclosed.
  • the cowling 5 may, for example, be dome shaped as shown in Fig. 1 or may have another shape, such as a box or cylinder.
  • the cowling 5 can be made from various materials including metal(s) and/or synthetic materials such as plastic(s) and/or composites, etc.
  • the cowling 5 can be fabricated by any suitable process, including but not limited to an injection molding process, such as a high-pressure permanent molding technology, or a blow molding or thermoforming process.
  • the cowling 5 may be integrally formed, for example as a one-piece shell. In other embodiments, the cowling may be composed from multiple modules that are coupled to each other.
  • the cowling 5 is mounted in sealed engagement with the adapter plate 6, creating a fluid tight and/or gastight sealed enclosure 102 enclosing the chamber 7 that accommodates the electric motor 2 and the invertor 4.
  • the platform 100 further comprises a cooling system 22 for cooling the electric motor 2 and/or the invertor 4 and/or, optionally, electric power lines 16, 16' with a cooling liquid.
  • the adapter plate 6 may be provided with a cooling liquid interface, as described below, to facilitate the sealed exchange of cooling liquid between the chamber 7 and the cooling system 22.
  • a representative cooling liquid interface is described in more detail referring to Fig. 2 .
  • an ingoing cooling liquid channel 13 and an outgoing cooling liquid channel 13' also referred to as interconnection channels 13, 13', are integrated in the adapter plate 6.
  • the interconnection channels 13, 13' end in exterior side connection openings.
  • the ingoing and outgoing channels 13, 13' are connected, via chamber side connection openings, to liquid cooling lines 24, 24' to cool the invertor 4, the electric motor 2 and/or, optionally, electric power lines 16, 16'.
  • the platform 100 may include a pump unit 35 arranged in the chamber 7 to pump the cooling liquid towards and from the chamber 7. Alternatively, the pump unit 35 may be located outside the chamber 7.
  • cooling liquid channels 13, 13' may be part of an open or closed liquid cooling system.
  • the cooling liquid may be sea, lake or river water; in the latter case, the cooling liquid may a selected heat transfer fluid, for example, a glycol water mixture or another cooling liquid that may be indirectly cooled by environmental water.
  • FIG. 2 shows a bottom view of the adapter plate 6 of the outboard engine platform 100 illustrated in Fig. 1 .
  • the adapter plate 6 has an opening 12 for receiving the output shaft 3 of the electric motor 2, the opening thus serving as an output port for fluid tight passage of said output shaft 3 from the chamber 7, as described in more detail referring to the coupler 40 shown in Figure 4 .
  • the adapter plate 6 shown in Fig. 2 is an exemplary implementation of the supporting structure for an outboard engine mentioned above.
  • the adapter plate 6 shown in Fig. 2 includes a generally planar deck 17 having ribs 6c extending from the bottom side 6b of the plate downwardly, transverse to the plane P defined by the adapter plate 6, and generally parallel to the longitudinal axis L of the output shaft 3.
  • the adapter plate 6 includes an exterior rib or rim 6d defining a contour of the plate in a circumferential direction C around the longitudinal axis L.
  • the contour has a mainly oval shape.
  • the contour may have other shapes such as an ellipse, a circle, another curved contour or a polygon.
  • the exterior rim 6d extends downwardly from the bottom surface 6b, mainly parallel to the other ribs 6c.
  • the deck 17 generally extends from the opening 12 to the exterior rim 6d, forming the mainly flat bottom side 6b of the plate 6, with discrete segments being defined by the ribs 6c.
  • plate 6 is integrally formed.
  • One specific portion of the deck 17, defines an interface 21, typically located adjacent the opening 12.
  • the interface 21 defines a region where a cooling liquid may be exchanged into and out of the chamber 7 in a sealed manner.
  • the interface 21 integrated in the adapter plate 6 includes the ingoing cooling liquid channel 13 and the outgoing cooling liquid channel 13' mentioned above with reference to Fig. 1 .
  • the interface 21 includes an interior inlet opening 102 and an interior outlet opening 102', both opening into the chamber 7.
  • the interface 21 also includes an exterior inlet opening 103 and an exterior outlet opening 103' both opening away from the chamber 7.
  • the ingoing cooling liquid channel 13 runs from the exterior inlet opening 103 to the interior inlet opening 102
  • the outgoing cooling liquid channel 13' runs from the exterior outlet opening 103' to the interior outlet opening 102'.
  • the exterior inlet opening 103 and the exterior outlet opening 103' are located near the opening 12 so as to connect to a heat exchanger located below the adapter plate 6 concentric to the longitudinal axis L of the output shaft 3 or to another device providing input / output cooling liquid such as direct cooling using fresh water or seawater.
  • the illustrated interface 21 has a mainly rectangular shape, but in other embodiments, the interface 21 may have another shape, e.g. a triangular shape or another polygon shape.
  • the deck 17 including the interface 21 forms a pattern of regions adjoining each other forming the bottom side 6b of the generally flat plate 6.
  • the adapter plate 6 can be implemented without a deck 17 and rib 6c/rim6d configuration.
  • the adapter plate 6 could be implemented with a solid, honeycomb, hollow, or other structure for supporting electric motors of various sizes and weights.
  • the ingoing and outgoing cooling liquid channels 13, 13' may optionally be integrated in the adapter plate 6.
  • the cooling system includes a heat exchanger 22 forming part of a closed liquid cooling system.
  • the cooling liquid flowing within the closed liquid cooling system is referred to herein as a secondary cooling liquid and may be a glycol water mixture or another cooling liquid that may be indirectly cooled by environmental water referred to herein as a primary cooling liquid.
  • Figure 3 shows a schematic cross-sectional side view of the cooling system 22 of the cooled outboard engine platform 100 shown in Fig. 1 , along cross section III.
  • the heat exchanger 22 is mounted or positioned below the adapter plate 6 and extends along and mainly concentric to the output shaft 3 of the electric motor 2, the heat exchanger 22 and the electric motor output shaft 3 having predominantly the same orientation, along the longitudinal axis L of the output shaft 3 electric motor 2.
  • the heat exchanger 22 further has a mainly annular shaped structure surrounding a central channel 137 aligned with the longitudinal axis L of the electric motor output shaft 3, for passage of the driving shaft 19.
  • the heat exchanger 2 includes an array of heat exchanger tubes or internal tubes predominantly aligned with the longitudinal axis L of the electric motor output shaft 3. As illustrated elsewhere, the driving shaft 19 may pass through the central channel 137 of the heat exchanger 22.
  • the heat exchanger 22 is provided with a modular design or construction, including stacked sections that may be interchanged to provide a selected thermal capacity.
  • a modular heat exchanger 22 may include, but is not limited to a chamber section 101, a top cover section 107 on top of the chamber section 101, and a bottom cover section 108 at the bottom of the chamber section 101.
  • the respective stacked sections 101, 107, 108 are mounted in sealed engagement with each other, preferably using a bolted connection and O-rings, gaskets, pressure fittings, or another method of providing a seal between each section.
  • the chamber section 101 includes pipe elements 109, 110, also referred to as internal tubes, pipes or channels, that may be arranged in a concentric design around the longitudinal axis L of the output shaft 3 of the electric motor 2.
  • the height of the chamber section 101 i.e. the dimension of the chamber section 101 along the longitudinal axis L of the electric motor output shaft 3 may be selected to provide sufficient cooling for the electric power output and thermal requirements of the electric motor 2, inverter 4, and associated elements. Generally, when the power of the electric motor increases, the height of the chamber 101 selected to cool that electric motor may be increased.
  • Figure 4 shows a schematic cross-sectional top view of the cooling system 22 shown in Fig. 3 , along cross section IV.
  • the chamber section 101 includes a first and a second semi-annular chamber 111, 112 of similar shape, together forming a mainly closed annular chamber section 101 concentric to the longitudinal axis L.
  • the first and second chamber 111, 112 are arranged as mutually complementary annular sectors, respectively.
  • the first and second chamber 111, 112 each have a radial exterior wall 105 and a radial interior wall 106, both radial exterior walls 105 together forming a mainly closed exterior wall symmetrically positioned around the longitudinal axis L, and both radial interior walls 106 together forming a mainly closed interior wall also symmetrically positioned around the longitudinal axis L and radially bounding the central channel 137.
  • the first chamber 111 includes a first series of cooling channels 109 for downward flow F down of the closed circuit, secondary cooling liquid.
  • the second chamber 112 includes a second series of cooling channels 110 for upward flow F up of the closed circuit, secondary cooling liquid.
  • the first and second chamber 111, 112 each include inflow openings 113, 114, near a bottom portion of the chamber section 101, for flowing a primary cooling liquid into the respective chamber 111, 112.
  • the first and second chamber 111, 112 each include outflow openings 115, 116, near a top portion of the chamber section 101, for flowing the primary cooling liquid from the respective chamber 111, 112 outwardly.
  • the inflow openings 113, 114 can be implemented as multiple openings preferably distributed evenly in the circumferential direction C.
  • embodiments having multiple outflow openings 115, 116 preferably have the outflow openings 115, 116 distributed evenly in the circumferential direction C.
  • a single inflow opening and/or a single outflow opening can be placed into fluid communication with the first and/or second chamber 111, 112, respectively.
  • the pipe elements or channels 109, 110, the radial exterior wall 105 and the radial interior wall 106 are preferably made from stainless steel or another non-corrosive material.
  • the pipe elements 109, 110 are made from austenitic steel.
  • tens or hundreds of pipe elements 109, 110 can be used, e.g. 100, 150 or 200 pipe elements.
  • the pipe elements may have an outer diameter ranging between about 5 mm and about 15 mm, e.g. about 9 mm, and may have an inner diameter also ranging between about 5 mm and about 15 mm, e.g. about 8.7 mm.
  • pipe elements having other dimensions can be utilized as well, including but not limited to pipe elements 109, 110 having larger or smaller inner and/or outer diameters and selected wall thicknesses.
  • the top cover section 107 mounted in sealed engagement with the chamber section 101 includes or defines a first and a second channel section 117, 118.
  • the first and second channel section are separate from each other, and provided, at their lower side, with respective openings 119, 120.
  • the openings 119, 120 are mated in sealed engagement with the upper portions of the first and second series of cooling channels or tubes 109, 110.
  • the first and second channel section 117, 118 are further provided, at a top side, with openings 121, 122 located to be aligned with corresponding exterior side connection openings 103, 103' of the cooling liquid interface 21 of the adapter plate 6.
  • the exterior side connection openings 103, 103' of the cooling liquid interface 21 form direct hose-less connections with the corresponding first and second channel section 117, 118 and the corresponding cooling channels 109, 110 of the heat exchanger 22.
  • Said hose-less connections between the openings 119, 121 and the exterior side connection openings 103, 103' are clamped into tight and sealed engagement, for example by bolts used to attach the heat exchanger 22 to the adapter plate 6.
  • a fluid-tight seal at the hose-less connection may be enhanced by providing suitable O rings, gaskets or other sealing structures at the connection.
  • the bottom cover section 108 includes a common channel section 123 that is provided, at its top side, with respective openings 124, 125 receiving corresponding lower portions of the first and second series of cooling channels or tubes 109, 110 in a sealed engagement.
  • the bottom parts of the first and second series of cooling channels or tubes 109, 110 are in fluid communication with the common channel section 123 via hose-less connections.
  • Said hose-less connections can be clamped into sealed engagement, preferably using bolts or a similar attachment method.
  • the pipe elements 109, 110 can be permanently bonded into sealed engagement with one or both of the top cover section 107 and the bottom cover section 108 using a brazing / welding process, adhesives, or another suitable attachment method.
  • the bottom cover section 108 includes a primary circuit channel section 126 positioned around a lower portion of the chamber section 101 and having an inlet 127 for the inflow of the primary cooling liquid, e.g. seawater, and a first and a second outflow openings 128, 129 aligned with the respective inflow openings 113, 114 of the respective chambers 111, 112.
  • the selected length of the inflow section 127 may vary, depending for example on the shaft length and/or a position of a gear casing.
  • the top cover section 107 and/or the bottom cover section 108 may have a modular design itself, for example, the top cover section 107 and the bottom cover section 108 may include stacked sub modules.
  • the top cover section 107 and the bottom cover section 108 are made from aluminum.
  • the respective stacked sections 101, 107, 108 are mounted to each other and to the adapter plate 6, preferably using a bolt construction and O-rings 131, 132, 133, 134, 135, 136 as shown in Fig. 3 using first bolts 138 mounting the top cover section 107 to the adapter plate 6, and second bolts 139, the second bolts 139 being longer than the first bolts 138 and extending from the bottom cover section 108 into corresponding threaded holes in the top cover section 107, thereby sandwiching the chamber section 101 between the top cover section 107 and the bottom cover section 108.
  • the stacked sections 101, 107, 108 in the adapter plate 6 may be mounted to each other using another suitable construction method and other suitable sealing methods, including but not limited to gaskets, welded joints, pressure fittings and the like.
  • the bottom cover section 108, and, subsequently, the chamber section 101 can be removed from the top cover section 107 without removing the top cover section 107 that is attached to the adapter plate 6, thereby providing ready access to the interior of the heat exchanger 22 for service by qualified personnel.
  • the primary cooling liquid flows via a first flow path P 1 from the inflow section 127 of the bottom cover section 108 into the channel section 126. Then, the flow is divided into two sub flows flowing to the first and second chambers 111, 112, respectively, via a second path P 2 in the first outflow section 128 and the first inflow opening 113, and via a third path P 3 in the second outflow section 129 and the second inflow opening 114, respectively. Then, the primary cooling liquid flows upwardly via the fourth path P 4 and the fifth path P 5 , in the first and second chambers 111, 112, respectively.
  • the primary cooling liquid exchanges heat with and cools the secondary liquid in the first and second series of cooling channels 109, 110. Subsequently, the primary cooling liquid flows from the first and second chamber 111, 112 outwardly, via a sixth path P 6 and a seventh path P 7 , respectively, through the respective outflow openings 115, 116, and into an output channel 130 that may be formed as a hose, tube, pipe, or other conduit that may optionally be provided for flowing the heated primary cooling liquid towards anyone of specific inflow opening in the drive shaft housing, a gear casing of the outboard engine, towards another module, or directly back into the surrounding water.
  • the primary cooling liquid flows via the outflow openings 115, 116 directly into a drive shaft housing from where it flows outwardly through the gear casing into the surrounding environmental water.
  • the primary cooling liquid may be circulated by an optional pump unit and/or by directing a first cooling liquid inflow opening towards a propulsion direction of the boat.
  • the secondary cooling liquid flows in downward flow F down in the second series of cooling channels 110 arranged in the second chamber 112.
  • the secondary cooling liquid flows through the second chamber 112 it exchanges heat with and is cooled by the surrounding upwardly flowing primary cooling liquid, using the heat exchanger principle of co-flow and counter flow on the hot side.
  • the secondary cooling liquid flows via the common channel section 123 towards the first chamber 111, and via the first series of cooling channels 109 in an upward flow F up towards the first channel section 117 of the top cover section 107.
  • the secondary cooling liquid then flows via the exterior inlet opening 103 into the ingoing channel 13 of the cooling liquid interface 21.
  • the secondary cooling liquid flows, via the interior inlet opening 102, into a first secondary liquid cooling line 24 to cool the invertor 4, the electric motor 2 and/or, optionally, electric power lines 16, 16'.
  • the heated secondary liquid cooling liquid flows via a second secondary liquid cooling line 24' back, via the interior outlet opening 102' into the outgoing liquid channel 13', and then, via the exterior outlet opening 103' into the second channel section 118 of the top cover section 107, and back into the second series of cooling channels 110 in the second chamber 112, thus forming a closed circuit for the secondary cooling liquid.
  • the secondary cooling liquid flow is circulated by the pump unit 35.
  • an expansion reservoir 23 may be provided connected to the closed secondary cooling liquid circuit, as described referring to Fig. 5 , to accommodate and limit any temperature induced pressure increase in said circuit.
  • the expansion reservoir 23 is installed above the cooling liquid entrance of the motor 2 and the invertor 4, respectively.
  • the first and second secondary liquid cooling lines 24, 24' may include hoses, located in the chamber 7 where the electric motor 2 and the invertor 4 are located.
  • the cooling lines may include a first hose running between the interior inlet opening 102 and an invertor inlet, a second hose running between an invertor outlet and an electric motor inlet, a third hose running between an electric motor outlet and the interior outlet opening 103, and a fourth hose running from the first hose and the expansion reservoir 23.
  • FIG. 5 is a schematic system overview of the cooling system 22 shown in Figs. 3 and 4 .
  • an open primary cooling liquid circuit 151 and a closed secondary cooling liquid circuit 152 are shown, exchanging heat from the secondary cooling liquid circuit 152 to the primary cooling liquid circuit 151 within the heat exchanger 22.
  • the open primary cooling liquid circuit 151 may be supplied by environmental water received through an opening below the waterline, for example through an opening in a gear case of the platform.
  • the circulation of the primary cooling liquid may be caused by a water pump 153 that is preferably arranged in or near the gear case, upstream of the heat exchanger 22.
  • the water pump 153 may have a capacity of about 10 liters per minute to about 100 liters per minute, for example about 60 liter per minute.
  • the water pump flow rate may be selected depending on the electric power output and cooling requirements of the electric motor. Downstream from the heat exchanger, the primary cooling liquid may flow back to the water pump, via the sixth flow path P 6 .
  • Circulation of the secondary cooling liquid may be caused by the pump unit 35 positioned in or near the chamber 7.
  • the pump unit 35 may have a capacity of about 5 liters per minute to about 60 liters per minute, for example about 20 liters per minute at a specific system back pressure, for example 1 bar.
  • the secondary cooling liquid flow rate, and pump unit 35 size may be selected depending on the electric power and associated cooling requirements of the electric motor and inverter.
  • the secondary cooling liquid circuit 152 includes an expansion reservoir 23 as described above. Said secondary cooling liquid circuit 152 can be filled, refilled, topped off or otherwise accessed via the expansion reservoir 23.
  • the invertor 4 and the electric motor 2 are cooled by the secondary cooling liquid in series, with the invertor 4 being cooled prior to the electric motor 2.
  • the order may be reversed such that the invertor 4 is cooled with cooling liquid having previously cooled the electric motor 2.
  • the secondary cooling liquid circuit 152 may be split for cooing the electric motor 2 and the invertor 2 in a parallel manner.
  • the electric power lines may be cooled by the secondary cooling liquid circuitry 152, if required.
  • the heat exchanger 22 may be sized and configured for maintaining a temperature of the secondary cooling liquid below a predefined temperature level, e.g. about 45 degrees Celsius, during normal operational conditions of the engine platform 100.
  • a control module may be provided for controlling operation of at least one pump unit 35 and/or 153 to control a liquid flow rate of the primary and/or secondary cooling liquid, depending on temperature data sensed by a cooling liquid temperature sensor.
  • Fig. 6 is a schematic side view of an alternative cooled outboard engine platform 100 according to the invention.
  • a transmission unit 201 is interposed between the adapter plate 6 and the heat exchanger 22, thereby maintaining an efficient and compact design.
  • the transmission unit 201 is positioned concentrically relative to the longitudinal axis L of the output shaft 3 and includes an input side connected to the output shaft 3 of the electric motor 2, a transmission mechanism 202, e.g. a planetary type transmission mechanism, and a transmission output shaft 203 connected to the driving shaft 19.
  • transmission output shaft 203 carries an internal spline and is made from corrosion resistant material.
  • the transmission mechanism 202 is configured to provide a transmission ratio between the output shaft 3 of the electric motor 2, as input shaft of the mechanism 202, and the transmission output shaft 203, as output shaft of the mechanism 202 or driving shaft 19.
  • the transmission ratio may be selected to be larger then unity, e.g. about 1.25 to match an optimal operational rotational speed of the electric motor and to provide an optimal operational rotational speed of the driving shaft 19 and a propeller driven by the driving shaft 19.
  • the transmission ratio may have any other suitable value, e.g. greater than about 1.25 or smaller than about 1.25, e.g. 1 or smaller than 1, e.g. about 0.75.
  • the transmission unit 201 may provide a variable transmission ratio between the output shaft 3 and driving shaft 19.
  • the transmission unit 201 further includes passages 213, 213' interconnecting the exterior inlet opening 103 and the exterior outlet opening 103' of the interface 21 to the respective openings 121, 122 of the first and second channel section 117, 118 of the top cover section 107 of the heat exchanger 22.
  • a radial dimension of the transmission unit 201 i.e. a dimension mainly transverse to the longitudinal axis L, is substantially the same as a radial dimension of the heat exchanger 22.
  • the diameter of the transmission unit 201 may be smaller or larger than the diameter of the heat exchanger 22.
  • the transmission unit 201 may have a larger diameter than the heat exchanger 22.
  • the cooled outboard engine platform 100 shown in Fig. 6 can be implemented with a coupler 40 as described above, especially if the transmission mechanism includes corrodible elements, including but not limited to elements of the transmission mechanism at the driving shaft side.
  • the transmission output shaft 203 can be connected at the input side of the coupler and the driving shaft 19 can be connected at the output side of the coupler 40.
  • the cooling system can be implemented as a so-called open liquid cooling system, the cooling liquid being sea water, lake water or another environmental water source.
  • cooling system including a heat exchanger as described above is not limited to application with a cooled outboard engine platform as described herein, specifically a platform having an electric motor having an output shaft for outboard propulsion, and an invertor for driving the electric motor.
  • the cooling system can also be applied more generally with any engine or power source as a cooling system having a tubular arrangement that is mainly concentric around the drive shaft, preferably having a modular construction including stacked sections.
  • the cooling system may have no heat exchanger.
  • the cooling system may e.g. be constructed as an open cooling liquid circuitry, e.g. for cooling the motor, the invertor and/or the power lines directly with seawater.

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  • Chemical & Material Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP20197882.2A 2020-09-23 2020-09-23 Plateforme de moteur hors-bord à refroidissement Withdrawn EP3974309A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP20197882.2A EP3974309A1 (fr) 2020-09-23 2020-09-23 Plateforme de moteur hors-bord à refroidissement
US17/070,090 US20220089266A1 (en) 2020-09-23 2020-10-14 Outboard Engine Arrangement

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20197882.2A EP3974309A1 (fr) 2020-09-23 2020-09-23 Plateforme de moteur hors-bord à refroidissement

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EP3974309A1 true EP3974309A1 (fr) 2022-03-30

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005153727A (ja) * 2003-11-26 2005-06-16 Suzuki Motor Corp 電動式船外機
JP2005162055A (ja) * 2003-12-03 2005-06-23 Suzuki Motor Corp 電動式船外機
JP2014080077A (ja) * 2012-10-15 2014-05-08 Suzuki Motor Corp 電動船外機
WO2016008233A1 (fr) * 2014-07-18 2016-01-21 常州高尔登科技有限公司 Machine de suspension d'hélice pour navire
US20160059949A1 (en) * 2014-05-06 2016-03-03 Pure Watercraft, Inc. Sternboard drive for marine electric propulsion
US10760470B2 (en) * 2016-10-26 2020-09-01 Guangdong Epropulsion Technology Limited Ship propulsion apparatus

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005153727A (ja) * 2003-11-26 2005-06-16 Suzuki Motor Corp 電動式船外機
JP2005162055A (ja) * 2003-12-03 2005-06-23 Suzuki Motor Corp 電動式船外機
JP2014080077A (ja) * 2012-10-15 2014-05-08 Suzuki Motor Corp 電動船外機
US20160059949A1 (en) * 2014-05-06 2016-03-03 Pure Watercraft, Inc. Sternboard drive for marine electric propulsion
WO2016008233A1 (fr) * 2014-07-18 2016-01-21 常州高尔登科技有限公司 Machine de suspension d'hélice pour navire
US10760470B2 (en) * 2016-10-26 2020-09-01 Guangdong Epropulsion Technology Limited Ship propulsion apparatus

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