Planetary gear set, and transmission having a planetary gear set

Abstract

Planetary gear sets have a variety of applications. Transmissions are intended, for example, for marine propulsion devices. A main planetary gear set connects the input shaft to the output shaft to drive the output shaft for forward rotation. A supplementary planetary gear set connects the input shaft to the output shaft together with the main planetary gear set to drive the output shaft for reverse rotation. A forward brake engages the main planetary gear set in the forward gear where the main planetary gear set drives the output shaft for forward rotation. A reverse brake engages the supplementary planetary gear set in the reverse gear where the supplementary planetary gear set drives the output shaft together with the main planetary gear set for reverse rotation.

Description

Technical Field

[0001] The present invention relates to a planetary gear set in a transmission whose main use area is within the drive train of a marine propulsion device. In a marine propulsion device, an internal combustion engine provides power to the drive train, and the drive train drives one or more propellers of the propulsion unit at a reduced speed to move the ship on water. Of course, the planetary gear set can have a range of other applications, from small gearing in watch manufacturing, automotive transmissions including hybrids, drive units of outboard motors and stern engines, to transmissions of heavy equipment such as agricultural tractors, or wheel loaders, compactors, dozers, graders, etc. The planetary gear set can act as an acceleration device, a deceleration device, or a power split device that can be arranged on the input of the drive train, in the middle of the drive train, or on the output of the drive train.

Background Art

[0002] Transmissions described in, for example, US9708048B2 (Patent Document 1), US9731803B2 (Patent Document 2), US9908604B2 (Patent Document 3), US20180148149A1 (Patent Document 4), US10875616B2 (Patent Document 5), US8425373B2 (Patent Document 6), US9676463B1 (Patent Document 7), US9759321B1 (Patent Document 8), US9919783B1 (Patent Document 9), US9964210B1 (Patent Document 10), US10239598B2 (Patent Document 11), US10502312B1 (Patent Document 12) are used to drive multiple propellers or a large number of propellers of a ship having an internal combustion engine with a power within the range from 220.7 kW (300 PS) of SUZUKI DF300B to 447.3 kW (600 hp) of MERCURY Verado 600 hp 7.6L V12.

[0003] The main drawbacks of the transmissions known by Suzuki in patents US9708048B2 (Patent Document 1), US9731803B2 (Patent Document 2), US9908604B2 (Patent Document 3), and US20180148149A1 (Patent Document 4) are that the transmissions have bevel gear sets that are difficult to manufacture, and the difficult assembly of the bevel gear sets requires precise measurements and the insertion of shims. The bevel gears have a clutch in which dog teeth are formed. Shifting with such a dog clutch without the benefit of speed synchronization produces noisy punching and damage given at least by the engine's idling speed, the moment of inertia of the crankshaft with a flywheel, and the moment of inertia of the propeller, which are partially mitigated by the torsional elasticity of a torsional rubber damper inside the propeller. The forward gears are only direct 1:1, and therefore, reduction must be ensured by a combination of partial reduction before the final drive or reverse transmission and partial reduction by the final drive. In rare cases, the idler shaft, which is horizontally positioned with the bevel gears and shift mechanism, occupies space at the expense of the exhaust pipe.

[0004] The Mercury Marine transmission described in ZF Patent US10875616B2 (Patent Document 5) has multiple gear pairs with large horizontal mounting dimensions and a wet multi-plate clutch with large horizontal and vertical mounting dimensions, making it practically impossible to integrate the transmission into a gear case housing. This necessitates placing the transmission in a drive shaft housing, in which case a dedicated torsional vibration damper is required instead of the torsional elasticity of a short drive shaft or the absence of a drive shaft, and steering is achieved not by the yawing of the entire outboard motor, but solely by the gear case housing, which must be steerable. The transmission casing is neither lightweight nor simple, as it has three axes for the shaft. Comprehensive and complex environment-sensitive hydraulics are required to control the multi-plate clutch, which necessitates complex compensation of centrifugal pressure in the rotating piston of the multi-plate clutch, resulting in more wear on the moving seals. Furthermore, the three multi-plate clutches with vertical axes and the double or triple gear pairs through which power flows result in significant power loss.

[0005] The transmission described in Yamaha's patent US8425373B2 (Patent Document 6) has a small mounting space, which is provided horizontally by a planetary gear set and mainly limited vertically by a multi-plate clutch, and has the other drawbacks described in the previous paragraph. The transmission can be partially incorporated into a gear case housing, and its operation can be the same as the yawing of a typical simple outboard motor.

[0006] The transmission described in Mercury Marine patents US9676463B1 (Patent Document 7), US9759321B1 (Patent Document 8), US9919783B1 (Patent Document 9), US9964210B1 (Patent Document 10), US10239598B2 (Patent Document 11), and US10696370B1 (Patent Document 13) comprises two planetary carriers and components of a planetary gear set intricately joined by grooved joints, spline joints, and bolted joints, thereby increasing the installation space in both the horizontal and vertical directions. [Prior art documents] [Patent Documents]

[0007] [Patent Document 1] US9708048B2 [Patent Document 2] US9731803B2 [Patent Document 3] US9908604B2 [Patent Document 4] US20180148149A1 [Patent Document 5] US10875616B2 [Patent Document 6] US8425373B2 [Patent Document 7] US9676463B1 [Patent Document 8] US9759321B1 [Patent Document 9] US9919783B1 [Patent Document 10] US9964210B1 [Patent Document 11] US10239598B2 [Patent Document 12] US10502312B1 [Patent Document 13] US10696370B1 [Overview of the Initiative] [Problems that the invention aims to solve]

[0008] The drawbacks described in the previous paragraph are largely eliminated by the transmission having a planetary gear set according to the proposed invention. [Means for solving the problem]

[0009] In a specific example, the transmission is for a marine propulsion device having an internal combustion engine that drives a propulsion device for propelling a ship on water. The input shaft is driven to rotate by the engine. The output shaft drives the propulsion device to rotate. The main planetary gear set connects the input shaft to the output shaft so as to drive the output shaft to rotate forward. The supplementary planetary gear set connects the input shaft to the output shaft together with the main planetary gear set so as to drive the output shaft to rotate backward. The forward brake engages the main planetary gear set in the forward gear in which the main planetary gear set drives the output shaft to rotate forward. The reverse brake engages the supplementary planetary gear set in the reverse gear in which the supplementary planetary gear set drives the output shaft to rotate backward together with the main planetary gear set. In other examples, the planetary gear set may have a number of use areas, and at least some of the other examples are illustrated in the accompanying drawings and described in examples of implementation forms.

[0010] The present disclosure will be described with reference to the following drawings. The same numbers are used throughout the drawings to refer to similar features and similar components.

Brief Description of the Drawings

[0011] [Figure 1] It is a side view of an outboard propulsion device. [Figure 2] It is a perspective view of a transmission for an outboard propulsion device. [Figure 3] It is an exploded view of the transmission. [Figure 4] It is an exploded view of the transmission. [Figure 5] It is an exploded view of the transmission. [Figure 6] It is an exploded view of the transmission. [Figure 7] It is a top view of a brake for the transmission. [Figure 8] It is a perspective view of a band brake for the transmission. [Figure 9] It is a perspective view of another type of band brake for the transmission. [Figure 10]It is a view of cross-section 10-10 taken in FIG. 2, showing a transmission in neutral gear. [Figure 11] It is a view of cross-section 10-10 taken in FIG. 2, showing a transmission in forward gear. [Figure 12] It is a view of cross-section 10-10 taken in FIG. 2, showing a transmission in reverse gear. [Figure 13] It is a schematic diagram of a tractor power transmission system having a planetary gear set at the input of the drive train. [Figure 14] It is a schematic diagram of a tractor power transmission system having a planetary gear set in the middle of the drive train. [Figure 15] It is a schematic diagram of a tractor power transmission system having a planetary gear set near the output of the drive train. [Figure 16] It is a view of a wheel loader with a transmission having a planetary gear set. [Figure 17] It is a schematic diagram of a wheel loader transmission having the planetary gear set shown in FIG. 16. [Figure 18] It is a view of a planetary gear set having a main planetary gear within a supplementary planetary gear. [Figure 19] It is a view of a planetary gear set having a main planetary gear within a supplementary planetary gear. [Figure 20] It is a view of a planetary gear set having a main planetary gear between supplementary planetary gears. [Figure 21] It is a view of a planetary gear set having a main planetary gear within and between supplementary planetary gears.

Mode for Carrying Out the Invention

[0012] Figure 1 shows an outboard propulsion device 11 that propels a vessel 12 on the water. The outboard propulsion device 11 is connected to the transom 14 of the vessel 12 by a transom bracket 16. Conventionally, the outboard propulsion device 11 includes an internal combustion engine 18 located within an upper cowling 20. The engine 18 generates rotation of a drive shaft 22 extending downward through a drive shaft housing 24. A transmission 26 relays rotational force from the drive shaft 22 to a propulsion shaft 28 located within a propulsion shaft housing 30. The transmission 26 is located within or on top of a gear case housing 32, which is positioned below the drive shaft housing 24. The rotation of the propulsion shaft 28 generates rotation of a propulsion system 34, which in this example includes a reverse-rotating propeller 36. The type of propulsion device 34 may be changed from those shown in the illustration, and other examples may include one or more propellers or one or more impellers, etc.

[0013] Embodiments of the transmission 26 are shown in Figures 2 to 12. Referring to Figures 2 to 6, the transmission 26 includes an input shaft 38 that is driven and rotated by the engine 18. The input shaft 38 may be the drive shaft 22 or an extension of the drive shaft 22 such that the rotation of the drive shaft 22 simultaneously causes the input shaft 38 to rotate. The transmission 26 also includes an output shaft 40, which is connected to the propulsion shaft 28 via, for example, a conventional gear set (not shown) such that the rotation of the output shaft 40 simultaneously causes the propulsion shaft 28 to rotate. The input shaft 38 and the output shaft 40 are connected together by a main planetary gear set 42 and a supplementary planetary gear set 44 such that the input shaft 38 and the output shaft 40 are coaxially aligned.

[0014] The planetary gear set 27 consists of a main planetary gear set 42 and a supplementary planetary gear set 44.

[0015] As will be described in more detail below, the main planetary gear set 42 connects the input shaft 38 to the output shaft 40 to drive the output shaft 40 into forward rotation. The supplementary planetary gear set 44 connects the input shaft 38 to the output shaft 40 together with the main planetary gear set 42 to drive the output shaft 40 into reverse rotation. Both the main planetary gear set 42 and the supplementary planetary gear set 44 provide the same or similar reduction from the input shaft 38 to the output shaft 40. In a non-limiting example, the nominal reduction ratio is 1.667:1. The forward brake 46 engages the main planetary gear set 42 in the forward gear to drive the output shaft 40 into forward rotation. The reverse brake 48 engages the supplementary planetary gear set 44 together with the main planetary gear set 42 in the reverse gear to drive the output shaft 40 into reverse rotation. Regardless of whether the forward brake 46 or the reverse brake 48 is applied, the output shaft 40 does not engage the neutral gear, which is separated from the input shaft 38.

[0016] Referring to Figures 3 to 6, the main planetary gear set 42 includes a main ring gear 50, which is fixed to the input shaft 38 and rotates with the input shaft 38. The main ring gear 50 and the input shaft 38 may be formed together as a single part, or as separate parts connected together. The main ring gear 50 includes a radially inward gear surface 52. The main planetary gear set 42 also includes a main sun gear 54, which is coaxially mounted on the lower casing extension 55 (see Figures 10 to 12). The main sun gear 54 has a radially outward gear surface 56 and a radially inward bearing surface 58. The radially inward bearing surface 58 supports the lower casing extension 55 so that the main sun gear 54 is rotatable relative to the lower casing extension 55. The type of bearing surface can be changed, and in this example, it includes a roller bearing 59. The main planetary gear set 42 further includes a forward brake drum 60 that rotates with the main sun gear 54. The forward brake drum 60 may be formed as a single component together with the main sun gear 54, or the forward brake drum 60 may be a separate component attached to the main sun gear 54.

[0017] The main planetary gear set 42 further includes a plurality of main planetary gears 62, each of which is rotatable around its own central axis and is radially arranged between the main ring gear 50 and the main sun gear 54. Each main planetary gear 62 has a radially outward gear surface 66 that engages with the radially inward gear surface 52 of the main ring gear 50, and also has a radially outward gear surface 67 that engages with the radially outward gear surface 56 of the main sun gear 54.

[0018] The main planetary gear 42 further includes a main carrier 68 that holds a plurality of main planetary gears 62 such that the main planetary gear 62 is rotatable around its own central axis 64. The main carrier 68 is fixed to the output shaft 40 and rotates with the output shaft 40, and is rotatable relative to the main ring gear 50 and the main sun gear 54. The main carrier 68 and the output shaft 40 may be formed together as a single part, or they may be separate parts that are connected together.

[0019] The supplemental planetary gear set 44 includes a supplemental sun gear 74, which is fixed to the main sun gear 54 and the forward brake drum 60 and rotates together with the main sun gear 54 and the forward brake drum 60. The supplemental sun gear 74 may be formed as a single component with the main sun gear 54 and the forward brake drum 60, or it may be formed separately from the main sun gear 54 and the forward brake drum 60 and connected to the main sun gear 54 and the forward brake drum 60. The supplemental sun gear 74 includes a radially outward gear surface 76. The supplemental planetary gear set 44 also includes a supplemental ring gear 78, which is fixed to the reverse brake drum 94 and rotates together with the reverse brake drum 94. The supplemental ring gear 78 and the reverse brake drum 94 may be formed together as a single part, or they may be separate parts connected together. The bearings 97, such as roller bearings, support the supplementary ring gear 78 with respect to the upper casing expansion portion 99 (see Figures 10 to 12). The supplementary ring gear 78 includes a radially inward gear surface 84.

[0020] The supplemental planetary gear set 44 further includes a plurality of supplemental planetary gears 86, each of which is rotatable around its own central axis 88 and is radially arranged between the supplemental ring gear 78 and the supplemental sun gear 74. Each supplemental planetary gear 86 has a radially outward gear surface 90, which engages with the radially inward gear surface 84 of the supplemental ring gear 78 and the radially outward gear surface 76 of the supplemental sun gear 74.

[0021] In one embodiment shown in Figures 18-19, the supplemental planetary gear set 44 holds the supplemental planetary gear 86 using interplanetary bearings 92, main planetary gears 62 and main carriers 68, allowing the supplemental planetary gear 86 to rotate around its own central axis 88. In this embodiment, the main planetary gears 62 are aligned coaxially with the supplemental planetary gears 86 such that each main planetary gear 62 is positioned inside each supplemental planetary gear 86. In this embodiment, the central axis 64 of the main planetary gears 62 and the central axis 88 of the supplemental planetary gears 86 are the same.

[0022] In another embodiment shown in Figure 20, the supplemental planetary gear set 44 holds the supplemental planetary gear 86 using a main carrier 68, allowing the supplemental planetary gear 86 to rotate around its own central axis 88. In this embodiment, the main planetary gear 62 is positioned between the supplemental planetary gears 86, and therefore the main planetary gear 62 is not coaxially aligned with the main planetary gear 86, and the central axes 64 and 88 are not identical.

[0023] Referring to Figures 7 to 9, the exact configuration of the forward brake 46 and reverse brake 48 can be modified. In some examples, the forward brake 46 and reverse brake 48 are conventional single-wrap band brakes as shown in Figure 8. In some examples, the forward brake 46 and reverse brake 48 are conventional double-wrap band brakes as shown in Figure 9. The functions of single-wrap band brakes and double-wrap band brakes are generally the same, except that the torque capacity of the double-wrap band brake is higher than that of the single-wrap band brake for the same operating force. In the examples in Figures 2 to 6, the forward brake 46 and reverse brake 48 are wrapped around the forward brake drum 60 and the reverse brake drum 94 and act on the forward brake drum 60 and the reverse brake drum 94. By tightening the band brake, rotation of the brake drum is prevented. By loosening the band brake, rotation of the brake drum is allowed.

[0024] Figure 7 shows an example in which the reverse brake 48 is a double-wrap band brake wound around the reverse brake drum 94. The forward brake 46 and forward brake drum 60 may be configured similarly. The actuator 96 is configured to actuate either the forward brake 46 or the reverse brake 48. The type of actuator may be changed from that shown. In this example, the actuator 96 includes a servo motor 98, which moves a pin 100 in the direction of arrow 102 relative to a bearing bracket 104 located at one end of the reverse brake 48. The other end of the reverse brake 48 is fixed to a gear case housing 106. The movement of the pin 100 in the direction of arrow 102 tightens the reverse brake 48 around the reverse brake drum 94, thus preventing the reverse brake drum 94 from rotating. In this example, the forward brake 46 and the reverse brake 48 are self-biased, which means that the rotation direction of the forward brake drum 60 and the reverse brake drum 94 (indicated by arrow 103) is the same as the operating direction indicated by arrow 102. Therefore, the rotation of the brake drums 60 and 94 assists the operation of the forward brake 46 and the reverse brake 48. Movement of the pin 100 in the opposite direction to that of arrow 102 releases the reverse brake 48 relative to the reverse brake drum 94, thus allowing the reverse brake drum 94 to rotate.

[0025] Referring to Figures 10 to 12, the transmission 26 can engage the input shaft 38 with the output shaft 40 in neutral, forward, and reverse gears. Figure 10 shows the transmission 26 in neutral gear, where the rotation of the input shaft 38 does not cause the rotation of the output shaft 40. In neutral gear, neither brake 46 nor 48 is tightened around the brake drums 60 and 94. That is, the actuator 96 does not move the pin 100 in the direction of arrow 102. Therefore, both brake drums 60 and 94 rotate freely.

[0026] Thus, the forward rotation of the input shaft 38 (indicated by arrow 105) causes the main ring gear 50 to rotate forward. The forward rotation of the main ring gear 50 causes the main planetary gear 62 to rotate forward, and the forward rotation of the main planetary gear 62 causes the main sun gear 54, the forward brake drum 60, and the supplemental sun gear 74 to rotate backward. The backward rotation of the supplemental sun gear 74 causes the supplemental planetary gear 86 to rotate forward, and the forward rotation of the supplemental planetary gear 86 causes the supplemental ring gear 78 and the reverse brake drum 94 to rotate forward. The main carrier 68 and the output shaft 40 remain stationary. The rotation of the input shaft 38 is not transmitted to the output shaft 40.

[0027] Figure 11 shows the transmission 26 in forward gear, and the forward brake 46 is actuated by the actuator 96 to move pin 100 in the direction of arrow 102, and pin 100 holds the forward brake drum 60 and the main sun gear 54 and supplemental sun gear 74 stationary as described above. The forward rotation of the input shaft 38 (at 105) causes the forward rotation of the main ring gear 50, and the forward rotation of the main ring gear 50 causes the forward rotation of the multiple main planetary gears 62 as well as the forward rotation of the main carrier 68 and output shaft 40. The forward rotation of the main carrier 68 also results in the forward rotation of the multiple supplemental planetary gears 86 as well as the forward rotation of the supplemental ring gear 78 and reverse brake drum 94.

[0028] Figure 12 shows the transmission 26 in reverse gear, where the actuator 96 moves pin 100 in the direction of arrow 102, and pin 100 holds the reverse brake drum 94 and supplemental ring gear 78 stationary as described above. The forward rotation of the input shaft 38 (at 105) causes the forward rotation of the main ring gear 50, and the forward rotation of the main ring gear 50 causes the forward rotation of the multiple main planetary gears 62 as well as the reverse rotation of the main sun gear 54 and the forward brake drum 60 and supplemental sun gear 74, as well as the forward rotation of the multiple supplemental planetary gears 86 as well as the reverse rotation of the main carrier 68 and output shaft 40.

[0029] Therefore, it can be seen that the rotation of the input shaft 38 simultaneously directly powers the main planetary gear set 42 and indirectly powers the supplementary planetary gear set 44. More specifically, the rotation of the input shaft 38 simultaneously directly powers the main planetary gear set 42 via the main ring gear 50 and indirectly powers the supplementary planetary gear set 44 via the main planetary gear set 42.

[0030] As shown in Figure 2, the output shaft 40 is directly connected to a reverse lubrication pump 110 that supplies lubrication, such as oil, to the transmission and lower gearbox unit 26. Therefore, the reverse lubrication pump 110 operates whenever the engine 18 is running and a forward or reverse gear is engaged. The coolant pump 112 is directly connected to the input shaft 38 so that the rotation of the input shaft 38 causes the coolant pump 112 to inject coolant into the engine 18. Therefore, the coolant pump 112 operates whenever the engine 18 is running. Neither the reverse lubrication pump 110 nor the coolant pump 112 changes their operation based on the forward or reverse gear changes performed by the transmission 26. The reverse lubrication pump 110 does not operate in neutral if the splash vanes 108 attached to the rotating main sun gear 54 provide sufficient lubrication. The cooling water pump 112 operates in neutral, forward, or reverse gear as performed by the transmission 26. The components of the transmission 26 can be made from a variety of materials, including steel and metals such as cast iron which dissipates heat.

[0031] Advantageously, the transmission 26 can be configured to provide the same reduction in both forward and reverse gears, and to have a higher power density compared to the prior art.

[0032] Advantageously, the transmission 26 can withstand specific torque inputs, speeds, shift cycles, and transient conditions such as ripples and throttle chops, while still being positioned between the drive shaft housing 24 and the gear case housing 32, for example, within a minimum axial length, while still maintaining a hydrodynamic gear case shape that minimizes resistance.

[0033] In the above description, certain terms are used for brevity, clarity, and ease of understanding. No unnecessary limitations beyond the requirements of the prior art should be inferred from these terms, for they are used for illustrative purposes and are intended to be interpreted broadly. The various systems and method steps described herein may be used alone or in combination with other systems and methods. For experts, it is expected that various equivalents, alternative forms, and modifications are possible within the scope of the appended claims.

[0034] One of the following examples of implementations of the planetary gear set 27 according to the present invention shows the structure of this planetary gear set 27 in a transmission 26 as a power reverser in a tractor power transmission system 114 or another vehicle, located at the input of the drive train, or in the middle of the drive train, or near the output of the drive train, as shown, for example, in Figures 13, 14, and 15.

[0035] Figure 13 shows an example of the implementation configuration of the tractor power transmission system 114, in which the transmission 26 is located directly behind the internal combustion engine 18, which has a torsional vibration damper 116.

[0036] Behind the transmission 26, a multi-speed transmission 118, a range-change transmission 120, and the remaining vehicle drive train 124 may follow.

[0037] The forward brake 46 and the reverse brake 48 may be, for example, wet multi-plate brakes, as is common in automatic transmissions.

[0038] The transmission 26 may have a power take-off shaft 122 connected to the hollow of the input shaft 38 and the output shaft 40, allowing the power take-off shaft 122 or another shaft, such as for an oil pump 136, to pass through this hollow.

[0039] Figure 14 shows an example of an implementation where the transmission 26 is located in the middle of the tractor power transmission system 114. The transmission 26 is located behind the internal combustion engine 18, which has a torsional vibration damper 116, and behind the multi-speed transmission 118, and therefore in front of the range-change transmission 120 and the rest of the vehicle drive train 124, which may have a final drive, the final drive having a hub reduction gearing and transfer case for all-wheel drive.

[0040] Figure 15 shows an example of an implementation in the tractor power transmission system 114 in which the transmission 26 is located behind the internal combustion engine 18 with a torsional vibration damper 116, the continuously variable transmission 126 and the power split planetary gear set 128 and then the range change transmission 120. Behind the transmission 26 is the rest of the vehicle drive train 124.

[0041] In another example for a different vehicle, instead of the continuously variable transmission 126 with the power split planetary gear set 128, there may be a continuously variable transmission 126 alone or a multi-speed transmission 118. Also, instead of the range-change transmission 120, there may be a continuously variable transmission 126 with the power split planetary gear set 128, or a continuously variable transmission 126 alone, or a single-speed drive or direct drive before the rest of the vehicle's drive train 124.

[0042] The planetary gear set 27 can also be used in heavy machinery, particularly in the wheel loader transmission 130, as shown in Figure 16.

[0043] Figure 17 shows an example of an implementation configuration of a wheel loader transmission 130, where the internal combustion engine 18, which has a torque converter 130, is located in front of the transmission 26, which is reinforced by a direct drive clutch 134. In this case, behind the transmission 26 are the range change transmission 120 and the rest of the vehicle drive train 124.

[0044] The input shaft 38 may be hollow, allowing a power take-off shaft 122 or another shaft, such as an oil pump 136, to pass through this hollow.

[0045] In another example, the transmission 26 may be used with the input shaft 38 swapped with the output shaft 40 for speed amplification, in which case the gear ratio, and therefore the ratio of input speed to output speed, is -0.6 or 0.6.

[0046] Figures 18 and 19 show a planetary gear set 27, in which multiple supplementary planetary gears 86 are positioned coaxially with multiple main planetary gears 62 such that each main planetary gear 62 is positioned inside each supplementary planetary gear 86, and are rotatable around the central axis 88 of the supplementary planetary gear 86 itself, which is the same as the central axis 64 of the main planetary gear 62.

[0047] Figure 20 shows a planetary gear set 27, in which multiple main planetary gears 62 are located between multiple supplementary planetary gears 86, and the central axis 88 of the supplementary planetary gears 86 is not the same as the central axis 64 of the main planetary gears 62.

[0048] Figure 21 shows a planetary gear set 27 having multiple supplemental planetary gears 86, some of which are coaxially aligned with the main planetary gears 62 such that these main planetary gears 62 are positioned inside each supplemental planetary gear 86, and are rotatable around the same central axis 88 of the supplemental planetary gear 86 as the central axis 64 of the main planetary gears 62. The other main planetary gears 62 are positioned between the supplemental planetary gears 86. [Explanation of Symbols]

[0049] 10-10 Cross section 11. Outboard propulsion devices 12 Ships 14 transom 16 Transom Bracket 18 Internal Combustion Engine 20 Upper cowling 22 Drive shaft 24 Drive shaft housing 26 transmission 27 Planetary Gear Set 28 Propulsion shaft 30 Propulsion system shaft housing 32 Gear case housing 34 Propulsion device 36 Reverse Rotating Propeller 38 Input shafts 40 Output shaft 42 Main Planetary Gear Set 44 Supplemental Planetary Gear Set 46 Forward brake 48 Reverse brake 50 Main ring gear 52 Radially inward gear surface 54 Primary Solar Gear 55 Lower casing expansion section 56 Radially outward gear surface 58 Radially inward bearing surface 59 Roller bearing 60 Forward Brake Drum 62 Main Planetary Gear 64 Center axis 66 Radially outward gear surface 67 Radially outward gear surface 68 Main Carrier 74 Supplementary Solar Gear 76 Radially outward gear surface 78 Supplementary Ring Gear 84 Radially inward gear surface 86 Supplemental Planetary Gear 88 Center axis 90 Radially outward gear surface 92 Planetary bearings 94 Reverse brake drum 96 Actuator 97 Bearings 98 Servo motor 99 Upper casing expansion section 100 pins 102 Arrow 103 Arrow 104 Bearing bracket 105 Arrow 106 Gear Case Enclosure 108 Feathered wing 110 Reverse Lubrication Pump 112 Cooling water pump 114 Tractor Power Transmission System 116 Torsional vibration damper 118 Multi-speed transmission 120 Range-shift transmission 122 Power Take-Off Shaft 124 Remaining vehicle drive train 126 Continuously Variable Transmission 128 Powered Planetary Gear Set 130 Wheel Loader Transmission 130 Torque Converter 134 Direct drive clutch 136 Oil pump

Claims

1. A planetary gear set consisting of a main planetary gear set and a supplementary planetary gear set, The aforementioned main planetary gear set comprises a main ring gear, and the main ring gear comprises a radially inward gear surface. The main planetary gear further comprises a main sun gear disposed coaxially with the main ring gear, and the main sun gear has a radially outward-facing gear surface. The main planetary gear further comprises a plurality of main planetary gears, each of which is rotatable about its own central axis, and is radially arranged between the main ring gear and the main sun gear, each of which has a radially outward gear surface, the radially outward gear surface engaging with the radially inward gear surface of the main ring gear, and the main planetary gear also has another radially outward gear surface that engages with the radially outward surface of the main sun gear, The main planetary gear set further comprises a main carrier, the main carrier holding the main planetary gear and being rotatable relative to the main ring gear and the main sun gear. The supplemental planetary gear set comprises a supplemental sun gear, and the supplemental sun gear comprises a radially outward-facing gear surface. The supplemental planetary gear set further comprises a supplemental ring gear, the supplemental ring gear having a radially inward gear surface, The supplemental planetary gear set further comprises a plurality of supplemental planetary gears, each of which is rotatable about its own central axis, and is radially arranged between the supplemental ring gear and the supplemental sun gear, with each supplemental planetary gear having a radially outward gear surface, the radially outward gear surface engaging with the radially inward surface of the supplemental ring gear and the radially outward surface of the supplemental sun gear. A planetary gear set characterized by the following:

2. Each of the aforementioned main planetary gears is arranged coaxially inside each of the aforementioned supplementary planetary gears. The aforementioned supplemental planetary gear set further comprises interplanetary bearings, The supplementary planetary gear is held by the interplanetary bearing, the main planetary gear, and the main carrier, and rotates around the same central axis as the main planetary gear. The planetary gear set according to claim 1.

3. The main planetary gear is disposed between the supplemental sun gear and the supplemental ring gear, and simultaneously, the supplemental planetary gear is disposed between the main planetary gears. The supplementary planetary gear is held by the main carrier and rotates around the central axis of the supplementary planetary gear itself. The planetary gear set according to claim 1.

4. The main carrier is fixed to the output shaft and rotates together with the output shaft. The main ring gear is fixed to the input shaft and rotates together with the input shaft. The supplemental sun gear is fixed to the main sun gear and rotates together with the main sun gear. The planetary gear set according to claim 2.

5. The main carrier is fixed to the output shaft and rotates together with the output shaft. The main ring gear is fixed to the input shaft and rotates together with the input shaft. The supplemental sun gear is fixed to the main sun gear and rotates together with the main sun gear. The planetary gear set according to claim 3.

6. A transmission for a ship propulsion device having an internal combustion engine that drives a propulsion system for propelling a ship on water, wherein the transmission is An input shaft driven and rotated by the aforementioned engine, The output shaft that drives the propulsion device, A main planetary gear set connects the input shaft to the output shaft so as to drive the output shaft to rotate it forward, A supplementary planetary gear set is provided to connect the input shaft to the output shaft together with the main planetary gear set, so as to drive the output shaft to rotate it in reverse, In a forward gear in which the main planetary gear set drives the output shaft to rotate forward, the forward brake engages the main planetary gear set, In a reverse gear in which the supplementary planetary gear set drives the output shaft together with the main planetary gear set to rotate in reverse, the reverse brake engages the supplementary planetary gear set and Equipped with, Regardless of whether the forward brake or the reverse brake is applied, the output shaft does not engage the neutral gear, which is separated from the input shaft. The main planetary gear set comprises a main ring gear fixed to the input shaft and rotating together with the input shaft, the main ring gear having a radially inward gear surface, The main planetary gear set further comprises a main sun gear coaxially arranged on the lower casing extension, and the main sun gear has a radially outward-facing gear surface. The main sun gear has a radially inward bearing surface, and the radially inward bearing surface supports the lower casing extension so that the main sun gear is rotatable relative to the lower casing extension. The aforementioned main planetary gear set further comprises a forward brake drum that rotates together with the main sun gear, The main planetary gear set further comprises a plurality of main planetary gears, each of which is rotatable about its own central axis, and is radially arranged between the main ring gear and the main sun gear, and each of the plurality of main planetary gears has a radially outward gear surface, the radially outward gear surface engages with the radially inward gear surface of the main ring gear, and the main planetary gear also has another radially outward gear surface that engages with the radially outward gear surface of the main sun gear, The main planetary gear set further comprises a main carrier that holds the plurality of main planetary gears, the main carrier being fixed to the output shaft and rotating together with the output shaft, and the main carrier being rotatable relative to the main ring gear and the main sun gear. The supplemental planetary gear set includes a supplemental sun gear, which is fixed to the main sun gear and the forward brake drum, rotates together with the main sun gear and the forward brake drum, and the supplemental sun gear has a radially outward-facing gear surface. The supplemental planetary gear set further comprises a supplemental ring gear, the supplemental ring gear being fixed to the reverse brake drum and rotating together with the reverse brake drum, and the supplemental ring gear having radially inward gear surfaces, The supplemental planetary gear set further comprises a plurality of supplemental planetary gears, the plurality of supplemental planetary gears are coaxially aligned with the plurality of main planetary gears such that each main planetary gear is disposed inside each supplemental planetary gear, the plurality of supplemental planetary gears are rotatable about the central axis of the plurality of supplemental planetary gears themselves, are radially disposed between the supplemental ring gear and the supplemental sun gear, each of the plurality of supplemental planetary gears has a radially outward gear surface, the radially outward gear surface engages with the radially inward gear surface of the supplemental ring gear and the radially outward gear surface of the supplemental sun gear, The supplemental planetary gear set further comprises interplanetary bearings, and further uses the main planetary gear and the main carrier to hold the supplemental planetary gear, so that the supplemental planetary gear can rotate around its own central axis, which is the same as the central axis of the main planetary gear. In neutral gear, the rotation of the input shaft does not cause the rotation of the output shaft. In the neutral gear, the forward rotation of the input shaft causes the main ring gear to rotate forward, the forward rotation of the main ring gear causes the plurality of main planetary gears to rotate forward, the forward rotation of the plurality of main planetary gears causes the main sun gear, the forward brake drum and the supplemental sun gear to rotate backward, the backward rotation of the main sun gear, the forward brake drum and the supplemental sun gear further causes the plurality of supplemental planetary gears to rotate forward, and the forward rotation of the plurality of supplemental planetary gears causes the supplemental ring gear and the reverse brake drum to rotate forward. A transmission characterized by the following features.

7. It further comprises a reverse brake drum that rotates together with the aforementioned supplementary ring gear. The transmission according to claim 6.

8. The forward brake and the reverse brake are band brakes that act on the forward brake drum and the reverse brake drum, respectively. The transmission according to claim 7.

9. At least one of the forward brake and the reverse brake is equipped with a double-wrap band brake. The transmission according to claim 8.

10. The system further comprises an actuator for operating at least one of the forward brake or the reverse brake. The transmission according to claim 7.

11. In the aforementioned forward gear, The forward brake drum and the main sun gear are held stationary by the forward brake. The forward rotation of the input shaft causes the forward rotation of the main ring gear, and the forward rotation of the main ring gear causes the forward rotation of the plurality of main planetary gears, as well as the forward rotation of the main carrier and the output shaft. The transmission according to claim 6.

12. In the aforementioned reverse gear, The supplementary ring gear is held stationary by the reverse brake, The forward rotation of the input shaft causes the main ring gear to rotate forward, and the forward rotation of the main ring gear causes the forward rotation of the multiple main planetary gears, as well as the reverse rotation of the main sun gear, the forward brake drum, and the supplemental sun gear, which in turn causes the forward rotation of the multiple supplemental planetary gears, as well as the reverse rotation of the main carrier and the output shaft. The transmission according to claim 11.

13. The rotation of the input shaft simultaneously directly powers the main planetary gear set via the main ring gear and indirectly powers the supplemental planetary gear set via the main planetary gear set. The transmission according to claim 12.

14. The rotation of the input shaft simultaneously directly powers the main gear set and indirectly powers the supplemental planetary gear set. The transmission according to claim 6.

15. The output shaft and the input shaft are aligned coaxially. The transmission according to claim 6.

16. The system comprises a first bearing that supports the forward brake drum and a second bearing that supports the reverse brake drum, and the first bearing and the second bearing are coaxially aligned. The transmission according to claim 15.

17. The system includes a reverse lubrication pump, and the reverse lubrication pump is connected to the output shaft such that rotation of the output shaft in any direction powers the reverse lubrication pump. The transmission according to claim 6.

18. The system includes a water pump connected to the input shaft, and the rotation of the input shaft provides power to the water pump. The transmission according to claim 6.

19. A transmission for a ship propulsion device having an internal combustion engine that drives a propulsion system for propelling a ship on water, wherein the transmission is An input shaft driven and rotated by the aforementioned engine, An output shaft that drives and rotates the propulsion device, A main planetary gear set connects the input shaft to the output shaft so as to drive the output shaft to rotate it forward, A supplementary planetary gear set connects the input shaft to the output shaft together with the main planetary gear set, so as to drive the output shaft to rotate it in reverse, In a forward gear in which the main planetary gear set drives the output shaft to rotate forward, the forward brake engages the main planetary gear set, In a reverse gear in which the supplementary planetary gear set drives the output shaft together with the main planetary gear set to rotate in reverse, the gear is further equipped with a reverse brake that engages the supplementary planetary gear set. The aforementioned main planetary gear set is, A main ring gear fixed to the input shaft and rotating together with the input shaft, the main ring gear having a radially inward gear surface, A main sun gear coaxially disposed on the lower casing extension, comprising a main sun gear having a radially outward-facing gear surface, The main sun gear is rotatable relative to the lower casing extension, and the lower casing extension is supported by a radially inward bearing surface, A forward brake drum that rotates together with the main sun gear, A plurality of main planetary gears, wherein the plurality of main planetary gears are rotatable about the central axis of the plurality of main planetary gears themselves, are arranged radially between the main ring gear and the main sun gear, and each of the plurality of main planetary gears has a radially outward gear surface, the radially outward gear surface engages with the radially inward gear surface of the main ring gear, and the main planetary gear also has another radially outward gear surface that engages with the radially outward gear surface of the main sun gear, A main carrier holding the plurality of main planetary gears, wherein the main carrier is fixed to the output shaft and rotates together with the output shaft, and the main carrier is rotatable relative to the main ring gear and the main sun gear, In the forward gear, the forward brake drum and the main sun gear are held stationary by the forward brake, the forward rotation of the input shaft causes the forward rotation of the main ring gear, and the forward rotation of the main ring gear causes the forward rotation of the plurality of main planetary gears, as well as the forward rotation of the main carrier and the output shaft. A transmission characterized by the following features.

20. A transmission for a ship propulsion device having an internal combustion engine that drives a propulsion system for propelling a ship on water, An input shaft driven and rotated by the aforementioned engine, The output shaft that drives the propulsion device, A main planetary gear set for connecting the input shaft to the output shaft so as to drive the output shaft to rotate it forward, comprising a main planetary gear set with a main carrier, A supplementary planetary gear set connects the input shaft to the output shaft together with the main planetary gear set, so as to drive the output shaft to rotate it in reverse, In a forward gear in which the main planetary gear set drives the output shaft to rotate forward, the forward brake engages the main planetary gear set, In a reverse gear in which the supplementary planetary gear set drives the output shaft together with the main planetary gear set to rotate in reverse, the reverse brake engages the supplementary planetary gear set and Equipped with, The aforementioned main planetary gear set is, A main ring gear fixed to the input shaft and rotating together with the input shaft, the main ring gear having a radially inward gear surface, A main sun gear coaxially disposed on the lower casing extension, comprising a main sun gear having a radially outward-facing gear surface, The main sun gear is rotatable relative to the lower casing extension, and the lower casing extension is supported by a radially inward bearing surface, A forward brake drum that rotates together with the main sun gear, A plurality of main planetary gears, wherein the plurality of main planetary gears are rotatable about the central axis of the plurality of main planetary gears themselves, are arranged radially between the main ring gear and the main sun gear, and each of the plurality of main planetary gears has a radially outward gear surface, the radially outward gear surface engages with the radially inward gear surface of the main ring gear, and the main planetary gear also has another radially outward gear surface that engages with the radially outward gear surface of the main sun gear, A main carrier holding the plurality of main planetary gears, wherein the main carrier is fixed to the output shaft and rotates together with the output shaft, and the main carrier is rotatable relative to the main ring gear and the main sun gear, The aforementioned supplemental planetary gear set is, A supplementary sun gear fixed to the main sun gear and the forward brake drum, and rotating together with the main sun gear and the forward brake drum, the supplementary sun gear having a radially outward-facing gear surface, A supplementary ring gear fixed to the reverse brake drum and rotating together with the reverse brake drum, comprising a supplementary ring gear having a radially inward gear surface, A plurality of supplemental planetary gears, wherein each of the plurality of supplemental planetary gears is coaxially positioned with the plurality of main planetary gears such that each main planetary gear is disposed inside each of the supplemental planetary gears, and is rotatable about the central axis of the plurality of supplemental planetary gears itself, and is radially arranged between the supplemental ring gear and the supplemental sun gear, and each of the plurality of supplemental planetary gears has a radially outward gear surface, the radially outward gear surface engaging with the radially inward gear surface of the supplemental ring gear and the radially outward gear surface of the supplemental sun gear, A plurality of interplanetary bearings disposed on the main planetary gear and the main carrier, wherein the plurality of interplanetary bearings hold the plurality of supplementary planetary gears so that the supplementary planetary gears can rotate around the central axis of the supplementary planetary gears themselves, which is the same as the central axis of the main planetary gear, It comprises a reverse brake drum that rotates together with the aforementioned supplementary ring gear, In the reverse gear, the supplementary ring gear is held stationary by the reverse brake, the forward rotation of the input shaft causes the forward rotation of the main ring gear, the forward rotation of the main ring gear causes the forward rotation of the plurality of main planetary gears and the reverse rotation of the main sun gear, the forward brake drum and the supplementary sun gear, and also causes the forward rotation of the plurality of supplementary planetary gears and the reverse rotation of the main carrier and the output shaft. A transmission characterized by the following features.

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