JP5291438B2 - Reducer for counter rotating propeller - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a reduction gear for a counter-rotating propeller, using a cross compound type steam turbine as a power engine for uniformly distributing and transmitting the power of a high pressure side output shaft and a low pressure side output shaft to the inner shaft and the outer shaft of a counter-rotating propeller. <P>SOLUTION: The reduction gear for the counter-rotating propeller is provided with: a high pressure side power dividing means 11 for independently dividing the rotating power of the high pressure side output shaft 21 in half; a lower pressure side power dividing means 12 for independently dividing the rotating power of the low pressure side output shaft 22 in half; an inner shaft driving high pressure side power transmitting means 13 for transmitting one high pressure side rotating power divided by the high pressure side power dividing means to the inner shaft 31; an inner shaft driving low pressure side power transmitting means 14 for transmitting one low pressure side rotating power divided by the low pressure side power dividing means to the inner shaft; an outer shaft driving high pressure side power transmitting means 15 for transmitting the other high pressure side rotating power divided by the high pressure side power dividing means to the outer shaft 32 while reversing it; and an outer shaft driving low pressure side power transmitting means 16 for transmitting the other low pressure side rotating power divided by the low pressure side power dividing means to the outer shaft while reversing it. <P>COPYRIGHT: (C)2010,JPO&amp;INPIT

Description

  The present invention relates to a counter gear for a counter rotating propeller for transmitting power to a counter rotating propeller using a cross compound steam turbine as a prime mover.

  For example, Patent Document 1 discloses a conventional counter gear for a counter rotating propeller (a marine counter rotating propeller type propulsion device). This reduction gear for a counter rotating propeller is driven by a cross-compound steam turbine, its high-pressure side output shaft and low-pressure side output shaft, and the outer shaft (bow side propeller shaft) and inner shaft (stern side) of the counter rotating propeller. Propeller shaft). The rotation of the high-pressure side output shaft is transmitted to the high-pressure side drive shaft by meshing between the high-pressure side output gear of the high-pressure side output shaft and the high-pressure side reduction gear of the high-pressure side drive shaft. On the other hand, the rotation of the low pressure side output shaft is transmitted to the low pressure side drive shaft arranged in parallel with the high pressure side drive shaft by meshing with the low pressure side output gear of the low pressure side output shaft and the low pressure side reduction gear of the low pressure side drive shaft. The Each of the high-pressure side drive shaft and the low-pressure side drive shaft is provided with two small gears facing each other between the drive shafts. Among these small gears, the first set of small gears facing each other on the bow side of each drive shaft are meshed with the inner shaft drive gear provided on the inner shaft, and the rotation of the first set of small gears is the inner shaft. It is transmitted to the inner shaft via the drive gear. In addition, the second set of small gears facing each other on the stern side of each drive shaft is engaged with an outer shaft drive gear provided on the outer shaft via a reverse gear, and the rotation of the second set of small gears is performed. It is transmitted to the outer shaft via the outer shaft drive gear while being reversed.

JP-A-7-33084

  However, with the counter gear for the contra-rotating propeller shown in Patent Document 1 described above, it is difficult to distribute the power evenly between the inner shaft and the outer shaft, which is the principle of the counter-rotating propeller. In the reduction gear of Patent Document 1 described above, in order to evenly distribute the power to the inner shaft and the outer shaft, both the high-pressure side and the low-pressure side transmit power by the engagement of the output gear and the reduction gear (A), In relation to each power transmission (b, c) from the small gear to each drive gear, it is necessary that (b) = (b) + (c) and (b) = (c). However, in the speed reduction device of Patent Document 1 described above, the small gears that contribute to power transmission (b) and power transmission (c) are arranged together on one drive shaft. Depending on the degree of meshing and the difference in timing of power transmission, power is preferentially transmitted to one of the drive gears. For this reason, each power transmission (b, c) from each small gear to each drive gear in one drive shaft is not equal to each other.

  In order to match the degree of meshing between each small gear and each driving gear and the timing of power transmission, the physique shape of each small gear on one driving shaft must be the same, and the transmission torque (output and rotation) to each driving gear. Number) is the same, the meshing of each small gear and each driving gear is the same, and the timing of meshing occurs simultaneously, the tooth surface shape of each small gear and each driving gear is the same, cross compound The behavior of each small gear and each drive gear in the transient state and the steady state during operation of the type steam turbine (atmosphere temperature, gear temperature, shaft twist, shaft deflection, gear twist, gear deflection, shaft center) However, it is practically difficult to make these elements appropriate.

  Further, the tooth surface of the gear is subjected to tooth trace correction assuming an actual rated operation. To correct the tooth traces, the transmission torque, ambient temperature, gear temperature, shaft twist, shaft deflection, gear twist, gear deflection, etc. are taken into account along the axial direction so that the gear will have an ideal tooth contact at the time of rating. To correct the tooth surface curve in advance. However, since the gear size and the transmission torque differ depending on the difference in the rotation speed of each propeller and the presence or absence of the reverse gear, the degree of tooth trace correction varies greatly between the small gears.

  For these reasons, the speed reduction device of Patent Document 1 described above cannot prevent power from being preferentially transmitted to any one of the drive gears, and evenly distributes power to the inner shaft and the outer shaft for transmission. Is difficult.

  The present invention solves the above-described problems, and uses a cross-compound steam turbine as a prime mover, and a counter-rotating propeller capable of evenly distributing and transmitting power to an inner shaft and an outer shaft of the counter-rotating propeller. An object of the present invention is to provide a reduction gear for a vehicle.

In order to achieve the above-mentioned object, in the contra-rotating propeller speed reducer of the present invention, the power of the high-pressure side output shaft and the low-pressure side output shaft in the cross-compound steam turbine is converted to the inner shaft and the outer shaft of the counter-rotating propeller. In the counter-rotating propeller speed reducer, the high-pressure side power dividing means for independently dividing the rotational power of the high-voltage side output shaft into two equal parts, and the rotational power of the low-pressure side output shaft are divided into two. A low pressure side power splitting means that divides the power into two independently, and a high pressure side power transmission means for driving the inner shaft that transmits the rotational power of one high pressure side divided by the high pressure side power splitting means to the inner shaft, An inner shaft driving low pressure side power transmission means for transmitting one low pressure side rotational power divided by the low pressure side power split means to the inner shaft, and another high pressure side power split by the high pressure side power split means. Inverted rotational power The outer shaft drive high pressure side power transmission means for transmitting to the outer shaft while the other low pressure side rotational power divided by the low pressure side power split means is reversed and transmitted to the outer shaft while being reversed. Side power transmission means, and the high pressure side power split means meshes with a high pressure side first small gear provided on the high pressure side output shaft, and equally divides the high pressure side power into two independently. The high pressure side first large gear, the low pressure side power splitting means meshes with the low pressure side first small gear provided on the low pressure side output shaft, and the low pressure side power is divided into two independently. It has two low pressure side first large gears that equally divide .
In the counter gear for the counter rotating propeller, the high-pressure side first small gear and the low-pressure side first small gear, and the high-pressure side first large gear and the low-pressure side first large gear are respectively paired with gears. The inclined teeth having an angle with respect to the axis of the inner shaft and the outer shaft of the contra-rotating propeller are arranged symmetrically adjacent to each other.

  According to this contra-rotating propeller speed reducer, on the high pressure side, the power transmission between the one divided by the high pressure side power dividing means and the other is equal. Furthermore, one of the divided power transmissions is equal to the power transmission to the inner shaft by the high-pressure side power transmission means for driving the inner shaft. Furthermore, the other divided power transmission is equal to the power transmission to the outer shaft by the high-voltage side power transmission means for driving the outer shaft. On the low pressure side, the power transmission between the one divided by the low pressure side power dividing means and the other is equal. Further, one of the divided power transmissions is equal to the power transmission to the inner shaft by the low pressure side power transmission means for driving the inner shaft. Furthermore, the other divided power transmission is equal to the power transmission to the outer shaft by the low pressure side power transmission means for driving the outer shaft. As a result, power from the high-pressure side output shaft and the low-pressure side output shaft can be evenly distributed and transmitted to the inner shaft and the outer shaft.

  Further, in the contra-rotating propeller speed reducer according to the present invention, the high pressure side power split means includes the same two high pressure side first large gears meshed with the high pressure side first small gear provided on the high pressure side output shaft. And the low pressure side power split means has the same two low pressure side first large gears meshed with the low pressure side first small gear provided on the low pressure side output shaft. The shaft driving high-pressure side power transmission means is provided on the inner shaft while being provided on the inner shaft driving high-pressure side rotating shaft provided with one of the high-pressure side first large gears, and being provided on the inner shaft driving high-pressure side rotating shaft. An inner shaft driving high pressure side second small gear meshing with the provided inner shaft driving second large gear, and the inner shaft driving low pressure side power transmission means is one of the low pressure side first gears. The inner shaft driving low-pressure side rotating shaft provided with a large gear and the inner shaft driving low-pressure side rotating shaft A second small gear for driving the inner shaft that meshes with the second large gear for driving the shaft, and the high pressure side power transmission means for driving the outer shaft is provided with the other first high gear on the high pressure side. The outer shaft driving high pressure side rotating shaft, the outer shaft driving high pressure side second small gear provided on the outer shaft driving high pressure side rotating shaft, the outer shaft driving high pressure side second small gear, and the The second large gear for driving the outer shaft engages with the second large gear for driving the outer shaft provided on the outer shaft and reverses the rotational power transmitted by the second small gear for driving the outer shaft. A low pressure side power transmission means for driving the outer shaft, the low pressure side rotary shaft for driving the outer shaft provided with the other low pressure side first large gear, and the outer A low-pressure side second small gear for driving the outer shaft provided on the low-pressure side rotary shaft for shaft driving, the low-pressure side second small gear for driving the outer shaft, and the outer A low-pressure side reversing gear that meshes with the driving second large gear and reverses the rotational power transmitted by the low-pressure side second small gear for driving the outer shaft while transmitting to the second large gear for driving the outer shaft. It is characterized by having.

  According to this contra-rotating propeller speed reducer, the counter-rotating propeller speed reducer capable of evenly distributing and transmitting the power of the high-pressure side output shaft and the low-pressure side output shaft to the inner shaft and the outer shaft. Can be realized.

  Further, in the contra-rotating propeller speed reducer of the present invention, the outer diameters of the inner shaft and the outer shaft provided with the drive gears are formed larger in diameter than other parts, and The large-diameter portion that is formed to project from the drive gear in the extending direction of the inner shaft and the outer shaft, and the large-diameter portion is supported in a manner of receiving a load in the extending direction of the inner shaft and the outer shaft. And a thrust bearing portion.

  According to the counter gear for the contra-rotating propeller, since the thrust bearing portion is incorporated into the configuration of each drive gear and unitized, the internal gear is compared with the configuration in which the thrust bearing portion is separately arranged with respect to the drive gear. The extension length of the shaft and the outer shaft can be shortened. As a result, the apparatus can be reduced in size, and the space efficiency can be improved in the engine room where the installation space is limited.

  The contra-rotating propeller speed reducer according to the present invention includes a housing that accommodates the inner shaft and the outer shaft, and the housing forms a case of the thrust bearing portion.

  According to the counter gear for the contra-rotating propeller, since a part of the housing can be configured as a case of the thrust bearing portion, the device can be further downsized.

  According to the present invention, power from the high-pressure side output shaft and the low-pressure side output shaft in the cross-compound steam turbine can be evenly distributed and transmitted to the inner shaft and the outer shaft of the counter rotating propeller.

  Hereinafter, embodiments of a speed reducer for a counter rotating propeller according to the present invention will be described in detail with reference to the drawings. Note that the present invention is not limited to the embodiments. In addition, constituent elements in the following embodiments include those that can be easily replaced by those skilled in the art or those that are substantially the same.

  FIG. 1 is a schematic development view of a speed reducer for a counter rotating propeller according to an embodiment of the present invention, and FIG. 2 is a schematic perspective view of the speed reducer for a counter rotating propeller shown in FIG.

  A counter gear 1 for a counter rotating propeller (hereinafter referred to as a speed reducing device) 1 according to the present embodiment is for transmitting power to the counter rotating propeller 3 using a cross compound steam turbine 2 as a prime mover. Further, the counter gear 1 for counter rotating propeller, the cross-compound steam turbine 2 and the counter rotating propeller 3 are applied to a ship to which propulsive force is applied.

  The cross-compound steam turbine 2 is a tandem compound type in which a high-pressure turbine, an intermediate-pressure turbine, and a low-pressure turbine are arranged on one axis by using a high-pressure turbine, an intermediate-pressure turbine, and a low-pressure turbine divided into two shafts, a primary and a secondary. Compared with a steam turbine, the output can be easily increased and the thermal efficiency can be improved. In the cross-compound steam turbine 2 of the present embodiment, a high pressure and an intermediate pressure are disposed on a high pressure side output shaft (primary shaft) 21 as a high pressure side turbine 2A, and a low pressure is disposed on a low pressure side output shaft (secondary shaft) as a low pressure side turbine 2B. (Axis) 22. The high voltage side output shaft 21 and the low voltage side output shaft 22 are provided in parallel.

  In the contra-rotating propeller 3, propellers (screws) 31 a and 32 a are respectively arranged on an inner shaft 31 and an outer shaft 32 configured on the same axis, and the shafts 31 and 32 are rotated in opposite directions. Thus, counter torque applied to the hull is offset, and propeller efficiency is improved. In the contra-rotating propeller 3 of the present embodiment, the propeller 31a disposed on the inner shaft 31 is provided on the stern side, and the propeller 32a disposed on the outer shaft 32 is provided on the bow side.

  A reduction gear device 1 according to the present embodiment is interposed between a cross-compound steam turbine 2 and a counter-rotating propeller 3, and transmits power from a high-pressure side output shaft 21 and a low-pressure side output shaft 22 to an inner shaft 31. It is transmitted separately to the outer shaft 32. The reduction gear 1 includes a high pressure side power split means 11, a low pressure side power split means 12, an inner shaft drive high pressure side power transmission means 13, an inner shaft drive low pressure side power transmission means 14, and an outer shaft drive. The high pressure side power transmission means 15 and the low pressure side power transmission means 16 for driving the outer shaft are configured.

  The high-pressure side power dividing means 11 divides the rotational power of the high-pressure side output shaft 21 into two equal parts independently. The high pressure side power split means 11 has the same two high pressure side first large gears 11 a and 11 b that respectively mesh with a high pressure side first small gear 21 a provided on the high pressure side output shaft 21.

  The low pressure side power split means 12 divides the rotational power of the low pressure side output shaft 22 into two equal parts independently. The low-pressure side power split means 12 has the same two low-pressure side first large gears 12a and 12b that respectively mesh with a low-pressure side first small gear 22a provided on the low-pressure side output shaft 22.

  The inner shaft driving high pressure side power transmission means 13 transmits one rotational power divided by the high pressure side power dividing means 11 to the inner shaft 31. The inner shaft driving high pressure side power transmission means 13 includes an inner shaft driving high pressure side rotating shaft 13 a provided with one high pressure side first large gear 11 a and an inner shaft driving second large shaft provided on the inner shaft 31. The inner shaft driving high-pressure side second small gear 13b is provided on the inner shaft driving high-pressure side rotating shaft 13a while meshing with the gear 31b. The high-pressure side rotary shaft 13a for driving the inner shaft is configured as a flexible shaft having flexibility, and meshing between the high-pressure side first small gear 21a and the one high-pressure side first large gear 11a and driving the inner shaft. Static / dynamic misalignment due to meshing of the high-pressure side second small gear 13b and the second large gear 31b for driving the inner shaft and torsional vibration from the propeller 31a are absorbed by bending.

  The inner shaft driving low-pressure side power transmission means 14 transmits one rotational power divided by the low-pressure side power dividing means 12 to the inner shaft 31. The inner shaft driving low pressure side power transmission means 14 is engaged with the inner shaft driving low pressure side rotating shaft 14a provided with one low pressure side first large gear 12a and the inner shaft driving second large gear 31b. It has an inner shaft driving low pressure side second small gear 14b provided on the shaft driving low pressure side rotating shaft 14a. The low pressure side rotary shaft 14a for driving the inner shaft is configured as a flexible shaft having flexibility, and meshing between the low pressure side first small gear 22a and the one low pressure side first large gear 12a, and inner shaft driving. Static / dynamic misalignment due to engagement of the low-pressure side second small gear 14b and the second large gear 31b for driving the inner shaft and torsional vibration from the propeller 31a are absorbed by bending.

  The outer shaft driving high-pressure side power transmission means 15 transmits the other rotational power divided by the high-pressure side power dividing means 11 to the outer shaft 32 while inverting it. The outer shaft driving high pressure side power transmission means 15 includes an outer shaft driving high pressure side rotating shaft 15a provided with the other high pressure side first large gear 11b and an outer shaft driving high pressure side rotating shaft 15a. A high-pressure side second small gear 15b for driving the shaft, a high-pressure side reversing gear 15c that meshes with the high-pressure side second small gear 15b for driving the outer shaft and the second large gear 32b for driving the outer shaft provided on the outer shaft 32. Have. The high-pressure side reversing gear 15c reverses the rotational power transmitted by the outer shaft driving high-pressure side second small gear 15b and transmits it to the outer shaft driving second large gear 32b. Further, the outer shaft driving high-pressure side rotating shaft 15a is configured as a flexible shaft having flexibility, and between the other high-pressure side first large gear 11b and the outer shaft driving high-pressure side second small gear 15b. Since the gear coupling 15d for connecting the flexible shafts is provided at the part, the engagement between the high-pressure side first small gear 21a and the other high-pressure side first large gear 11b and the high-pressure side for driving the outer shaft The meshing static / dynamic misalignment of the second small gear 15b, the high-pressure side reversing gear 15c, and the second large gear 32b for driving the outer shaft, and the torsional vibration from the propeller 32a are bent and absorbed by the gear coupling 15d.

  The low pressure side power transmission means 16 for driving the outer shaft transmits the other rotational power divided by the low pressure side power dividing means 12 to the outer shaft 32 while inverting it. The outer shaft driving low pressure side power transmission means 16 includes an outer shaft driving low pressure side rotating shaft 16a provided with the other low pressure side first large gear 12b and an outer shaft driving low pressure side rotating shaft 16a. The shaft driving low pressure side second small gear 16b, and the low pressure side second small gear 16b for driving the outer shaft and the low pressure side reversing gear 16c meshing with the second large gear 32b for driving the outer shaft are provided. The low-pressure side reversing gear 16c reverses the rotational power transmitted by the low-pressure side second small gear 16b for driving the outer shaft and transmits it to the second large gear 32b for driving the outer shaft. Further, the low pressure side rotary shaft 16a for driving the outer shaft is configured as a flexible shaft having flexibility, and between the other low pressure side first large gear 12b and the low pressure side second small gear 16b for driving the outer shaft. And having the gear coupling 16d for connecting the flexible shafts to each other, the engagement between the low-pressure side first small gear 22a and the other low-pressure side first large gear 12b, and the low-pressure side for driving the outer shaft The meshing static / dynamic misalignment of the second small gear 16b, the low-pressure side reversing gear 16c, and the second large gear 32b for driving the outer shaft, and the torsional vibration from the propeller 32a are bent and absorbed by the gear coupling 16d.

  The gears 11a, 11b, 12a, 12b, 13b, 14b, 15b, 15c, 16b, 16c, 21a, 22a, 31b, and 32b described above are formed by adjacent gear pairs. In the gear pair, the inclined teeth having an angle with respect to the axis S are arranged symmetrically adjacent to each other. For this reason, in meshing with other gears, the tooth contact is dispersed, torque fluctuation is small, and deviation in the thrust direction can be offset between the inclined teeth of the gear pair.

  The transmission of the rotational power by the reduction gear 1 described above will be described. Rotational power from the high pressure side output shaft 21 of the high pressure side turbine 2A is equally divided into two independently by meshing the high pressure side first small gear 21a with the two high pressure side first large gears 11a and 11b. . The divided high-pressure side rotational power is transmitted from one high-pressure side first large gear 11a to the inner-shaft driving high-pressure side rotating shaft 13a, and the inner power provided on the inner-shaft driving high-pressure side rotating shaft 13a is transmitted. The shaft driving high-pressure side second small gear 13b is transmitted to the inner shaft 31 by meshing with the inner shaft driving second large gear 31b. Further, the divided rotary power on the other high pressure side is transmitted from the other high pressure side first large gear 11b to the outer shaft driving high pressure side rotating shaft 15a and provided on the outer shaft driving high pressure side rotating shaft 15a. The outer shaft 32 is rotated while its rotation is reversed by the meshing of the outer shaft driving high-pressure side second small gear 15b with the high-pressure side reversing gear 15c and the high-pressure side reversing gear 15c with the second large gear 32b for driving the outer shaft. Is transmitted to.

  The rotational power from the low pressure side output shaft 22 of the low pressure side turbine 2B is equally divided into two independently by meshing of the two low pressure side first large gears 12a, 12b of the low pressure side first small gear 22a. The divided one low-pressure side rotational power is transmitted from one low-pressure side first large gear 12a to the inner-shaft driving low-pressure side rotating shaft 14a, and the inner power provided to the inner-shaft driving low-pressure side rotating shaft 14a is transmitted. The shaft driving low-pressure side second small gear 14b is transmitted to the inner shaft 31 by meshing with the inner shaft driving second large gear 31b. The other divided low-pressure side rotational power is transmitted from the other low-pressure side first large gear 12b to the outer shaft driving low-pressure side rotating shaft 16a and provided on the outer shaft driving low-pressure side rotating shaft 16a. The outer shaft 32 is rotated while its rotation is reversed by the meshing of the low pressure side second small gear 16b for driving the outer shaft with the low pressure side reversing gear 16c and the engagement of the low pressure side reversing gear 16c with the second large gear 32b for driving the outer shaft. Is transmitted to.

  The rotational power to the high pressure side output shaft 21 by the high pressure side turbine 2A is different from the rotational power to the low pressure side output shaft 22 by the low pressure side turbine 2B. Therefore, in the reduction gear 1 of the present embodiment, the rotational power transmitted by the meshing of the high pressure side first large gears 11a, 11b and the high pressure side first small gear 21a of the high pressure side power split means 11 and the low pressure side The rotary power transmitted by the meshing of the low pressure side first large gears 12a, 12b and the low pressure side first small gear 22a of the power split means 12 is configured to be equal. For this reason, the one high-pressure side rotational power divided by the high-pressure side power dividing means 11 and the one low-pressure side rotational power divided by the low-pressure side power dividing means 12 become equal, and each rotational power is stored in the interior. It can be transmitted to the shaft 31. Similarly, the other high-pressure side rotational power divided by the high-pressure side power splitting means 11 is equal to the other low-pressure side rotational power split by the low-pressure side power splitting means 12, and the respective rotational powers are separated from each other. It can be transmitted to the shaft 32.

  As described above, in the contra-rotating propeller speed reduction device 1 of the above-described embodiment, the rotational power of the high-pressure side output shaft 21 is equally divided into two directions, and the rotational power of the low-pressure side output shaft 22 is divided. After being divided equally in two directions, the divided high pressure side rotational power and the divided low pressure side rotational power are transmitted to the inner shaft 31, and the other divided high pressure side The rotational power and the divided rotational power on the other low-pressure side are respectively inverted and transmitted to the outer shaft 32.

  According to the reduction gear 1 for the counter rotating propeller, on the high pressure side, power transmission (d) from the high pressure side first small gear 21a to the one high pressure side first large gear 11a and the high pressure side first small gear 21a are performed. Power transmission to the other high-pressure side first large gear 11b (e), power transmission from the high-pressure side second small gear 13b for inner shaft driving to the second large gear 31b for inner shaft driving (f), In relation to the power transmission (g) from the shaft driving high-pressure side second small gear 15b to the outer shaft driving second large gear 32b via the high-pressure side reversing gear 15c, (d) = (e), (d ) = (F), (e) = (g). On the low pressure side, power is transmitted from the low pressure side first small gear 22a to one low pressure side first large gear 12a, and from the low pressure side first small gear 22a to the other low pressure side first large gear 12b. Power transmission (re), power transmission from the low pressure second small gear 14b for inner shaft driving to the second large gear 31b for inner shaft driving, and low pressure second small gear 16b for outer shaft driving. In relation to the power transmission (le) to the second large gear 32b for driving the outer shaft through the low-pressure side reversing gear 16c, (h) = (re), (h) = (nu), (re) = ( Le). As a result, the power from the high-pressure side output shaft 21 and the low-pressure side output shaft 22 can be evenly distributed and transmitted to the inner shaft 31 and the outer shaft 32.

  3 is a cross-sectional view taken along the axis of the contra-rotating propeller, and FIG. 4 is a diagram of the counter-rotating propeller reduction device viewed from the stern side.

  As shown in FIGS. 1 to 3, in the contra-rotating propeller speed reduction device 1 of the present embodiment, the inner shaft 31 has an outer diameter at a portion where the second large gear 31 b for driving the inner shaft is provided. An inner diameter formed larger than that of the other portion of the shaft 31 and projecting in the extending direction of the inner shaft 31 (the extending direction of the shaft center S) from the second large gear 31b for driving the inner shaft. The shaft has a large diameter portion 31c. The inner shaft large-diameter portion 31 c is supported by the inner shaft thrust bearing portion 17 that receives a load in the extending direction of the inner shaft 31.

  Further, the outer shaft 32 is formed such that the outer diameter of the portion where the second large gear 32b for driving the outer shaft is provided is larger than that of the other portion of the outer shaft 32, and the second outer shaft driving second gear 32b. An outer shaft large-diameter portion 32c is formed so as to protrude from the large gear 32b in the extending direction of the outer shaft 32 (the extending direction of the shaft center S). The outer shaft large diameter portion 32 c is supported by the outer shaft thrust bearing portion 18 that receives a load in the extending direction of the outer shaft 32.

  The main thrust of the propeller 31a of the inner shaft 31 is propagated to the hull (not shown) through the inner shaft large diameter portion 31c and the inner shaft thrust bearing portion 17. The main thrust of the propeller 32a of the outer shaft 32 (the load of the outer shaft 32) propagates to the hull (not shown) via the outer shaft large diameter portion 32c and the outer shaft thrust bearing portion 18.

  According to the counter gear 1 for the counter rotating propeller, the thrust bearing portions 17 and 18 that receive a load in the extending direction of the inner shaft 31 and the outer shaft 32 (extending direction of the shaft center S) are provided on each drive gear 31b. , 32b is configured to support the large-diameter portions 31c, 32c provided in the portion, the thrust bearing portions 17, 18 are incorporated into the configuration of the drive gears 31b, 32b and unitized. become. For this reason, compared with the structure which has arrange | positioned the thrust bearing parts 17 and 18 separately with respect to each drive gear 31b and 32b, the extension length of the inner shaft 31 and the outer shaft 32 can be shortened. As a result, the reduction gear 1 can be reduced in size, and the space efficiency can be improved in the hull engine room where the installation space is limited.

  As shown in FIGS. 3 and 4, the contra-rotating propeller speed reduction device 1 of the present embodiment includes a housing 19 a that houses the inner shaft 31 and the outer shaft 32. The housing 19a also serves as a case for housing the thrust bearing portions 17 and 18. The housing 19a is fixed to a block 19b fixed to the hull (not shown) of the hull. Along with the inner shaft 31 and the outer shaft 32, the block 19b houses a lower portion of the second large gear 31b for driving the inner shaft and a lower portion of the second large gear 32b for driving the outer shaft. Moreover, the housing 19a which makes the case of the thrust bearing parts 17 and 18 is supported by the hull side by being connected to the leg part 19c extended from the ship's grain. Also, on the upper part of the block 19b, gears 11a, 11b, 12a, 12b, 13b, 14b, 15b, 15c, 16b, 16c, 21a, 22a, 31b, 32b and shafts 13a, 14a, 15a, 16a are provided. A cover member 19d for covering is attached.

  According to the counter gear 1 for the contra-rotating propeller, the housing 19a that accommodates the inner shaft 31 and the outer shaft 32 forms a case that covers the thrust bearing portions 17 and 18, whereby a part of the housing 19a is replaced with the thrust bearing portion 17. , 18 cases, the apparatus can be further downsized.

  As described above, the counter gear for the counter rotating propeller according to the present invention uses the cross compound steam turbine as a prime mover, and distributes and distributes the power evenly between the inner shaft and the outer shaft of the counter rotating propeller. Is suitable.

1 is a schematic development view of a speed reducer for a counter rotating propeller according to an embodiment of the present invention. It is a schematic perspective view of the speed reducer for counter rotating propellers shown in FIG. It is sectional drawing which follows the axial center of a contra-rotating propeller. It is the figure which looked at the deceleration device for counter rotating propellers from the stern side.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Deceleration apparatus for counter rotating propellers 11 High pressure side power split means 11a, 11b High pressure side first large gear 12 Low pressure side power split means 12a, 12b Low pressure side first large gear 13 High pressure side power transmission means 13a for inner shaft drive High-pressure side rotating shaft 13b for shaft driving High-pressure side second small gear for driving inner shaft 14 Low-pressure side power transmission means for driving inner shaft 14a Low-pressure side rotating shaft for driving inner shaft 14b Low-pressure side second small gear for driving inner shaft 15 Outside High-pressure side power transmission means for shaft drive 15a High-pressure side rotary shaft for outer shaft drive 15b High-pressure side second small gear for outer shaft drive 15c High-pressure side reversing gear 15d Gear coupling 16 Low-pressure side power transmission means for outer shaft drive 16a Outer shaft Low-pressure side rotating shaft for driving 16b Low-pressure side second small gear for driving outer shaft 16c Low-pressure side reversing gear 16d Gear coupling 17 Inner shaft thrust bearing portion 18 Outer shaft thrust bearing portion 19a USING 2 Cross-compound steam turbine 2A High-pressure side turbine 2B Low-pressure side turbine 21 High-pressure side output shaft 21a High-pressure side first small gear 22 Low-pressure side output shaft 22a Low-pressure side first small gear 3 Counter rotating propeller 31 Inner shaft 31a Propeller 31b Inner shaft driving second large gear 31c Inner shaft large diameter portion 32 Outer shaft 32a Propeller 32b Outer shaft driving second large gear 32c Outer shaft large diameter portion

Claims (5)

In the counter gear for the counter rotating propeller that transmits the power of the high pressure side output shaft and the low pressure side output shaft in the cross compound type steam turbine separately to the inner shaft and the outer shaft of the counter rotating propeller,
High pressure side power splitting means for equally dividing the rotational power of the high pressure side output shaft into two independently;
Low pressure side power split means for equally dividing the rotational power of the low pressure side output shaft into two independently;
High pressure side power transmission means for driving an inner shaft for transmitting one high pressure side rotational power divided by the high pressure side power split means to the inner shaft;
An inner shaft driving low pressure side power transmission means for transmitting one of the low pressure side rotational powers divided by the low pressure side power split means to the inner shaft;
An outer shaft driving high pressure side power transmission means for inverting the rotational power of the other high pressure side divided by the high pressure side power split means while transmitting to the outer shaft;
A low-pressure side power transmission means for driving the outer shaft that transmits to the outer shaft while reversing the rotational power on the other low-pressure side divided by the low-pressure side power split means;
Equipped with a,
The high-pressure side power split means has two high-pressure side first large gears that mesh with a high-pressure side first small gear provided on the high-pressure side output shaft and divide the high-pressure side power into two independently. And
The low pressure side power split means has two low pressure side first large gears that mesh with a low pressure side first small gear provided on the low pressure side output shaft and divide the low pressure side power into two independently. Become
A reduction gear for a contra-rotating propeller characterized by the above. The high-pressure side first small gear and the low-pressure side first small gear, and the high-pressure side first large gear and the low-pressure side first large gear respectively correspond to the inner shaft of the contra-rotating propeller and the 2. The speed reducer for a contra-rotating propeller according to claim 1, wherein oblique teeth having an angle with respect to the axis of the outer shaft are arranged symmetrically adjacent to each other. The inner shaft driving high pressure side power transmission means is provided on the inner shaft driving high pressure side rotating shaft provided with one of the high pressure side first large gears, while being provided on the inner shaft driving high pressure side rotating shaft. An inner shaft driving high-pressure side second small gear meshing with an inner shaft driving second large gear provided on the shaft,
The inner shaft driving low pressure side power transmission means is provided on the inner shaft driving low pressure side rotating shaft provided with one of the low pressure side first large gears and the inner shaft driving low pressure side rotating shaft. A low-pressure side second small gear for driving the inner shaft that meshes with the second large gear for driving the shaft,
The outer shaft driving high pressure side power transmission means includes an outer shaft driving high pressure side rotating shaft provided with the other high pressure side first large gear, and an outer shaft provided on the outer shaft driving high pressure side rotating shaft. The high-pressure side second small gear for driving, the high-pressure side second small gear for driving the outer shaft and the second large gear for driving the outer shaft provided on the outer shaft are engaged with the second high-speed side for driving the outer shaft. A high-pressure side reversing gear for reversing the rotational power transmitted by the small gear to the second large gear for driving the outer shaft,
The outer shaft driving low pressure side power transmission means includes an outer shaft driving low pressure side rotating shaft provided with the other low pressure side first large gear, and an outer shaft provided on the outer shaft driving low pressure side rotating shaft. The low pressure side second small gear for driving, the low pressure side second small gear for driving the outer shaft, and the second large gear for driving the outer shaft are engaged with each other and transmitted by the low pressure side second small gear for driving the outer shaft. A low-pressure side reversing gear for reversing the rotating power transmitted to the second large gear for driving the outer shaft,
The speed reducer for a contra-rotating propeller according to claim 1. Outer diameters of the inner shaft and the outer shaft provided with the drive gears are larger in diameter than other portions, and the inner shaft and the outer shaft extend from the drive gears. A large-diameter portion formed protruding in the direction;
A thrust bearing portion that supports the large diameter portion in a manner of receiving a load in the extending direction of the inner shaft and the outer shaft;
The speed reducer for a contra-rotating propeller according to claim 3 . 5. The contra-rotating propeller speed reduction device according to claim 4 , further comprising a housing that accommodates the inner shaft and the outer shaft, wherein the housing forms a case of the thrust bearing portion.

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