JP2013253637A - Transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a transmission allowing the entire structure thereof to be made more compact.SOLUTION: A transmission is equipped with: an input shaft (1); an input side sun gear (31) linked with the input shaft; an output shaft (2); an output side sun gear (32) linked with the output shaft; a pinion gear (33) including an input gear part (33a) that meshes with the input side sun gear and an output gear part (33b) that meshes with the output side sun gear; a pinion shaft that rotatably supports the pinion gear, a planetary carrier (34) being coaxially rotatable with the input shaft, and a switching mechanism (40) that switches the position of the planetary carrier between a position where it is brought to be connected with a fixing member (41) to finally come to stationary, and at a position where it is connected with the input shaft (1) for being integrally rotated together with the input shaft.

Description

  The present invention relates to a transmission provided with a planetary gear mechanism, and more particularly to a transmission capable of switching a gear ratio between two stages of a high range and a low range.

  In recent years, needs for improving fuel efficiency for automobiles have been further increased, and development of a transmission for realizing efficient driving performance is desired. As one of such vehicles, an automobile equipped with a sub-transmission for compensating for a variable range of the gear ratio of the main transmission is known.

  Japanese Patent Laying-Open No. 2008-87607 (Patent Document 1) discloses a device intended to simplify the structure of a transfer device provided with a planetary gear type gear ratio switching mechanism and to eliminate gear noise at the time of switching.

  1 and 2 schematically show the structure of the auxiliary transmission disclosed in Patent Document 1. FIG. FIG. 1 shows a state during high range traveling, and FIG. 2 shows a state during low range traveling.

  The transmission shown in FIGS. 1 and 2 includes an input shaft 1, an output shaft 2, a planetary gear mechanism 10 that decelerates the rotation of the input shaft 1, and a switching that switches a power transmission path from the input shaft 1 to the output shaft 2. Mechanism 20.

  The planetary gear mechanism 10 includes an input-side sun gear 11 fixedly connected to the input shaft 1, a pinion gear 12 disposed so as to mesh with the input-side sun gear 11, a fixed ring gear 13 having internal teeth that mesh with the pinion gear 12, and a pinion gear 12. And a planetary carrier 14 having a pinion shaft that rotatably supports the input shaft 1 and rotatably provided concentrically with the input shaft 1.

  The switching mechanism 20 includes an input side engaging portion 21 connected and fixed to the input shaft 1, an output side engaging portion 22 connected and fixed to the output shaft 2, and a planetary side engaging portion connected and fixed to the planet carrier 14. And the input side engaging part 21 and the output side engaging part 22 at one position, and the planetary side engaging part 23 and the output at the other position. And a clutch member 24 that connects the side engaging portion 22.

  The clutch member 24 has a sleeve shape and is provided so as to be movable in the axial direction. An input internal tooth portion 24a and an output side engagement portion that can be engaged with the input side engagement portion 21 on the inner diameter side thereof. 22 has an output inner tooth portion 24 b that can be engaged with the planetary gear 22, and has a planetary outer tooth portion 24 c that can be engaged with the planetary side engaging portion 23 on the outer diameter side thereof.

  In the high range traveling state shown in FIG. 1, the rotation of the input shaft 1 is transmitted to the pinion gear 12 via the sun gear 11. The pinion gear 12 meshed with the fixed ring gear 13 rotates around the input shaft 1 while rotating to rotate the planet carrier 14.

  In the state shown in FIG. 1, the clutch member 24 is brought to a position closer to the sun gear 11. At that position, the input internal gear portion 24a of the clutch member 24 is engaged with the input side engaging portion 21 fixed to the input shaft 1, and the output internal gear portion 24b of the clutch member 24 is fixed to the output shaft 2. The side engaging portion 22 is engaged. The planetary side engaging portion 23 of the planetary carrier 14 is not engaged with any member. Due to such a connection relationship, the rotation of the input shaft 1 is transmitted to the output shaft 2 through the clutch member 24 without being decelerated as it is. Since the input shaft 1 and the output shaft 2 have a direct connection structure, the reduction ratio is 1.0.

  In the low range running state shown in FIG. 2, the clutch member 24 is brought to a position closer to the output shaft 2. At that position, the planetary outer teeth portion 24 c of the clutch member 24 engages with the planetary engagement portion 23 of the planet carrier 14, and the output inner teeth portion 24 b of the clutch member 24 is fixed to the output shaft 2. The part 22 is engaged. The input side engaging portion 21 fixed to the input shaft 1 is not engaged with any member. Due to such a connection relationship, the rotation of the input shaft 1 is decelerated by the planetary gear mechanism 10, and this decelerated rotation is transmitted to the output shaft 2 via the clutch member 24.

JP 2008-87607 A

  The transmission as shown in FIGS. 1 and 2 has the following problems.

  First, a sleeve-like clutch member 24 that is displaceable in the axial direction of the input shaft has an input inner tooth portion 24a and an output inner tooth portion 24b on its inner diameter side, and a planetary outer tooth portion on its outer diameter side. 24c, and the tooth portions 24a, 24b, and 24c are offset from each other in the axial direction. Therefore, the length of the clutch member 24 in the axial direction becomes long, and the transmission as a whole has a compact design. Difficult to do.

  Next, in the low range traveling state, the rotation of the input shaft 1 is decelerated via the planetary gear mechanism 10, and this decelerated rotation is transmitted to the output shaft 2 via the clutch member 24. If the number of teeth of the sun gear 11 is Zs and the number of teeth of the fixed ring gear is Zr, the reduction ratio can be expressed by the following equation.

Reduction ratio = (Zs + Zr) / Zs = 1 + (Zr / Zs)
In the above equation, since there is a relationship of Zr> Zs, the reduction ratio is always 2.0 or more. In order to ensure a more efficient running state in the low range, it is desirable to be able to set the reduction ratio more finely.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a transmission capable of making the overall structure more compact.

  Another object of the present invention is to provide a transmission in which the reduction ratio can be set more finely.

  A transmission according to the present invention includes an input shaft, an input-side sun gear coupled to the input shaft, an output shaft, an output-side sun gear coupled to the output shaft, an input gear portion that meshes with the input-side sun gear, and an output side A pinion gear having an output gear portion that meshes with the sun gear, a pinion shaft that rotatably supports the pinion gear, and a planetary carrier that is rotatably provided concentrically with the input shaft, and the planetary carrier is connected to a stationary member to be stationary. And a switching mechanism that switches between a position to be moved and a position that is coupled to the input shaft and rotated together with the input shaft.

  In one embodiment, the switching mechanism includes a fixed side engaging portion that is connected and fixed to the fixing member, a planetary side engaging portion that is connected and fixed to the planet carrier, and an input side engaging portion that is connected and fixed to the input shaft. And movably provided between the first position and the second position along the axial direction of the input shaft, connecting the fixed side engaging portion and the planetary side engaging portion at the first position, A clutch member connecting the input side engaging portion and the planetary side engaging portion at the second position;

  Preferably, the fixing member includes a fixed side ring member concentric with the input shaft and surrounding the input shaft. Said fixed side engaging part is provided in the fixed side ring member. Preferably, the planet carrier includes a cylindrical member that is concentric with the input shaft and extends between the input shaft and the stationary ring member, and a planetary ring member that is fixedly connected to the outer peripheral surface of the cylindrical member. Including. The planetary engagement portion is provided on the planetary ring member. Preferably, the input shaft includes an input side ring member concentrically with the input shaft and fixedly connected to the input shaft. The input side engaging portion is provided on the input side ring member.

  In one embodiment, the stationary ring member, the planetary ring member, and the input ring member have the same outer diameter. Preferably, a first synchronizer ring is provided between the fixed side engaging portion and the planetary side engaging portion, and a second synchronizer ring is provided between the planetary side engaging portion and the input side engaging portion. .

  Preferably, the switching mechanism is centrally arranged on one side of the planetary gear mechanism including the input / output side sun gear and the pinion gear as viewed in the axial direction of the input shaft. In one embodiment, the switching mechanisms are collectively arranged on the input side of the planetary gear mechanism as viewed in the axial direction of the input shaft.

  The technical significance or operational effects of the above characteristic configuration will be described in detail in the following section.

  According to the present invention, the overall structure of the transmission can be made more compact.

It is a figure which shows typically the conventional transmission in a high range driving state. It is a figure which shows typically the conventional transmission in a low range driving state. It is a figure which shows typically the transmission which concerns on one Embodiment of this invention in a low range driving state. It is a figure which shows typically the transmission which concerns on one Embodiment of this invention in a high range driving state.

  3 and 4 are diagrams schematically showing a transmission according to an embodiment of the present invention. FIG. 3 shows a state during low range traveling, and FIG. 4 shows a state during high range traveling.

  The transmission shown in FIGS. 3 and 4 includes an input shaft 1, an output shaft 2, a planetary gear mechanism 30 that decelerates the rotation of the input shaft 1, and a switching that switches a power transmission path from the input shaft 1 to the output shaft 2. Mechanism 40.

  The planetary gear mechanism 30 includes an input-side sun gear 31 that is connected to the input shaft 1 and rotates together with the input shaft, an output-side sun gear 32 that is connected to the output shaft 2 and rotates together with the output shaft, It has a pinion gear 33 having an input gear portion 33 a meshing with the input side sun gear 31 and an output side gear portion 33 b meshing with the output side sun gear 32, and a pinion shaft 34 a that rotatably supports the pinion gear 33, and rotates concentrically with the input shaft 1. And a planetary carrier 34 provided as possible.

  The switching mechanism 40 includes a fixed side engaging portion 43 connected and fixed to the fixing member 41, a planetary side engaging portion 45 connected and fixed to the planet carrier 34, and an input side engaging portion connected and fixed to the input shaft 1. 47 and a clutch member 48 provided to be movable between a first position and a second position along the axial direction of the input shaft 1. The clutch member 48 connects the fixed-side engaging portion 43 and the planetary-side engaging portion 45 at the first position shown in FIG. 3, and the input-side engaging portion 47 at the second position shown in FIG. 4. The planetary engagement portion 45 is connected.

  The fixed member 41 includes a fixed-side ring member 42 that is concentric with the input shaft 1 and surrounds the input shaft. The fixed side engaging portion 43 described above is provided on the fixed side ring member 42.

  The planet carrier 34 includes a pinion shaft 34 a that rotatably supports the pinion gear 33, a cylindrical member 34 b that is concentric with the input shaft 1 and extends between the input shaft 1 and the fixed ring member 42, and the cylinder And a planetary ring member 44 fixedly connected to the outer peripheral surface of the member 34b. The planetary engagement portion 45 described above is provided on the planetary ring member 44.

  The input shaft 1 includes an input side ring member 46 that is concentric with the input shaft and fixedly connected to the input shaft. The input side engaging portion 47 described above is provided on the input side ring member 46.

  The clutch member 48 is always engaged with the planetary side engaging portion 45 and engages with the fixed side engaging portion 43 when brought to the first position shown in FIG. When it is brought to the position 2, it engages with the input side engaging portion 47. In order to simplify the structure of the clutch member 48 and the engaging portions 43, 45, 47, the fixed side ring member 42, the planetary side ring member 44, and the input side ring member 46 preferably have the same outer diameter. Have dimensions.

  As shown in FIG. 3 and FIG. 4, the first synchronizer ring 50 is preferably disposed between the fixed side engaging portion 43 and the planetary side engaging portion 45, and the input side engaging portion 47 and the planetary side engagement are arranged. A second synchronizer ring 51 is arranged between the joint portion 45. The first synchronizer ring 50 synchronizes the rotation of the stationary ring member 42 and the planetary ring member 44 when the clutch member 48 is engaged with both the stationary engagement portion 43 and the planetary engagement portion 45. is there. The second synchronizer ring 51 synchronizes the rotation of the input side ring member 46 and the planetary side ring member 44 when the clutch member 48 is engaged with both the input side engaging portion 47 and the planetary side engaging portion 45. is there.

  In the embodiment shown in FIG. 3 and FIG. 4, the switching mechanism 40 is one side of the planetary gear mechanism 30 composed of the input / output side sun gears 31 and 32 and the pinion gear 33, for example, planetary It is centrally arranged on the input side of the gear mechanism.

  With reference to FIG. 3, the operation of the transmission during low-range traveling will be described. The rotation of the input shaft 1 is transmitted to the pinion gear 33 via the input side sun gear 31. Since the clutch member 48 connects the fixed side engaging portion 43 of the fixed member 41 and the planetary side engaging portion 45 of the planet carrier 34, the planet carrier 34 does not rotate. Therefore, the pinion gear 33 performs only the rotation movement without performing the revolution movement. The rotation of the pinion gear 33 is transmitted to the output shaft 2 via the output sun gear 32. By appropriately selecting the number of gear teeth that mesh with each other, the reduction ratio from the input shaft 1 to the output shaft 2 can be set to a desired value. Naturally, it is also possible to obtain a reduction ratio of 2.0 or less.

  With reference to FIG. 4, the operation of the transmission during high-range travel will be described. The rotation of the input shaft 1 is transmitted to the pinion gear 33 via the input side sun gear 31. Since the clutch member 48 connects the input side engaging portion 47 connected and fixed to the input shaft 1 and the planetary side engaging portion 45 of the planet carrier 43, the planet carrier 34 and the input shaft 1 are integrated. Rotate. The rotation of the planet carrier 34 is transmitted to the output shaft 2 via the pinion gear 33 and the output side sun gear 32.

  According to one embodiment of the present invention described above, the following operational effects are achieved.

  (1) Since the internal gear is eliminated as a structure in which two sun gears 31 and 32 are arranged and one pinion gear 33 is engaged with two sun gears, a more compact transmission can be obtained.

  (2) Since the sleeve-shaped clutch member has engaged portions engaged with the input side engaging portion, the planetary side engaging portion and the fixed side engaging portion only on the inner surface side, the outer surface and the inner surface Compared with the conventional clutch member (FIGS. 1 and 2) having the engaged portions on both sides, the sleeve length can be shortened and the structure can be simplified.

  (3) Since the switching mechanism 40 having the clutch member 48 is centrally arranged on one side of the planetary gear mechanism 30, a shifting operation for moving the clutch member 48 can be performed by a shift lever method. Therefore, it is not necessary to arrange a hydraulic actuator or the like necessary for the hydraulic clutch switching method, and it can be adopted for a manual transmission. In addition, since the input shaft and output shaft are concentric, it can also be used in automatic transmissions.

  (4) By setting the number of teeth of the sun gear and the pinion gear, a value of 2.0 or less can be realized as the reduction ratio during low range traveling.

  (5) Since the switching mechanism includes a synchromesh mechanism including a synchronizer ring, no gear squeal is generated even when shifting is performed during traveling.

  As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to the thing of embodiment shown in figure. Various modifications and variations can be made to the illustrated embodiment within the same range or equivalent range as the present invention.

  The present invention can be advantageously used as a transmission that can maintain good vehicle running performance while improving fuel efficiency.

  DESCRIPTION OF SYMBOLS 1 Input shaft, 2 Output shaft, 10 Planetary gear mechanism, 11 Sun gear, 12 Pinion gear, 13 Ring gear, 14 Planet carrier, 20 Switching mechanism, 21 Input side engaging part, 22 Output side engaging part, 23 Planetary side engaging part 24 clutch member, 24a input internal gear, 24b output internal gear, 24c planetary external gear, 30 planetary gear mechanism, 31 input sun gear, 32 output sun gear, 33 pinion gear, 33a input gear gear, 33b output gear gear 34 planetary carrier, 34a pinion shaft, 34b cylindrical member, 40 switching mechanism, 41 fixing member, 42 fixed side ring member, 43 fixed side engaging part, 44 planetary side ring member, 45 planetary side engaging part, 46 input Side ring member, 47 input side engaging portion, 48 clutch member, 50 first synchronizer ring, 51 second sink Ronizer ring.

Claims (7)

An input shaft;
An input-side sun gear coupled to the input shaft;
An output shaft;
An output side sun gear coupled to the output shaft;
A pinion gear having an input gear portion meshing with the input side sun gear and an output gear portion meshing with the output side sun gear;
A planet carrier that has a pinion shaft that rotatably supports the pinion gear, and is rotatably provided concentrically with the input shaft;
A transmission, comprising: a switching mechanism that switches between a position where the planetary carrier is connected to a stationary member and stationary, and a position where the planetary carrier is connected to the input shaft and rotated together with the input shaft. The switching mechanism is
A fixed-side engaging portion connected and fixed to the fixing member;
A planetary engagement portion connected and fixed to the planet carrier;
An input side engaging portion connected and fixed to the input shaft;
It is provided so as to be movable between a first position and a second position along the axial direction of the input shaft, and the fixed-side engaging portion and the planetary-side engaging portion are connected at the first position. The transmission according to claim 1, further comprising: a clutch member that connects the input side engaging portion and the planetary side engaging portion at the second position. The fixing member includes a fixed-side ring member that is concentric with the input shaft and surrounds the input shaft;
The fixed side engaging portion is provided on the fixed side ring member,
The planetary carrier is concentric with the input shaft and extends through the space between the input shaft and the fixed ring member, and the planetary ring member fixedly connected to the outer peripheral surface of the cylindrical member. Including
The planetary engagement portion is provided on the planetary ring member,
The input shaft includes an input side ring member that is concentric with the input shaft and fixedly connected to the input shaft;
The transmission according to claim 2, wherein the input side engaging portion is provided on the input side ring member.   The transmission according to claim 3, wherein the fixed ring member, the planetary ring member, and the input ring member have the same outer diameter. A first synchronizer ring is provided between the fixed side engaging portion and the planetary side engaging portion,
The transmission according to any one of claims 2 to 4, further comprising a second synchronizer ring between the planetary side engaging portion and the input side engaging portion.   6. The switching mechanism according to claim 1, wherein the switching mechanism is arranged on one side of a planetary gear mechanism including the input / output-side sun gear and the pinion gear as viewed in the axial direction of the input shaft. transmission.   The transmission according to claim 6, wherein the switching mechanism is collectively arranged on the input side of the planetary gear mechanism as viewed in the axial direction of the input shaft.

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