JP6550600B2 - transmission - Google Patents

Description

  The present invention relates to a transmission provided with a dog clutch.

  In Patent Document 1, in order to reduce the shock generated when the dog clutch is engaged, a pinhole capable of discharging oil is formed at the top of the crown surface of the dog, and oil is supplied to the engagement surface of the dog. A technique is disclosed for relieving shock during engagement.

JP, 2013-92211, A

However, since it is necessary to forcibly supply oil by the oil pump, there is a problem in that energy efficiency is deteriorated due to an increase in the oil pump load.
The objective of this invention is providing the transmission which can relieve the engagement shock of a dog clutch, without causing the fall of energy efficiency.

In order to achieve the above object, according to a transmission of the present invention, a first gear relatively rotatably supported on a first shaft;
A second gear fixedly supported by a second shaft and constantly meshed with the first gear to achieve a predetermined gear ratio;
A disc-shaped clutch ring having a clutch ring dog that meshes with the dog of the first gear by movement toward the axial meshing side;
An actuator for controlling a power transmission state in which the clutch ring dog is axially moved to mesh with the dog and a power non-transmission state in which the clutch ring dog and the dog are released;
A cylindrical member provided on the clutch ring and surrounding an outer periphery of the clutch ring dog;
An intake port formed on the first shaft and taken up by rotation of the first gear and the second gear into an axial oil passage formed in the first shaft, and an intake port taken from the intake port A supply port for supplying the extracted oil from the axial center oil passage toward the inner periphery of the cylindrical member;
Equipped with.

  Therefore, since oil can be supplied to the dog without providing an oil pump or the like, a reduction in energy efficiency can be avoided. Further, oil can be stored in the vicinity of the clutch ring dog by the cylindrical member, and since the oil functions as a shock absorbing material when the dogs engage with each other, meshing shock can be suppressed.

FIG. 1 is a schematic system diagram showing an automatic transmission according to a first embodiment. FIG. 2 is a view showing a configuration of a dog clutch of the first embodiment. FIG. 2 is a partial cross-sectional view showing a configuration of a dog clutch of Example 1; FIG. 7 is a top view of a spline portion of the first shaft of the first embodiment. It is the schematic showing the flow of oil when the dog clutch mechanism of Example 1 transfers to a fastening state from a releasing state. FIG. 7 is a schematic view showing a clutch ring dog of Example 2; FIG. 14 is a schematic view showing a clutch ring dog of Example 3; FIG. 18 is a cross-sectional view illustrating a first shaft of Example 4;

Example 1
FIG. 1 is a schematic system diagram showing an automatic transmission according to a first embodiment. A clutch 2 is connected to the engine output shaft of the engine 1. The clutch 2 is a dry clutch, and the position of the clutch plate is controlled by the clutch actuator 2a. The clutch actuator 2a controls the position of the clutch piston that presses the clutch plate according to the requested torque transfer capacity, and performs slip control for transmitting torque while allowing relative rotation of the clutch 2, and relative rotation of the clutch 2 Do not allow full engagement control. The clutch actuator 2a has a piston stroke sensor 11 that detects the stroke position of the clutch piston, and controls the torque transmission capacity based on the detected stroke position.

  The output side of the clutch 2 is connected to an automatic transmission 3 that shifts the input rotation and outputs the same to the drive wheels 4. The automatic transmission 3 has a first shaft 3a connected to the automatic transmission side of the clutch 2 and a second shaft 3b arranged in parallel with the first shaft 3a. A first speed drive gear 31 and a second speed drive gear 32 supported rotatably relative to the first shaft 3 a are provided on the first shaft 3 a. A first speed driven gear 33 fixed to the second shaft 3b and integrally rotating with the second shaft 3b and a second speed driven gear 34 are provided on the second shaft 3b. Each driven gear always meshes with each drive gear. Although not shown, when configuring an automatic transmission with four forward gears, it is better if three-speed drive gear, three-speed driven gear, four-speed drive gear and four-speed driven gear are mounted as well as the first and second gears. , I do not mention in particular.

  A first dog 31 a extending in the axial direction is provided on a side surface of the first-speed drive gear 31. A side surface of the second drive gear 32 has a second dog 32a extending in the axial direction. The first speed drive gear 31 and the second speed drive gear 32 have first and second dog clutch mechanisms. The first dog clutch mechanism includes a first clutch ring 311 that is fixedly installed on the first shaft 3 a so as to be movable in the axial direction and meshes with the first shift fork 310 so as to be relatively rotatable. Similarly, the second dog clutch mechanism also has a second clutch ring 321.

  The first clutch ring 311 is a disc-like member that can be applied to the first shift fork 310 while being held rotatably relative to the first shift fork 310. The first clutch ring 311 is spline-fitted with a spline 3as formed on the outer periphery of the first shaft 3a, and allows relative movement in the axial direction while restricting relative movement in the rotational direction. The first clutch ring 311 has a first clutch ring dog 311 a axially extended on the side facing the first speed drive gear 31. Similarly, the second clutch ring 321 is a disk-shaped member that can be applied to the second shift fork 320 and an axial force while being held rotatably relative to the second shift fork 320. The second clutch ring 321 is spline-fitted with the first shaft 3a, restricts relative movement in the rotational direction, and allows relative movement in the axial direction. The second clutch ring 321 has a second clutch ring dog 321 a axially extended on the side facing the second speed drive gear 32.

  In the first gear, the first shift fork 310 is moved to the right in FIG. 1, the first clutch ring 311 is moved to the right, and the first clutch ring dog 311a and the first dog 31a of the first drive gear 31 are moved. Engage and achieve 1st speed. At the time of upshift from first gear to second gear, the first shift fork 310 is moved to the left side in FIG. 1 to release the meshing between the first clutch ring dog 311a and the first dog 31a, and the second shift By moving the fork 320 to the right side in FIG. 1, the second clutch ring dog 321a and the second dog 32a are engaged with each other to achieve the second speed.

  The shift actuator 5 is configured to be able to move the first shift fork 310 and the second shift fork 320 in the axial direction. The shift actuator 5 has a shift drum 50 having shift grooves 51, 52 engaged with the shift forks 310, 320 on the outer periphery. The shift grooves 51 and 52 are formed so that the axial positions of the shift forks 310 and 320 can be moved with the rotation of the shift drum 50, and the shift motor 53 controls the rotational position of the shift drum 50 to shift. Do.

  The transmission controller 30 detects an engine rotational speed sensor 10 detecting an engine rotational speed, a first rotational angle sensor 12 detecting a rotational angle of the first shaft 3a, and a shift detecting a stroke position of each shift fork 310, 320 A stroke sensor 13, a current sensor 14 for detecting the current value of the shift motor 53, a second rotation angle sensor 15 for detecting the rotation angle of the second shaft 3b, and a shift for selecting the P, R, N, D ranges A desired gear position is determined based on the shift signal of the lever 7, and the drive current Is is output to the shift motor 53 of the shift actuator 5.

  FIG. 2 is a view showing the configuration of the dog clutch of the first embodiment. In addition, since the first dog clutch mechanism and the second dog clutch mechanism have the same configuration, only the first dog clutch mechanism will be described. 2 (a) is a view of the first clutch ring 311 viewed from the first drive gear 31 side, FIG. 2 (b) is a side view of the first clutch ring 311 viewed from the radial direction, and FIG. FIG. 2D is a side view of the first drive gear 31 viewed from the first clutch ring 311 side, and FIG. 2D is a side view of the first drive gear 31 viewed from the radial direction. 3 is a partial cross-sectional view showing the configuration of the dog clutch of the first embodiment, and FIG. 4 is a top view of the spline portion of the first shaft of the first embodiment.

  The first clutch ring 311 has an oil catch ring 311 b which is a cylindrical member surrounding the outer periphery of the dog 311 a. The axial length of the oil catch ring 311b, in other words, the height of the wall is substantially the same as the axial length of the dog 311a. The height may not be the same height as the dog 311a, or may be slightly lower, or may be higher than the dog 311a in a range not interfering with the side surface of the first drive gear 31, and is not particularly limited.

  When the first clutch ring 311 moves toward the first drive gear 31 in the axial direction, the outer periphery of the dog 31a of the first drive gear 31 enters the inner periphery of the oil catch ring 311b with a slight gap. The first shaft 3a includes an axial oil passage 3a1 for supplying oil, an oil intake port 3a2 for taking in the oil scraped by each gear in the axial oil passage 3a1, and an oil catch ring 311b for required lubricating oil. And a supply port 3a3 for supplying the Since the oil scraped up with the rotation of the gear by the oil intake port 3a2 is taken into the shaft center oil passage 3a1, there is no need to separately provide an oil pump or the like, and fuel consumption can be improved.

  As shown in FIG. 4, the supply port 3a3 has a long hole shape that opens between the splines 3as. Thus, the supply port 3a3 is not blocked even if the first clutch ring 311 moves in the axial direction when shifting from the dog clutch released state of FIG. 3A to the dog clutch engaged state of FIG. 3B. , Can supply oil. Further, since the supply port 3a is formed at a position radially opposed to the inner peripheral side end face 311a1 of the dog 311b, the supplied oil can always stay near the dog 311b.

  Next, the operation will be described. FIG. 5 is a schematic view showing the flow of oil when the dog clutch mechanism of the first embodiment shifts from the released state to the engaged state. In the released state, when oil is discharged from the supply port 3a3 by centrifugal force, the oil supplied toward the dog 311a is received by the oil catch ring 311b, and the oil catch ring 311b is interposed between the dog 311a and the dog 311a. Oil stagnates along the inner circumference of the In this state, the first clutch ring 311 starts to move in the axial direction, and when viewed in the radial direction, the dog 311a and the dog 31a are at the overlapping position, and when the relative position of both dogs approaches, the proximity of both dogs Oil is sandwiched between the side surfaces 311a2 and 31a2 of both dogs. As a result, the oil functions as a shock absorbing material when the two dogs engage with each other, so that the meshing shock can be suppressed. Further, the supply port 3a is formed at a position facing the dog 311a in the radial direction. Therefore, since the oil always stays near the dog 311a, the oil can be surely present when the side surfaces 311a2 and 31a2 of both dogs approach each other.

As described above, in the first embodiment, the following advantages can be obtained.
(1) A first speed drive gear 31 (first gear) rotatably supported on the first shaft 3a so as to be relatively rotatable;
A first-speed driven gear 33 (second gear) which is fixed to the second shaft 3 b and constantly meshes with the first-speed drive gear 31 to provide a first speed (predetermined gear ratio),
A disc-shaped first clutch ring 311 (clutch ring) having a first clutch ring dog 311a (clutch ring dog) meshing with the first dog 31a (first gear dog) by movement to the axial meshing side ,
A shift actuator that controls a power transmission state in which the first clutch ring dog 311a is axially moved to mesh with the first dog 31a, and a power non-transmission state in which the first clutch ring dog 311a and the first dog 31a are released. 5 (actuator), an oil catch ring 311b (cylindrical member) provided on the first clutch ring 311 and surrounding the outer periphery of the first clutch ring dog 311a, and the first shaft 3a, the first drive gear 31 and the first An intake port 3a2 for taking in the oil scraped up by the rotation of two gears into an axial oil passage 3a1 formed in the first shaft 3a, and an oil taken in from the intake port 3a2 from the axial oil passage 3a1 And a supply port 3a3 for supplying toward the inner periphery of the catch ring 311b.
Therefore, oil can be supplied to the dog without providing an oil pump or the like. Further, oil can be stored in the vicinity of the first clutch ring dog 311a by the oil catch ring 311b, and when the dogs engage with each other, the oil functions as a shock absorbing material, so that meshing shock can be suppressed.

  (2) The supply port 3a3 is formed at a position facing the first clutch ring dog 311a in the radial direction. Therefore, the oil can be retained near the first clutch ring dog 311a, and the oil can be reliably present when the side surfaces 311a2 and 31a2 of both dogs approach each other.

  (3) The supply port 3a3 is a long hole that can supply oil to the inner periphery of the oil catch ring 311b even if the first clutch ring 311 moves in the axial direction. Therefore, oil can be present in the vicinity of the first clutch ring dog 311 a regardless of the axial position of the first clutch ring 311.

Example 2
Next, Example 2 will be described. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 6 is a schematic diagram illustrating the clutch ring dog of the second embodiment. 6 (a) is a partial cross-sectional view of the first clutch ring 311, and FIG. 6 (b) is a partial perspective view of the first clutch ring 311. As shown in FIG. The inner peripheral end surface 311a3 of the first clutch ring dog 311a is formed as an inclined surface that is inclined toward the axially releasing side. In other words, the radial position of the inner circumferential end surface 311 a 3 is formed such that the radial position on the axial direction release side is closer to the outer diameter side than the radial position on the axial direction fastening side. That is, when the oil supplied from the supply port 3a3 flows to the fastening side of the first clutch ring dog 311a, it becomes difficult to retain the oil on the inner periphery of the oil catch ring 311b. Therefore, the oil can be positively retained in the oil catch ring 311 b by setting the inner end surface 311 a 3 as the inclined surface and guiding the oil toward the disc-like member side of the first clutch ring 311.

As described above, in the second embodiment, the following effects can be obtained.
(4) As for the radial position of the inner circumferential side end surface 311a3 of the first clutch ring dog 311a, the radial position on the axial direction release side of the radial direction position on the axial direction fastening side is on the outer diameter side.
Therefore, the oil supplied from the supply port 3a3 can be positively flowed toward the oil catch ring 311b. Although the inclined surface is formed in the second embodiment, the present invention is not limited to the inclined surface and may have a stepped shape.

[Example 3]
Next, Example 3 will be described. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 7 is a schematic diagram illustrating the clutch ring dog of the third embodiment. FIG. 7A is a partial cross-sectional view of the first clutch ring 311, and FIG. 7B is a partial perspective view of the first clutch ring 311. A guide protrusion 311a4 is formed on the inner circumferential end surface 311a1 of the first clutch ring dog 311a so that the thickness in the rotational direction decreases toward the axial center. That is, when the oil supplied from the supply port 3a3 flows to the fastening side of the first clutch ring dog 311a, it becomes difficult to retain the oil on the inner periphery of the oil catch ring 311b. Therefore, by forming the guide projections 311a4 on the inner peripheral side end surface 311a1 and guiding the oil to flow positively to the left and right, the oil can be positively retained on the inner periphery of the oil catch ring 311b.

As described above, in the third embodiment, the following effects can be obtained.
(5) At the inner circumferential end surface 311a1 of the first clutch ring dog 311a, a guide protrusion 311a4 is formed whose thickness in the rotational direction decreases toward the axial center.
Therefore, the oil supplied from the supply port 3a3 can be positively flowed toward the oil catch ring 311b. In addition to the configuration of the third embodiment, the configuration described in the second embodiment may be further combined to form an inclined surface or a stepped shape, so that oil may flow more positively to the oil catch ring 311b. .

(Example 4)
Next, Example 4 will be described. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 8 is a cross-sectional view illustrating a first shaft of the fourth embodiment. In the first embodiment, the supply port 3a3 is in the form of a long hole, and the long hole is connected to the axial center oil passage 3a1. On the other hand, the fourth embodiment differs in that the supply port is constituted by a small diameter radial oil passage 3a30 connected to the axial center oil passage 3a1 and an opening 3a31 having a long hole shape. Thus, in addition to the effects of the first embodiment, the discharge amount of oil can be controlled, and the target oil supply amount can be secured.

(Other examples)
As described above, the description is based on the first embodiment. However, the present invention is not limited to the above-described embodiment, and the present invention may be applied to a transmission having another configuration. For example, in the first embodiment, a drive gear as a relative rotating body is disposed on the first shaft 3a, and a dog clutch mechanism capable of selectively fixing these drive gears to the first shaft 3a is provided. The first shaft 3a is not limited to be provided on the second shaft 3b, or may be set to both the first shaft 3a and the second shaft 3b in combination.
Further, the present invention can be applied not only to the fourth forward speed, but also to the second forward speed and a multistage automatic transmission.
Further, in the embodiment, an example is described in which an engine that is an internal combustion engine is mounted as a power source, but the present invention can be applied to a hybrid vehicle that uses a drive motor or an engine and a motor together as a power source.

The oil intake port 3a2 may be provided not only in the middle of the first shaft 3a but also on the axial end face of the first shaft 3a. That is, the axial center oil passage 3a1 is opened at the axial end face of the first shaft 3a, and this opening functions as the oil intake port 3a2. In this case, the oil scraped up by the rotation of the gear is collected in an oil reservoir (not shown), and this oil reservoir is led to the opening of the axial end face of the first shaft 3a via a guide oil passage (not shown).
Moreover, although the automatic transmission was demonstrated to the example in each Example, even if it is a manual transmission, it is applicable similarly.

1 Engine 2 Clutch 3 Automatic transmission (transmission)
3a 1st shaft 3a1 axial center oil passage 3a2 oil intake port 3a3 supply port 3b 2nd shaft 5 shift actuator 30 transmission controller 31 first speed drive gear 31a first dog 33 first speed driven gear 310 first shift fork 311 first clutch ring 311a First clutch ring dog 311b Oil catch ring (cylindrical member)

Claims (5)

A first gear supported in a relatively rotatable manner on the first shaft;
A second gear fixedly supported by a second shaft and constantly meshed with the first gear to achieve a predetermined gear ratio;
A disc-shaped clutch ring having a clutch ring dog that meshes with the dog of the first gear by movement toward the axial meshing side;
An actuator for controlling a power transmission state in which the clutch ring dog is axially moved to mesh with the dog and a power non-transmission state in which the clutch ring dog and the dog are released;
A cylindrical member provided on the clutch ring and surrounding an outer periphery of the clutch ring dog;
An intake port formed on the first shaft and taken up by rotation of the first gear and the second gear into an axial oil passage formed in the first shaft, and an intake port taken from the intake port A supply port for supplying the extracted oil from the axial center oil passage toward the inner periphery of the cylindrical member;
A transmission characterized in that. In the transmission according to claim 1,
The transmission according to claim 1, wherein the supply port is formed at a position radially opposite the clutch ring dog. The transmission according to claim 1 or 2,
The transmission is characterized in that the supply port is a long hole that can supply oil to the inner periphery of the cylindrical member even if the clutch ring moves in the axial direction. The transmission according to any one of claims 1 to 3,
The transmission according to claim 1, wherein the radial position of the end face on the inner peripheral side of the clutch ring dog is such that the radial position on the release side in the axial direction is on the outer diameter side than the radial position on the fastening side in the axial direction. The transmission according to any one of claims 1 to 4,
The transmission is characterized in that the inner peripheral side end face of the clutch ring dog is formed with a protrusion whose thickness in the rotational direction becomes smaller toward the axial center side.

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