JP4339526B2 - Damper ring mounting structure - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a mounting structure for a damper ring, and in particular, when a sub-transmission with a planetary gear mechanism is provided to enable high-low switching in a four-wheel drive vehicle, and the ring gear is supported in a floating manner. The present invention relates to a mounting structure for a damper ring used for the operation.
[0002]
[Prior art]
In a transfer (power distribution device) of a four-wheel drive vehicle, it is known to provide a sub-transmission comprising a planetary gear mechanism to enable high-low switching (see Japanese Patent No. 3003330). ). In this case, due to the structure of the planetary gear mechanism, if the shaft positions are fixed for all the gears, the load sharing is not evenly performed. Therefore, it is necessary to make the shaft position free for any gear.
[0003]
[Problems to be solved by the invention]
Here, when considering a floating structure in which the largest-diameter ring gear is free, the ring gear is loosely fitted to the casing to allow eccentric movement, that is, play in the radial direction. Then, when the ring gear moves eccentrically, it directly collides with the casing, causing vibration noise. Therefore, a damper ring is inserted into the gap between the fitting portions to buffer or prevent mutual collision.
[0004]
Conventionally, the damper ring has been a relatively large diameter O-ring. When assembling the ring gear to the casing, first, the O-ring is fitted into the fitting hole on the casing side, and the O-ring is placed along the radially outer fitting surface by the elastic restoring force of the O-ring itself. After the oil was applied, the ring gear was carefully pressed into the O-ring.
[0005]
However, a large-diameter O-ring has a large variation in diameter and length, and the rigidity of the ring itself is low, so it is difficult to maintain its own shape. For this reason, the followability to the fitting surface of the O-ring is poor, and when the ring gear is press-fitted, the O-ring is folded or bitten inward in the radial direction, and the worst O-ring is broken. .
[0006]
For this reason, it is conceivable to embed a core material inside the ring to prevent variation in diameter and length and to increase ring rigidity.
[0007]
However, on the other hand, the phase position of the damper ring may be determined in advance, and in this case, if the damper ring is allowed to rotate freely, the damper ring performance may not be sufficiently exhibited.
[0008]
Accordingly, the present invention has been made in view of the above problems, and an object thereof is to provide a mounting structure for a damper ring that can accurately position the damper ring at a predetermined phase position.
[0009]
[Means for Solving the Problems]
The present invention has a structure in which a damper ring is inserted into a gap between an inner diameter side member and an outer diameter side member that are fitted to each other so that a direct collision between these members is buffered. But Ring body made of elastic material And embedded in the ring body Core material made of metal or plastic And consists of The ring body is pressed against the fitting surface of the outer diameter side member by the core material And install the above damper ring And providing a deficient portion at a predetermined location on the fitting surface of the outer diameter side member for the necessity of working space, etc., and projecting a stopper portion engaging with the inner wall of the deficient portion on the damper ring, The rotation of the damper ring is restricted by engagement.
[0010]
Here, it is preferable that the ring main body is removed from the damper ring and the core material is exposed in an opposite region in which the defect portion is axisymmetric.
[0011]
Further, in the damper ring existing in the defect portion, a pair of the stopper portions are provided to engage with both inner walls of the defect portion, and the ring body is removed between the stopper portions to expose the core material. Are preferably present.
[0012]
Moreover, it is preferable that the said core material is divided | segmented in the said exposed part, and is mutually connected.
[0013]
Further, the ring main body is divided and the divided ring bodies are arranged at a predetermined interval in the ring longitudinal direction at a place other than the defect portion and the opposite region, and the divided ring bodies are arranged in the core material. It is preferable that the core material is exposed through a gap between the split ring bodies.
[0014]
Moreover, it is preferable that the said core material consists of a coil spring, one spring steel, or a metal or a plastic wire.
[0015]
On the other hand, the present invention has a structure in which a damper ring is inserted into a gap between an inner diameter side member and an outer diameter side member that are fitted to each other so that a direct collision between these members is buffered. But Ring body made of elastic material And embedded in the ring body Core material made of metal or plastic And consists of The ring body is pressed against the fitting surface of the outer diameter side member by the core material And install the above damper ring In addition, a working part or the like is provided at a predetermined position on the fitting surface of the outer diameter side member so that a missing part is provided, and the ring main body is removed from the damper ring in an opposite region that is axially symmetric with the missing part. Is.
[0016]
DETAILED DESCRIPTION OF THE INVENTION
Preferred embodiments of the present invention will be described below in detail with reference to the accompanying drawings.
[0017]
First, a four-wheel drive vehicle and a transfer to which a damper ring according to the present invention is applied will be described. As shown in FIG. 19, in a four-wheel drive vehicle, after the power of the engine E is transmitted rearward to the transmission T / M and the transfer T / F and distributed to the front and rear sides by the transfer T / F. The four wheels are driven by being transmitted to the front wheel FW and the rear wheel RW. As will become apparent later, the driving of the front wheels FW is selective, and a so-called FR-based part-time 4WD configuration is adopted. The transmission T / M has a manual type including a friction clutch or an automatic transmission type including a fluid converter.
[0018]
FIG. 14 shows the transfer. The transfer T / F inputs the power of the transmission T / M from the input shaft 1, outputs the power from the rear output shaft 2 to the rear wheel side, and selectively outputs the power from the front output shaft 3 to the front wheel side. . The rear output shaft 2 and the front output shaft 3 are connected by a distribution device 4 comprising a chain / sprocket mechanism so that power is distributed and transmitted to each shaft. Power distribution to the front output shaft 3 is selectively performed by the selection device 5. This is the same configuration as the transmission mechanism in a normal manual transmission.
[0019]
A sub-transmission 6 comprising a planetary gear mechanism is provided to perform Hi-Lo two-stage switching of the entire transfer. The auxiliary transmission 6 has a reduction ratio of 1, that is, a direct connection when Hi, and a reduction ratio greater than 1 (for example, 2.5) when Lo, and reduces the rotation of the input shaft 1 and transmits it to the output side. The sub-transmission 6 also has a neutral (N) position. The entire input shaft 1 to auxiliary transmission 6 are accommodated in a common transfer casing 7.
[0020]
In the vicinity of the front end of the transfer T / F, the input shaft 1 and the rear output shaft 2 are coaxially fitted and connected so that they can rotate relative to each other. A needle bearing 8 is provided at the connecting portion. The input shaft 1 is hollow, and its front end protrudes from the casing 7, and a spline 9 is formed on the inner periphery thereof, so that a transmission output shaft (not shown) can be fitted into the spline. . The input shaft 1 is also supported from the outer peripheral side by a front bearing 11 formed of a ball bearing via a needle bearing 10 and a carrier bearing portion 30a. Thus, the input shaft 1 is supported from the inner and outer peripheral sides by the needle bearing 8 and the front bearing 11. A gap between the input shaft 1 and the casing 7 is sealed with an oil seal 12.
[0021]
The rear output shaft 2 extends substantially over the entire length of the transfer, and the rear end side is pivotally supported by a rear bearing 13 composed of a ball bearing. The rear end portion protrudes from the casing 7 (not shown), and the rear wheel drive shaft (propeller shaft) S / R can be connected as shown in FIG.
[0022]
The distribution device 4 is provided at a substantially middle position of the rear output shaft 2, and is attached to the front output shaft 3 and a drive sprocket (drive member) 14 that is attached to the outer peripheral side of the rear output shaft 2 so as to be relatively rotatable. It comprises a drive sprocket (driven member) 15 and a chain 16 that connects these sprockets. The front output shaft 3 is supported by a ball bearing 17 on the front side and a needle bearing 18 on the rear end, and the front end protrudes from the casing 7. A flange 19 is fastened to the protrusion by a nut 21 so that the front wheel drive shaft S / F can be connected using a bolt 20 as shown in FIG. A gap between the protruding portion and the casing 7 is sealed with an oil seal 22.
[0023]
Here, as shown in FIG. 17, the transfer T / F is inclined not diagonally but vertically. A front output shaft 3 is disposed obliquely below the input shaft 1 and the rear output shaft 2, and these shaft positions are offset in the left-right direction. As a result, as shown in FIG. 19, interference between the engine E and the transmission T / M and the front wheel drive shaft S / F is prevented.
[0024]
The selection device 5 is provided adjacent to the front of the drive sprocket 14. The selection device 5 includes a dog gear 23 provided on the drive sprocket 14, a clutch hub 24 fixed to the rear output shaft 2, and a selection sleeve 25 that is spline-fitted to the outer periphery of the clutch hub 24 so as to be axially slidable. And a synchronizer ring 26 provided between the dog gear 23 and the clutch hub 24. The two-wheel drive (neutral) state is illustrated, and when the selection sleeve 25 is slid rearward from this state, the selection sleeve 25 meshes with the dog gear 23 after synchronization by the synchronizer ring 26. As a result, the clutch hub 24 and the dog gear 23, and consequently, the rear output shaft 2 and the drive sprocket 14 are connected, and the rotational power of the rear output shaft 2 is distributed and transmitted to the front output shaft 3 to be in a four-wheel drive state.
[0025]
The auxiliary transmission 6 is provided in front of the selection device 5 and in the vicinity of the connection portion between the input shaft 1 and the rear output shaft 2. The sub-transmission 6 is a planetary gear type, and includes a sun gear 27 integrally provided on the input shaft 1, a plurality of planetary gears 28 meshed with the outer peripheral portion of the sun gear 27, and the planetary gears 28 connected to each other via a shaft 29. It comprises a carrier 30 to be supported and a ring gear 31 having an inner peripheral gear meshed with each planetary gear 28. The carrier 30 is provided with a bridge 32 at a circumferential position where there is no planetary gear 28, and wraps around the sun gear 27 and the planetary gear 28 to support the shaft 29 at both ends. The carrier bearing portion 30 a described above is a part of the carrier 30 and protrudes forward from the carrier 30 and is pivotally supported between the needle bearing 10 and the front bearing 11. A thrust needle bearing 33 is provided to reduce the thrust load between the sun gear 27 and the carrier 30. The ring gear 31 is spline fitted and fixed to the casing 7 as will be described in detail later.
[0026]
A hollow portion is provided inside the sun gear 27 and the carrier 30 in the radial direction, and a switching sleeve 34 is provided slidably on the rear output shaft 2 there. A spline 35 is provided on the rear output shaft 2, and a sleeve 34 is spline-fitted to the spline 35 to allow the sleeve 34 to slide in the axial direction, thereby preventing rotation on the rear output shaft 2.
[0027]
Splines 36, 37, and 38 are provided on the inner periphery of the sun gear 27 and the carrier 30 and on the outer periphery of the switching sleeve 34. The switching sleeve 34 is slid, and the spline 38 is selectively meshed with either the sun gear or the carrier splines 36, 37, thereby switching Hi-Lo. A neutral (N) position for disengaging (free) the spline 38 of the switching sleeve 34 is provided between the sun gear and the carrier splines 36, 37. This auxiliary transmission or switching mechanism is not provided with a synchro.
[0028]
As shown in the figure, when the switching sleeve 34 is engaged with the sun gear 27, the input shaft 1 and the rear output shaft 2 are directly connected, and the rotational power of the input shaft 1 is transmitted to the rear output shaft 2 as it is. This is Hi position. At this time, the planetary gear 28 rotates following the sun gear 27.
[0029]
On the other hand, when the switching sleeve 34 is slid rearward from the illustrated state and meshed with the carrier 30 beyond the N position, the rotational power of the input shaft 1 is changed from the sun gear 27 → the planetary gear 28 → the carrier 30 → the switching sleeve 34 → the rear output shaft. 2, the rear output shaft 2 is decelerated and rotated with respect to the input shaft 1. This is Lo's position.
[0030]
In this transfer, the two-wheel drive / four-wheel drive switching by the selection device 5 and the Hi-N-Lo switching by the auxiliary transmission 6 are automatically performed by a common actuator 39. The actuator 39 has a phase-controlled motor 40 and two cam grooves 41 and 42 that are rotated stepwise to a plurality of phase positions by the motor 40 and for switching between the selection device 5 and the auxiliary transmission 6. A cylindrical cam 43 is engaged with the cam groove 41 and the selection sleeve 25 to move the selection sleeve 25 according to the rotation of the cam groove 41, and is engaged with the cam groove 42 and the switching sleeve 34 to be connected to the cam groove. A switching arm 45 that moves the switching sleeve 34 according to the rotation of 42 and two shafts (only one shaft 46 is shown) that support the arms 44 and 45 so as to be movable in the axial direction are provided. Each arm 44, 45 is provided with a shock absorber 48 using a spring (only one spring 47 is shown) so as not to apply an overload when the splines are engaged. A check mechanism 48a is provided for positioning with respect to each shaft.
[0031]
Lubricating oil is stored in the casing 7, but since this transfer is inclined as shown in FIG. 17, the oil is stored on the lower front output shaft 3 side, and is difficult to reach the upper part. Therefore, the oil pump 49 forcibly lubricates the upper parts.
[0032]
The oil pump 49 is provided adjacent to the rear portion of the distributor 4 and is a trochoid pump driven by the rear output shaft 2. The oil pump 49 sucks oil stored in the inner bottom portion of the casing through the suction pipe 50 and discharges it to an oil hole 51 formed in the center portion of the rear output shaft 2 as indicated by an arrow. The oil in the oil hole 51 is supplied to the support portion of the drive sprocket 14, the selection device 5, and the auxiliary transmission 6 through each oil supply hole 52. The front end of the oil hole 51 is opened, and oil supply to the needle bearing 8 is performed from here. A cap 53 is attached to the input shaft 1 in the vicinity of the front end of the rear output shaft 2 to prevent oil from leaking to the outside.
[0033]
A meter gear 54 is attached to the rear output shaft 2 adjacent to the rear side of the rear bearing 13, and the rotation of the meter gear 54 is detected by a rotation sensor (not shown) via the worm gear 55 to detect the vehicle speed.
[0034]
As shown in FIG. 18, the auxiliary transmission 6 employs a so-called floating structure in which a radial gap h is provided between the ring gear 31 and the casing 7 so that the ring gear 31 can move slightly eccentrically. Yes. A damper ring is provided to buffer a direct collision between the ring gear 31 and the casing 7. Hereinafter, the mounting portion of the ring gear 31 will be described in detail.
[0035]
As shown in FIG. 14, the ring gear 31 is inserted into the ring gear fitting hole 56 provided in the casing 7 from the rear, and the shaft position is fixed by the snap ring 57. A damper ring 58 is inserted in advance in the foremost end of the ring gear fitting hole 56, and then the ring gear 31 is inserted and the foremost end of the ring gear 31 is press-fitted into the damper ring 58. The damper ring 58 is fitted into the ring gear 31 and the ring gear. It is inserted between the joint holes 56.
[0036]
As shown in FIG. 15, in the ring gear fitting hole 56, a damper ring 58 is provided at a corner portion on the front back side by a fitting surface 59 (large-diameter side fitting surface) which is the inner peripheral surface and the front end stopper surface 60. Is formed, and a damper ring 58 is mounted thereon. On the fitting surface 59, teeth 62 a of the spline 62 are formed to protrude rearward from the front end stopper surface 60 by a predetermined distance. This engages with the spline of the ring gear 31 to restrict the rotation of the ring gear 31.
[0037]
As shown in FIG. 16, the ring gear 31 is inserted until the front end surface thereof contacts the front end stopper surface 60. At the same time, the spline 63 of the ring gear 31 meshes with the spline 62 on the casing 7 side. The spline 63 of the ring gear 31 is formed longer than the spline 62 on the casing 7 side, protrudes forward from the spline 62 in the attached state of the ring gear 31, and lightly contacts the damper ring 58. The press-fit portion 64 to the damper ring 58 at the foremost end of the ring gear is a flat circumferential surface without the spline 63 as a matter of course. The press-fit portion 64 has a smaller diameter than the fitting surface 59 and a radial gap h for inserting the damper ring 58 between the fitting surface 59. ₁ Form.
[0038]
When the ring gear 31 is inserted, the press-fit portion 64 is press-fitted into the damper ring 58, and the gap h between the fitting surface 59 and the press-fit portion 64 is inserted. ₁ The damper ring 58 is inserted in a slightly collapsed state. At this time, the ring gear 31 is centered coaxially with the input shaft 1 and the like, and at the same time, a uniform radial clearance h is secured between the splines 62 and 63. The clearance h achieves the floating support of the ring gear 31, and the ring gear 31 can move eccentrically by the clearance h during power transmission.
[0039]
Here, it is necessary to keep the damper ring 58 along the fitting surface 59 until the completion of the ring gear installation so that the damper ring 58 is not folded or bitten inward when the ring gear is installed. And in order to ensure such ring rigidity, the damper ring 58 of this embodiment has the following structure.
[0040]
As shown in FIGS. 1 to 3, the damper ring 58 includes an elastic body, in this embodiment, a ring main body 65 made of rubber, and a core member 66 made of metal or plastic and embedded in the center of the ring main body 65. The ring body 65 is pressed against the fitting surface 59 by the core material 66. The ring body 65 and the core member 66 are flexible bodies and can be bent relatively freely. The ring body 65 is divided into a ring longitudinal direction or a circumferential direction, and includes a plurality of divided ring bodies 67. The split ring bodies 67 are arranged at a predetermined interval in the ring longitudinal direction, the split ring bodies 67 are connected to each other by the core material 66, and the core material 66 is exposed from the gap between the split ring bodies 67. .
[0041]
In this embodiment, the core member 66 is a coil spring formed of spring steel. However, it may consist of a single spring steel, metal or plastic wire.
[0042]
As described above, the damper ring is configured by embedding the core material in the ring body, so that variations in the diameter and length of the damper ring are prevented and the rigidity is increased and the shape retention force is improved. Accordingly, the followability of the damper ring to the large-diameter side fitting surface is improved, and specifically, the damper ring 58 is surely pressed against and fitted along the fitting surface 59 until the ring gear is completely attached. Therefore, it is possible to prevent the damper ring from being folded inward (see the phantom line in FIG. 1) or being bitten or broken when the ring gear is attached.
[0043]
Even with this configuration, the damper ring 58 itself can be bent, so that the damper ring 58 can be bent appropriately and inserted into the ring gear fitting hole 56 while avoiding the teeth of the spline 62.
[0044]
Moreover, since the ring main body 65 is divided | segmented, the whole ring becomes easy to bend and the followable | trackability with respect to a casing fitting surface improves. More specifically, since the core member 66 exposed from the gap between the split ring bodies 67 is easier to bend than a portion where the split ring body 67 is located, a circular shape can be easily obtained.
[0045]
In the present embodiment, the split ring body 67 is formed in a sausage shape having a predetermined length, and both end faces in the longitudinal direction are spherical. However, the shape of the split ring body 67 is not limited to this. As shown in FIG. 16, when the ring gear is attached, the ring gear 31 is press-fitted and crushed by the ring body 65 or the split ring body 67. In the damper ring 58, the ring gear holding function by the conventional O-ring is assigned to the ring body 65, and the elastic function toward the diameter increasing direction is assigned to the core member 66.
[0046]
In the present embodiment, the core members 66 are divided and connected to each other. More specifically, the damper ring 58 is configured by connecting two equal ring units 68 each having a half ring circumference at both ends. Since the core material 66 having a predetermined length is exposed at both ends of each ring unit 68, the exposed ends of the core material 66 are connected to form one damper ring 58. The connecting portion is indicated by 69.
[0047]
The structure of the connecting portion of the core material 66 is as shown in FIGS. In the structure of FIG. 5, the winding of the coil spring is made dense (that is, the winding pitch is small) at one end 66a of the core material, and the coil spring is expanded and the winding is dense at the other end 66b of the core material. It is said. One end 66a is pre-twisted in a direction opposite to the winding direction of the coil spring, and is screwed into the other end 66b, thereby connecting each other in abutting manner. The number of reverse twists of one end 66a is made equal to the number of twists during screwing. As a result, it is possible to prevent the members from being connected to each other with the torsional force remaining.
[0048]
The structure of FIG. 6 uses a connecting member 70 as a separate part. That is, the coil spring is tightly wound with the same diameter as the core material 66 at the end portions 66a and 66b of both core materials, and the large-diameter connecting member 70 capable of screwing the end portions 66a and 66b is tightly wound with the coil spring. And prepared in advance. Then, after the connecting member 70 is screwed into one of the end portions 66a (or 66b), the other end portion 66b (or 66a) reversely twisted as described above is screwed to the opposite side of the connecting member 70. Combine. Thereby, mutual connection is achieved.
[0049]
Here, as shown in FIG. 1, a missing portion 71 is provided at one place in the circumferential direction of the fitting surface 59. That is, one circumferential direction portion of the ring gear fitting hole 56 bulges outward in the radial direction over the entire axial length, and as a result, the fitting surface 59 is partially missing. The defect portion 71 is provided for the necessity of work space, more specifically, the position adjustment of the damper ring 58 and the necessity of mounting the snap ring 57.
[0050]
The damper ring 58 is provided with a pair of stopper portions 74 a and 74 b that engage with both inner side walls 72 a and 72 b of the defect portion 71. That is, the stopper portions 74a and 74b are formed integrally and projecting radially outward from the outer diameter of the ring at the adjacent end portions of the ring main body 65 located on both sides of the connection portion 69 between the ring units 68. These stopper portions 74a and 74b enter into the defect portion 71 and engage with both inner side walls 72a and 72b. There is no ring body 65 between the stopper portions 74a and 74b, and the core member 66 is exposed. The cross-sectional shapes of the stopper portions 74a and 74b are linear as shown in FIG. 3, but may be semicircular as shown in FIG.
[0051]
Due to the engagement between the inner walls 72a and 72b and the stopper portions 74a and 74b, the rotation of the damper ring 58 is restricted or prevented, and it is possible to prevent the damper ring 58 from rotating when the ring gear is attached and causing a phase shift. As a result, the damper ring 58 stops at the desired phase position, so that the expected damping characteristic can be expected.
[0052]
Further, by providing the missing portion 71, it is possible to adjust the position of the damper ring 58 when attaching the ring gear by inserting a hand from here and pulling the core material 66 as appropriate. As a result, the damper ring 58 can be positioned more accurately.
[0053]
From the viewpoint of rotation stopping, only one stopper may be used. This is because a rotational phase shift in one direction can be prevented. However, providing a pair of stoppers is advantageous because it can prevent rotational phase shifts in both directions.
[0054]
Since it is sufficient that the missing portion is at least engaged with the stopper portion, the purpose is not necessarily limited to the work space. Any missing part for other purposes is available for engagement of the stopper part.
[0055]
Here, when such a missing portion 71 is provided, the supporting load of the ring gear 31 is removed as much as that, so that the eccentric movement toward the missing portion 71 side is remarkable when entering the missing portion 71 side when the ring gear 31 moves eccentrically. Become. Ideally, eccentric movement that is uniform in the circumferential direction is desirable, and it is not desirable that such eccentricity occurs only at a specific location.
[0056]
Therefore, the ring main body 65 is removed from the damper ring 58 in the opposite region R in which the defect portion 71 is axisymmetric. That is, only the core material 66 is exposed in the opposite region R located at the opposite phase portion of the missing portion 71 and having the same phase length as the missing portion 71. As a result, the support load of the ring gear 31 is released even in the opposite region R, and it becomes easy to move eccentrically to the opposite region R side. Therefore, the support load is balanced, the eccentric movement to one specific place is prevented, and the uniform circumferential damping characteristic can be obtained. This can also prevent abnormal noises during no load (Hi). The mating surface 59 naturally exists in the opposite region R.
[0057]
Here, if there is a defect portion 71, the press-fitting load from the outside in the radial direction with respect to the damper ring will be lost only in that portion. Therefore, in the conventional O-ring, the followability to the fitting surface is further deteriorated, or in the defect portion 71 The ring slackened. The damper ring according to this embodiment does not have such a variation because there is no variation in diameter and length and the ring rigidity is high.
[0058]
The ring main body 65 has only the stopper portions 74a and 74b in the missing portion 71 and does not exist in the opposite region R at all. Accordingly, at a place other than the region R opposite to the defective portion 71, that is, at the ring body forming portions 75a and 75b on the left and right sides in FIG. The separated ring bodies 67 are connected to each other by the core material 66 and the core material 66 is exposed from the gap between the divided ring bodies 67. In each ring main body formation location 75a, 75b, the split ring bodies 67 located at both ends are made longer than the other split ring bodies 67.
[0059]
Next, a damper ring manufacturing method will be described.
[0060]
The damper ring 58 is configured by connecting two ring units 68 in a single ring shape, but here, it is configured by connecting one ring unit 68a shown in FIG. 7 in a ring shape. That is, the damper ring may be divided at any number of locations, and the damper ring 58 is divided at two locations. In this example, the damper ring is divided at one location.
[0061]
As shown in FIG. 7, in the ring unit 68a, the ring main body 65 is removed by the portions 71x and Rx located in the defect portion 71 and the opposite region R. Then, both ends of the core material 66 are connected to each other by the above-described method as shown in FIGS.
[0062]
9 to 11 show how the damper ring is manufactured. For manufacturing, a die 78 composed of an upper die 76 and a lower die 77 is used, and a core material 66 is held therein, and rubber as a material is vulcanized to integrate them to form a ring unit 68a. Then, both ends of the ring unit 68a are connected to form a damper ring.
[0063]
Here, the mold 78 has a linear shape, and the ring unit 68a is manufactured in a linear state as shown in FIG. The reason for this will be described later.
[0064]
In the mold 78, a plurality of divided ring body forming portions 79 divided in the longitudinal direction and spaced apart from each other, and a core material that is positioned between the divided ring body forming portions 79 and that holds the core material 66. A holding unit 80 is provided. In the mold 78, the divided ring body forming portions 79 and the core material holding portions 80 are alternately arranged on a straight line. The split ring body forming portion 79 is a half-divided hollow portion having the same shape as the split ring body 67, and the core material holding portion 80 partitions between the split ring body forming portions 79 and allows only the passage of the core material 66. Only the permissible half-shaped core material holding hole 81 is provided. The core material holding hole 81 is positioned at the center of the split ring body forming portion 79 and accurately positions the core material 66 at the center of the ring.
[0065]
Each split ring body forming portion 79 is provided with a material injection port 82 and an air vent hole 83 on the opposite side, and each split ring body forming portion 79 alone allows rubber vulcanization.
[0066]
In this case, first, the core material 66 is placed in the core material holding hole 81 of the lower mold 77, and appropriate tension is applied to both ends of the core material 66 to hold the core material 66 straight. Then, the upper mold 76 is put on, the split ring body forming portion 79 is closed, and at the same time, the split ring body forming portions 79 are partitioned by the core material holding portion 80, and the core material 66 is held at the center of the ring by the core material holding portion 80.
[0067]
In this state, when rubber is vulcanized from the material injection port 82 to each divided ring body forming portion 79, the rubber is attached around the core material 66, and each divided ring body 67 is integrally formed. In this way, the ring unit 68a is completed, and then the product is divided and taken out. Thereafter, the burrs remaining in the material injection port 82 and the air vent hole 83 are removed as necessary.
[0068]
According to the above method, the core material 66 can be accurately held at the center of the ring or the split ring body 67 at the intermediate position in the ring longitudinal direction by the core material holding portion 80. Therefore, the core member 66 is not decentered, and the damping characteristics of the ring can be maintained as planned.
[0069]
That is, without such a core material holding portion 80, the core material 66 can be held only at both ends, and there is a possibility that slack or the like occurs in the middle portion and the center of the ring cannot be determined. Since it can hold | maintain in a position, the core material 66 can be determined in the ring center.
[0070]
Conversely, this is also a structural advantage in which the ring body is divided and a gap is provided between them. As a result, the core material holding portion 80 is formed in the mold, and the core material 66 can be held at the middle position in the longitudinal direction.
[0071]
From this point of view, it is better to provide a plurality of core material holding portions 80, and it is therefore preferable to provide a plurality of gaps between the split portions of the ring body. However, one may be used as long as the center of the core material can be positioned. In any case, such a number gives priority to the damper characteristics, and is optimally determined after considering the manufacturing reasons.
[0072]
Here, the reason why the mold 78 is formed in a linear shape, and the linear ring unit 68a is manufactured and connected later is because a plurality of molds are taken into consideration as shown in FIG. In other words, since the mold becomes smaller when the linear shape is used, the mold space is advantageously reduced even when a plurality of the ring units 68a are manufactured and the plurality of manufactured ring units 68a are taken out simultaneously. Of course, the mold itself is also small, which is advantageous for cost reduction.
[0073]
Of course, as shown in FIG. 12, for example, a plurality of molds may be arranged in a square shape to form a ring-shaped ring unit from the beginning, and a plurality of them may be obtained. In this case, the mold and the space thereof are increased in size and disadvantageous in terms of cost. However, the ring body or the split ring body 67 can be formed into an arc shape from the beginning, which is preferable in terms of function. Conversely, if it is a linear shape, it must be bent when the ring is installed, which is not ideal in terms of function. However, in this embodiment, since the relationship between the curvature and length of the split ring body 67 is optimally determined, there is no functional problem even if it is a linear shape.
[0074]
12 and 13 are schematic views of the mold, and the portions corresponding to the above-described portions are represented only by the corresponding symbols.
[0075]
Next, another embodiment of the damper ring will be shown.
[0076]
As shown in FIG. 8, in this embodiment, the core member 66a is harder than the previous one and cannot be bent freely, that is, made of a non-flexible body. The core member 66a has a ring shape, and its outer diameter is slightly smaller than the inner diameter of the teeth 62a of the spline 62. The split ring body 67 is positioned at the same circumferential position as the space 81 (circumferential clearance) between the teeth 62a of the spline 62, and is slightly shorter than the clearance so as to enter the space 81.
[0077]
According to this, when inserting the damper ring 58, while inserting the split ring body 67 in the space 81 and avoiding the teeth 62a of the spline 62, the entire ring is inserted while being slid by pushing forward in the axial direction. Can do. The split ring body 67 can be pressed against the fitting surface 59 by the hard core material 66a, and ring biting when the ring gear is inserted can be prevented. A predetermined crushing allowance h on the outer peripheral side and / or inner peripheral side of the split ring body 67 ₂ , H _Three May be provided. By this, the same operation and effect as before can be exhibited. Note that the shape of the split ring body 67 follows the shape of the space 81, and the core member 66 a is positioned offset inward in the radial direction of the split ring body 67.
[0078]
Various other embodiments of the present invention are also conceivable. For example, the damper ring of this embodiment has a total of twelve divided ring bodies, but this can be reduced to a minimum of two, and conversely can be increased from twelve. The damper ring according to the present invention can be applied not only to a ring gear mounting portion of a planetary gear mechanism of a vehicle transfer but also to a fitting portion between various members. That is, in the above embodiment, the large-diameter side member is the casing 7 and the small-diameter side member is the ring gear 31, but the present invention is not limited to this, and the damper ring of the present invention can be applied to any fitting portion.
[0079]
【The invention's effect】
The present invention exhibits the following excellent effects.
[0080]
(1) The damper ring can be accurately positioned at a predetermined phase position, and a desired damper ring performance can be exhibited.
[0081]
(2) The support load balance of the small-diameter side member can be achieved, and the eccentric movement to a specific location can be prevented.
[Brief description of the drawings]
FIG. 1 is a front view showing a damper ring of an embodiment.
FIG. 2 is a cross-sectional view taken along the line II of FIG.
FIG. 3 is a cross-sectional view taken along the line II-II of FIG.
4 is a cross-sectional view taken along the line II-II of FIG. 1, showing a cross section of another stopper portion.
FIG. 5 is a view showing a connecting structure of core members.
FIG. 6 is a view showing another connecting structure of the core material.
FIG. 7 is a front view showing a ring unit before connecting core members.
FIG. 8 is a front view showing another embodiment of the damper ring.
FIG. 9 is a plan view showing a lower mold and a core material according to a damper ring manufacturing method.
10 is a cross-sectional view taken along the line III-III in FIG.
11 is a cross-sectional view taken along the line IV-IV in FIG.
FIG. 12 is a schematic plan view showing another mold arrangement.
FIG. 13 is a schematic plan view showing the arrangement of molds.
FIG. 14 is a longitudinal side view showing a transfer, with the left side being the front and the right side being the rear.
FIG. 15 is an enlarged view showing a mounting portion of the damper ring.
FIG. 16 is an enlarged view showing a state after the ring gear is attached.
FIG. 17 is a schematic front view of a transfer.
FIG. 18 is a diagram showing a clearance around the outer periphery of the ring gear.
FIG. 19 is a plan view showing a four-wheel drive vehicle, with the left side being front (F) and the right side being rear (R).
[Explanation of symbols]
7 Casing
31 Ring gear
58 Damper ring
59 Mating surface
65 Ring body
66 Core material
67 Split ring body
71 Loss
72a, 72b inner wall
74a, 74b Stopper part
R opposite area

Claims (7)

Was charged a damper ring in the gap between the inner diameter side member and the outer diameter side member fitted to each other In the structure to buffer the direct impingement of these members to each other, the damper ring, and a ring body made of an elastic body , is composed of a core material made of metal or plastic is embedded in the ring body, the ring body so as to press against the mating surface of the outer diameter side member is attached to the damper ring by core material, In addition to providing a working part or the like at a predetermined position on the fitting surface of the outer diameter side member, a stopper is provided on the damper ring to engage with the inner wall of the missing part. The damper ring mounting structure is characterized in that the rotation of the damper ring is restricted by the above.   The damper ring mounting structure according to claim 1, wherein the ring body is removed from the damper ring and the core member is exposed in an opposite region in which the defect portion is axially symmetric.   In the damper ring present in the defect part, a pair of the stopper parts are provided to engage both inner walls of the defect part, and the ring body is removed between the stopper parts to expose the core material. The mounting structure of the damper ring according to claim 1 or 2, wherein the damper ring is present.   The damper ring mounting structure according to claim 2 or 3, wherein the core member is divided at the exposed portion and connected to each other.   The ring main body is divided and the divided ring bodies are arranged at a predetermined interval in the ring longitudinal direction, and the divided ring bodies are connected by the core material at a place other than the defect portion and the opposite region. The damper ring mounting structure according to any one of claims 1 to 4, wherein the core member is exposed from a gap between the split ring bodies.   The damper ring mounting structure according to any one of claims 1 to 5, wherein the core member is made of a coil spring, a single spring steel, or a metal or plastic wire. Was charged a damper ring in the gap between the inner diameter side member and the outer diameter side member fitted to each other In the structure to buffer the direct impingement of these members to each other, the damper ring, and a ring body made of an elastic body , is composed of a core material made of metal or plastic is embedded in the ring body, the ring body so as to press against the mating surface of the outer diameter side member is attached to the damper ring by core material, In addition to providing a missing part for the necessity of a working space or the like at a predetermined position on the fitting surface of the outer diameter side member, the ring body is removed from the damper ring in an opposite region that is axially symmetrical to the missing part. The characteristic damper ring mounting structure.

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