JP4017787B2 - Coupling - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a coupling that is disposed in a power transmission path and electromagnetically controls a transmission torque.
[0002]
[Prior art]
Page 126 of "Position Control Product Catalog 5th Edition" (issued by the Sales Division of Miki Pulley Co., Ltd. on February 1, 1994), Fig. 63 shows a mounting example of the electromagnetic clutch 201 of the flange mounting type as shown in Fig. 4 Has been.
[0003]
In the electromagnetic clutch 201, the core 205 of the electromagnet 203 is fixed to the stationary member 207 on one side, and is similarly disposed in the recess 209 a of the stationary member 209 on the other side fixed to the stationary member 207. The core 205 (electromagnet 203) is supported concentrically on the drive shaft 211 on the left side, for example, via a bearing 213. A rotor 215 is fitted on the drive shaft 211 and is keyed, and the rotor 215 rotates integrally with the drive shaft 211.
[0004]
On the other hand, a driven shaft 219 supported by a stationary member 209 on the other side via a bearing 217 is supported. A boss portion 221a of the clutch disk 221 is fitted on the driven shaft 219 and is keyed, and the clutch disk 221 rotates integrally with the driven shaft 219.
[0005]
When the electromagnetic clutch 203 is energized, the clutch disk 221 is attracted and the electromagnetic clutch 201 is connected.
[0006]
[Problems to be solved by the invention]
However, in order to smoothly connect the electromagnetic clutch 201, the centering of the drive shaft 211 and the driven shaft 219 is strictly required, and if there is an unbalance of rotation between the two shafts 211 and 219, the durability of the electromagnetic clutch 201 is increased. It will adversely affect sex.
[0007]
Accordingly, an object of the present invention is to improve the assembling and supporting properties of a coupling that electromagnetically controls the transmission torque.
[0008]
[Means for Solving the Problems]
In order to solve the above-mentioned problem, the invention according to claim 1 is a case-like torque transmission member rotatably supported at both ends of one side and the other side in a fixed case filled with oil, An axial torque transmission member disposed at the axial center of the case-shaped torque transmission member and rotatably supported by the torque transmission member at the inner and outer ends in the axial direction; a main clutch disposed between the two torque transmission members; An electromagnetic clutch, a cam mechanism that is sandwiched between the two clutches, and when the electromagnetic clutch is fastened, converts a fastening torque into a thrust force and expands the main clutch. And a pressing member to be pressed and fastened, wherein the one end of the case-like torque transmitting member is supported at substantially the same position in the axial direction as the outer end of the shaft-like torque transmitting member. The other end portion of the case-shaped torque transmitting member is integrated with the outer end portion of the rotor integrated at the other end portion and the fixed case at substantially the same axial position as the outer end portion. The inner end of the shaft-shaped torque transmission member is formed to have a smaller diameter than the inner peripheral spline, and the cam mechanism is connected to the inner end. It is characterized by being rotatably supported on the part .
[0009]
Therefore, when the electromagnetic clutch is engaged, the engagement torque is converted / expanded into thrust force by the cam mechanism. In response to the thrust force, the pressing member presses and fastens the main clutch. Thus, a large torque can be transmitted, and the coupling transmission torque can be adjusted by adjusting the fastening torque of the electromagnetic clutch.
[0010]
In addition, one end of the case-shaped torque transmission member and the outer end of the shaft-shaped torque transmission member are supported at substantially the same position in the axial direction, and at the other end of the case-shaped torque transmission member. The outer end portion of the integrated rotor and the fixed portion of the core are arranged and supported at substantially the same position in the axial direction, and the support portions at both ends are not arranged with a space in the axial direction. Since the size can be reduced and the support is ensured, the supportability is improved. Further, the shaft-shaped torque transmission member can be reduced in size and weight.
[0011]
The invention according to claim 2 is the coupling according to claim 1, wherein an outer peripheral portion of the rotor is connected to a spline portion at an inner periphery of the other end portion of the case-like torque transmitting member and It is characterized in that it is centered by fitting to a circumferential centering portion.
[0012]
Therefore, the operation and effect equivalent to the invention of claim 1 can be obtained, and the rotor is securely supported by the case-like torque transmission member, so that there is a rotational imbalance on the coupling input and output shaft side. In addition, the adverse effect of the engagement action of each clutch is suppressed, and the durability is improved.
[0013]
A third aspect of the present invention is the coupling according to the first or second aspect, wherein the spline portions are respectively formed on an inner periphery of the outer end portion of the shaft-shaped torque transmitting member and an inner periphery of the outer end portion of the rotor. , And each spline can be connected to any of the input and output shafts.
[0014]
Therefore, the operation and effect equivalent to the invention of the first or second aspect can be obtained, and both the coupling input and output shafts can be inserted and connected to the spline holes, so that the assembly is easy.
[0015]
Invention of Claim 4 is a coupling in any one of Claims 1-3, Comprising: The outer end part of the said shaft-shaped torque transmission member is supported by the case-shaped torque transmission member via a bearing, An outer end portion of the rotor is supported by a core of an electromagnetic clutch through a bearing, and the sizes of both the bearings are the same.
[0016]
Therefore, the same operation and effect as the invention according to any one of claims 1 to 3 can be obtained, and the size of the bearings at both ends of the coupling is the same, so the processing becomes easy and the cost is reduced. .
[0021]
DETAILED DESCRIPTION OF THE INVENTION
An embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a cross-sectional view of a coupling 1 of this embodiment used in a power transmission system of a vehicle. FIG. 2 and FIG. 3 are skeleton diagrams showing a power transmission system of a four-wheel drive vehicle that exemplifies an applicable portion of the coupling 1. The coupling 1 of any application example has the same internal structure.
[0022]
As shown in FIG. 1, the coupling 1 is accommodated in a fixed case 3 fixed to the vehicle body side, and the fixed case 3 is filled with oil. The fixed case 3 is formed by coupling a case 3a and a case 3b.
[0023]
The coupling 1 includes a rotating case 5 (case-shaped torque transmission member), a hollow shaft 7 (axial torque transmission member), a multi-plate main clutch 9 and a pilot clutch (electromagnetic clutch) 11, a ball cam 13 (cam mechanism), The ring-shaped electromagnet 15, armature 17, controller and the like are included.
[0024]
The rotating case 5 is formed by joining a left end (one side end) wall portion 5b to a cylindrical portion 5a of a nonmagnetic material. A spline portion 5c is formed on the inner periphery of the cylindrical portion 5a, and an opening 5d is provided at the right end (the other end). A centering portion 5e for centering a rotor 19 described later is formed on the inner periphery of the opening 5d.
[0025]
The rotor 19 is hollow, and the outer periphery of the left end portion is connected to the spline portion 5c of the rotary case 5, and is positioned in the axial direction by contacting the end portion on the mouth side of the spline portion 5c, while the outer periphery of the right end portion is The rotating case 5 is centered by being fitted to the centering portion 5 e, and is prevented from coming off by a retaining ring 21 and integrated with the rotating case 5. Then, the outer end portion of the rotor 19 is supported by a core 25 of an electromagnet 15 to be described later via a bearing 23 of both seals, and is further fixed to the fixed case 3 (core) via the outer end portion of the core 25 press-fitted into the fixed case 3. 25) is rotatably supported. The bearing 23 and the outer end of the core 25 are disposed at substantially the same position in the axial direction.
[0026]
On the other hand, a spline portion 19a is formed on the inner periphery of the rotor 19, and the input shaft or the output shaft can be connected to the spline. Reference numeral 27 denotes a non-magnetic ring.
[0027]
At the left end of the rotating case 5, the wall 5 b is rotatably supported by the fixed case 3 via a bearing 29. Thus, the left and right ends of the rotating case 5 are supported by the fixed case 3 by the bearings 29 and 23, respectively, and rotate together with the rotor 19.
[0028]
As shown in FIG. 1, the electromagnet 15 is disposed in a recess provided in the rotor 19, the outer end portion of the core 25 of the electromagnet 15 is press-fitted into the fixed case 3, and the pin 31 is a groove 3 c of the fixed case 3. And is fixed in the fixed case 3. In this state, the air gaps 33 and 33 are maintained at a predetermined amount. Further, the lead wire 35 of the electromagnet 15 is taken out through the take-out hole 3d provided in the fixed case 3 and wired.
[0029]
The hollow shaft 7 is disposed at the axial center of the rotating case 5, and the inner and outer ends are supported by the rotating case 5 via bearings 37 and 39, respectively. The sizes of the bearing 37 and the bearing 23 are the same. The bearing 37 that supports the outer end portion of the shaft 7 and the bearing 29 that supports the rotating case 5 are arranged at substantially the same position in the axial direction. A spline portion 7e is provided on the outer periphery adjacent to the outer end portion of the shaft 7, and a spline portion 7f is provided on the inner periphery. An unillustrated output shaft or input shaft (both not shown) can be connected to the inner peripheral spline portion 7f.
[0030]
The inner end portion of the hollow shaft 7 is formed in a small diameter portion 7a having a smaller diameter than the spline portion 7f on the inner periphery of the outer end portion. And the axial center part of the small diameter part 7a between the input and output shaft connected to the spline part 7f on the inner periphery of the outer end and the input and output shaft connected to the spline part 19a on the inner periphery of the rotor 19 An oil sump 47 is formed on the surface.
[0031]
The stepped portion 7c at the boundary between the spline portion 7f on the inner periphery of the shaft 7 and the small-diameter portion 7a and the back-side end portion 7d of the small-diameter portion 7a are inserted, and the insertion amount is regulated by contact with the end portion of the output shaft. Is possible.
[0032]
Further, oil passages 41, 43, and 45 through which oil flows in and out are provided on the end face sides of the bearings 37 and 39 that support the shaft 7. The oil in the oil reservoir 47 lubricates and cools the main clutch 9, the pilot clutch 11, the ball cam 13, etc. through the oil passages 49 and 51 provided radially and the oil passages 41, 43 and 45.
[0033]
The spline portions 19a and 7f on the inner periphery of the rotor 19 and the inner periphery of the shaft 7 are formed in the same specifications.
[0034]
The multi-plate main clutch 9 is disposed between the spline portion 5 c on the inner periphery of the cylindrical portion 5 a of the rotating case 5 and the spline portion 7 e on the outer periphery of the shaft 7. Oil passages 53 are provided radially in this portion of the spline portion 5 c on the inner periphery of the rotating case 5. An oil passage 57 is provided in the inner clutch plate of the main clutch 9.
[0035]
The multi-plate pilot clutch 11 is disposed between a spline portion 5c on the inner periphery of the rotating case 5 and a spline portion 61a on the outer periphery of the cam ring 61 (described later). Is provided with an oil passage 55. Further, each clutch plate of the pilot clutch 11 is formed with a notch 11a to prevent magnetic leakage.
[0036]
The armature 17 is disposed with the clutch plate of the pilot clutch 11 separated from the electromagnet 15. The outer periphery of the armature 17 is connected to the spline portion 5c on the inner periphery of the rotary case 5 and is movable in the axial direction. When the armature 17 is attracted by the electromagnet 15, the pilot clutch 11 is engaged.
[0037]
As described above, one specification spline portion 5 c on the inner periphery of the rotating case 5 is engaged with the main clutch 9, the pilot clutch 11, the armature 17, and the rotor 19.
[0038]
The spline portion 7e on the outer periphery of the shaft 7 and the spline portion 61a on the outer periphery of the cam ring 61 are formed to have the same specifications.
[0039]
The ball cam 13 is disposed between the clutches 9 and 11 on the small diameter portion 7a of the hollow shaft 7, and includes a cam ring 61, a pressure plate (pressing member) 63, a ball 65, and a ring-shaped retainer 67. It is composed of The pressure plate 63 is connected to the outer peripheral spline portion 7e of the shaft 7 so as to be movable in the axial direction.
[0040]
An oil passage 71 is provided in the pressure plate 63 in the axial direction.
[0041]
A cam surface is formed on the opposing surface of the pressure plate 63 and the cam ring 61 arranged with the ball 65 sandwiched in the axial direction, and the torque is converted into a thrust force by the cam action during the relative rotation of the both 63 and 65. And expanded. Since the movement of the ball 65 in the radial direction due to the centrifugal force is restricted by the peripheral retainer 67, the cam surface is formed in a plane inclined in the circumferential direction.
[0042]
A return spring 69 is disposed between the opposed surfaces of the hollow shaft 7 and the pressure plate 63, and biases the pressure plate 63 in the direction in which the main clutch 9 is released.
[0043]
The controller performs excitation of the electromagnet 15, control of excitation current, excitation stop, and the like.
[0044]
Next, the operation of this coupling 1 will be described.
[0045]
When the electromagnet 15 is excited, the armature 17 is attracted, and the pilot clutch 11 is pressed and fastened. When the pilot clutch 11 is engaged, the engagement torque is applied to the ball cam 13, and the direction is changed and expanded to the thrust force. In response to this thrust force, the pressure plate 63 presses the main clutch 9 and fastens it. In this way, the coupling 1 is connected.
[0046]
When the exciting current of the electromagnet 15 is controlled, the thrust force of the ball cam 13 is changed by the slip of the pilot clutch 11, the fastening force of the main clutch 9 is changed, and the driving force transmitted to the output side is adjusted.
[0047]
At this time, the oil in the oil reservoir 47 slides through the oil passages 43, 45, 49, 51, the inner clutch plates of the main clutch 9, the oil passages 57, 71 provided in the pressure plate 63, and the like. Each part such as a part is lubricated and cooled, and discharged from the oil passages 53 and 55 of the rotating case 5 to the outside. By providing the oil passages 53 and 55 in the rotating case 5, oil movement is promoted inside the rotating case 5, and the lubrication and cooling performance of each part is improved.
[0048]
When the excitation of the electromagnet 15 is stopped, the pilot clutch 11 is released, the thrust force of the ball cam 13 disappears, the main clutch 9 is released by the biasing force of the return spring 69, and the coupling 1 is disconnected. .
[0049]
As shown in FIG. 2, when the coupling 1 is disposed at the input of the rear differential 121, the driving force of the horizontally installed engine 103 is the transmission 105, the transfer 107, the front differential 109, the front axles 111 and 113, the left and right It is transmitted to the left and right rear wheels 127 and 129 via the front wheels 115 and 117, the rear wheel side propeller shaft 119, the coupling 1, the rear differential 121, and the rear axles 123 and 125.
[0050]
That is, when the coupling 1 is connected, the driving force of the engine 103 is distributed from the rear differential 121 to the left and right rear wheels 127 and 129 via the rear axles 123 and 125, and the vehicle enters a four-wheel drive state. Further, when the coupling 1 is released, the rear wheel side after the rear differential 121 is cut off, and the vehicle enters the front two-wheel drive state.
[0051]
Further, as shown in FIG. 3, the coupling 1 may be arranged between the transfer 107 and the rear wheel side propeller shaft 119, and in this case, the same operation as in the arrangement shown in FIG. 2 can be obtained. However, when the coupling 1 is disconnected and the vehicle is in the front two-wheel drive state, the propeller shaft 119 is idled on the rear wheel side, so that the number of idling members increases, which is disadvantageous compared to the case of FIG. It becomes.
[0052]
Thus, according to this embodiment, the rotating case 5 is supported by the fixed case 3 at the left end by the bearing 29 and the right end by the bearing 23 and the core 25, and the shaft 7 is supported by the rotating case 5 through the bearing 37 and the bearing 39. Therefore, the pair of input and output shafts connected to the inner peripheral spline portion 7f of the shaft 7 and the inner peripheral spline portion 19a of the rotor 19 are surely supported by the rotating case 5 and further the case 3. Therefore, the coupling action of the coupling 1 is not adversely affected by the rotational imbalance on the input and output shaft sides.
[0053]
Similarly, the electromagnet 15 is supported by the fixed case 3 and supported by the rotating case 5 via the bearing 23. Therefore, the electromagnet 15 is adversely affected by the rotational imbalance on the input and output shaft sides. There is no.
[0054]
In addition, since both the input and output shafts only need to connect the shaft spline to the inner peripheral spline portions 7f and 19a, the input and output shafts can be easily assembled.
[0055]
Further, since the inner peripheral spline portions 7f and 19a of the shaft 7 and the rotor 19 have the same specifications, and the outer peripheral spline portions 7e and 61a of the cam ring 61 have the same specifications, the cost is reduced.
[0056]
Moreover, since the bearing 37 and the bearing 23 are the same size, cost is reduced.
[0057]
Further, since the spline portion 5c on the inner periphery of the rotary case 5 is connected to the outer periphery of the main clutch 9, the armature 17, the pilot clutch 11, and the rotor 19, the structure is simplified and the cost is reduced.
[0058]
Further, since the ball cam 13 is disposed on the small diameter portion 7a of the hollow shaft 7, the size and weight can be reduced, and the cost is reduced accordingly.
[0059]
Moreover, since the small diameter part 7a is provided in the shaft 7, the insertion amount of the input / output shaft can be regulated.
[0060]
Further, the bearing 29 and the bearing 37 are arranged at substantially the same position in the axial direction and are arranged inside and outside in the radial direction, and the bearing 23 and the fixing portion of the core 25 of the electromagnet 15 to the fixing case 3 are arranged at substantially the same position in the axial direction. Therefore, the coupling 1 can be reduced in size without increasing in size in the axial direction.
[0061]
In addition, the above arrangement of the electromagnet 15 can ensure a sufficient magnetic path cross-sectional area while suppressing overhang in the axial direction, and can be downsized.
[0062]
In addition, the arrangement | positioning site | part of the coupling 1 is not limited to the site | part shown to the said FIG.2, FIG.3, The attachment part of the axle of the left-right each side of the front axle of a four-wheel drive vehicle, or the same attachment part of a rear axle You may arrange in.
[0063]
Further, it can be used, for example, between a motor and a drive system of an electric vehicle, a switching unit between an engine drive and a motor drive of a hybrid vehicle, and differential limiting of a differential device.
[0064]
【The invention's effect】
As apparent from the above description, according to the first aspect of the present invention, when the electromagnetic clutch is engaged, the engagement torque is converted and expanded to the thrust force by the cam mechanism. In response to the thrust force, the pressing member presses and fastens the main clutch. Thus, a large torque can be transmitted, and the coupling transmission torque can be adjusted by adjusting the fastening torque of the electromagnetic clutch.
[0065]
In addition, one end of the case-shaped torque transmission member and the outer end of the shaft-shaped torque transmission member are supported at substantially the same position in the axial direction, and at the other end of the case-shaped torque transmission member. Since the outer end portion of the integrated rotor and the fixed portion of the core are arranged and supported at substantially the same position in the axial direction, and the support portions at both ends are not arranged with a space in the axial direction. Can be reduced in size in the axial direction, and support is ensured, so that supportability is improved. Further, the shaft-shaped torque transmission member can be reduced in size and weight.
[0066]
According to the second aspect of the invention, the same effect as that of the first aspect of the invention can be obtained, and the rotor is securely supported by the case-like torque transmission member. Even if there is rotational imbalance, the adverse effect of the engagement action of each clutch is suppressed, and durability is improved.
[0067]
According to the invention described in claim 3, the same effect as that of the invention described in claim 1 or 2 can be obtained, and since both the coupling input and output shafts can be inserted into the spline holes and connected, it is easy to assemble. It is.
[0068]
According to the invention described in claim 4, the same effect as in the invention described in any one of claims 1 to 3 can be obtained, and since the sizes of the bearings at both ends of the coupling are the same, processing is easy. The cost is reduced.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of one embodiment of the present invention.
FIG. 2 is a skeleton diagram showing a dispositionable portion according to an embodiment.
FIG. 3 is a skeleton diagram showing another placeable portion according to an embodiment;
FIG. 4 is a cross-sectional view of a conventional example.
[Explanation of symbols]
3 Fixed case 5 Rotating case (Case-like torque transmission member)
5c, 7e, 7f, 19a, 61a, spline portion 7 shaft (axial torque transmission member)
7a Small diameter part 9 Main clutch 11 Pilot clutch (electromagnetic clutch)
13 Ball cam (cam mechanism)
15 Electromagnet 17 Armature 19 Rotor 23, 29, 37, 39 Bearing 25 Core 47 Oil reservoir 61 Cam ring 63 Pressure plate (Pressing member)
67 Retainer 69 Return spring

Claims (4)

A case-like torque transmission member rotatably supported in both ends of one side and the other side in a fixed case filled with oil;
An axial torque transmission member disposed at the axial center of the case-shaped torque transmission member and rotatably supported by the torque transmission member at the inner and outer ends in the axial direction;
A main clutch and an electromagnetic clutch disposed between the two torque transmission members;
A cam mechanism that is sandwiched between the two clutches and that, when the electromagnetic clutch is engaged, converts the engagement torque into a thrust force and expands it;
A coupling comprising a pressing member that receives the thrust force and presses and fastens the main clutch,
The one end portion of the case-shaped torque transmission member is supported at substantially the same position in the axial direction as the outer end portion of the shaft-shaped torque transmission member,
The other end of the case-shaped torque transmission member is integrated with the outer end of the rotor integrated at the other end, and the fixed case at substantially the same axial position as the outer end. is supported via the fixing portion of the core of an electromagnetic clutch which is,
The inner end portion of the shaft-shaped torque transmission member is formed to have a smaller diameter than the spline portion on the inner periphery of the outer end portion,
The coupling, wherein the cam mechanism is rotatably supported on the inner end portion . The coupling according to claim 1,
The coupling is characterized in that an outer peripheral portion of the rotor is connected to a spline portion at an inner periphery of the other end portion of the case-like torque transmission member, and is centered by being fitted to a centering portion of the inner periphery. The coupling according to claim 1 or 2,
Spline portions are respectively formed on the inner periphery of the outer end portion of the shaft-shaped torque transmission member and the inner periphery of the outer end portion of the rotor, and each spline can be connected to any of the input and output shafts. Coupling. The coupling according to any one of claims 1 to 3,
The outer end portion of the shaft-shaped torque transmission member is supported by the case-shaped torque transmission member via a bearing,
The outer end of the rotor is supported on the core of the electromagnetic clutch through a bearing,
Coupling characterized in that the sizes of the bearings are the same.

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